JP2015034577A - Clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch capable of reducing a compressive load acting on a strap plate.SOLUTION: In a clutch 1, a clutch disc 19 to be put in friction contact with an input side rotary member for transmitting torque is connected to an output side rotary member, a thrust plate 7 for elastically thrusting the clutch disc 19 against the side of the input side rotary member is arranged on the opposite side to the input side rotary member across the clutch disc 19, and a body of rotation 2 to be rotated integrally with the input side rotary member is connected to the thrust plate 7 via a connection mechanism 12 which transmits torque between the body of rotation 2 and the thrust plate 7. The connection mechanism 12 includes a first connection part 22 for transmitting torque from the body of rotation 2 to the thrust plate 7, as a tensile load, to increase the rotating speed of the output side rotary member, and a second connection part 23 for transmitting toque from the thrust plate 7 to the body of rotation 2, as a tensile load, to increase the rotating speed of the input side rotary member.

Description

  The present invention relates to a clutch configured to transmit torque by bringing a clutch disk into frictional contact with an input-side rotating member.

  2. Description of the Related Art Conventionally, there has been known a clutch configured to transmit torque by sandwiching a clutch disk between a flywheel that rotates integrally with an output shaft of an engine and a pressure plate coupled to the flywheel via a clutch cover. ing. A clutch configured in this way is described in Patent Document 1. In the clutch described in Patent Document 1, a flywheel and a clutch cover are integrated, and a pressure plate is provided inside the clutch cover so as to be movable in the axial direction. Further, a strap plate in which a plurality of plate members are stacked is provided so that an elastic force is applied in a direction in which the pressure plate is separated from the clutch disk and the clutch cover and the pressure plate are rotated together. Specifically, one end of the strap plate is connected to the clutch cover, and the other end is connected to the pressure plate at a position shifted in the circumferential direction from the fixed portion connected to the clutch cover. It is configured. The elastic force of the diaphragm spring is applied in a direction opposite to the elastic force of the strap plate, and a release mechanism is provided to reduce the elastic force of the diaphragm spring.

JP 2010-78156 A

  As described in Patent Document 1, a clutch having a strap plate is generally configured such that a tensile load acts on the strap plate when torque output from the engine is transmitted to the drive wheels. When the clutch is configured so that a tensile load acts on the strap plate when transmitting the engine output torque to the drive wheels in this way, torque is applied so that the engine speed increases from the clutch output side. When transmitting, a compressive load acts on the strap plate. Therefore, when the torque transmitted from the output side of the clutch is large so that the engine speed increases, the durability of the strap plate may be reduced.

  Further, when a tensile load acts on the strap plate, the component force of the tensile load acts in a direction to separate the pressure plate from the clutch disk. Thus, the component force of the tensile load acting on the pressure plate can be relatively predicted from the rigidity of the strap plate and the torque input to the clutch. On the other hand, when a compressive load acts on the strap plate, the component force of the compressive load acts so as to press the pressure plate toward the clutch disk. In this case, it is relatively difficult to predict the load that presses the pressure plate toward the clutch disk, and therefore the controllability of the transmission torque capacity of the clutch may be reduced.

  The present invention has been made paying attention to the above technical problem, and an object of the present invention is to provide a clutch capable of reducing the compressive load acting on the strap plate.

  In order to achieve the above object, according to the present invention, a clutch disk that is disposed to face an input side rotating member and is brought into frictional contact with the input side rotating member to transmit torque is coupled to the output side rotating member. A pressing plate that elastically presses the clutch disk toward the input-side rotating member is disposed on the opposite side of the input-side rotating member with the clutch disk interposed therebetween, and rotates integrally with the input-side rotating member. In a clutch in which a body and the pressing plate are connected by a connecting mechanism that transmits torque between the rotating body and the pressing plate, the connecting mechanism increases the rotational speed of the output-side rotating member. The first connecting portion that transmits torque from the rotating body to the pressing plate as a tensile load, and the tensile load as the tensile load so as to increase the rotational speed of the input-side rotating member. And it is characterized in that it comprises a second coupling part for transmitting torque to the rotary member from the pressure plate.

  The connection mechanism includes a first fixing portion connected to one of the rotating body and the pressing plate, and the other of the rotating body and the pressing plate on both sides of the first fixing portion in the circumferential direction. You may provide the 2nd fixing | fixed part and 3rd fixing | fixed part which are connected.

  The first fixing portion, the second fixing portion, and the third fixing portion are configured to be in the same position in the axial direction when the clutch disk and the pressing plate are in contact with each other to transmit torque. May be.

  The connection mechanism includes a third connection portion that is connected to the first fixing portion and the second fixing portion and elastically deforms in the axial direction, and is connected to the first fixing portion and the third fixing portion and in the axial direction. A fourth connecting portion that elastically deforms, and the third connecting portion and the fourth connecting portion may be formed to have the same length.

  The first connecting part may have a first bent part protruding in the axial direction, and the second connecting part may have a second bent part protruding in the axial direction.

  Torque transmitted from the rotating body to the pressing plate as a tensile load so as to increase the rotational speed of the output side rotating member, and from the pressing plate as a tensile load so as to increase the rotational speed of the input side rotating member. The amount of protrusion in the axial direction with respect to the length in the longitudinal direction of either one of the first bent portion and the second bent portion that transmits a large torque as the tensile load to the rotating body is the other. It may be formed smaller than the protruding amount in the axial direction with respect to the length in the longitudinal direction of the bent portion.

  The first connecting portion includes a fourth fixing portion that connects the first connecting portion and the second connecting portion to the pressing plate, and the first connecting portion is configured to move the fourth fixing portion when the pressing plate moves in the axial direction. Includes a fifth connecting portion that is elastically deformed so as to move only in the axial direction, and the second connecting portion moves only in the axial direction when the pressing plate moves in the axial direction. The 6th connection part which deforms elastically may be included.

  The connecting mechanism is provided with a fixing means for connecting the rotating body or the pressing plate, and the connecting mechanism is provided so as to be able to move relative to the fixing means in the circumferential direction of the pressing plate. May be.

  The connection mechanism includes a first plate member in which a first through hole is formed at a position connected to the rotating body or the pressing plate, and the fixing means is a first fixing inserted into the first through hole. And the outer diameter of the first fixing member is smaller than the inner diameter of the first through hole so that the pressing plate can move relative to the first plate member in the circumferential direction. It may be.

  The coupling mechanism includes a second plate member having a second through hole formed at one end thereof, a third through hole formed at one end portion thereof, and adjacent to the second plate member in the circumferential direction. A third plate member provided; and the fixing means is inserted into the second through hole and the third through hole, and the second plate member is inserted into one of the rotating body and the pressing plate. A second fixing member that couples the third plate member, and the third through-hole in the second through-hole is in a state in which no torque is input to either the second plate member or the third plate member. A gap between the inner wall surface on the plate member side and the second fixing member is smaller than a gap between the inner wall surface facing the inner wall surface on the second plate member side in the third through hole and the second fixing member. May be.

  Torque transmitted from the rotating body to the pressing plate as a tensile load so as to increase the rotational speed of the output side rotating member, and from the pressing plate as a tensile load so as to increase the rotational speed of the input side rotating member. The rigidity of any one of the first connecting part and the second connecting part that transmits a large torque as a tensile load to the rotating body is higher than the rigidity of the other connecting part. May be.

  The input-side rotating member may include an output shaft of an engine mounted on a vehicle, and the output-side rotating member may be connected to a cranking unit that rotates the output shaft to crank the engine.

  The cranking means may include a motor mounted on the vehicle.

  According to the present invention, the clutch disk that is disposed to face the input side rotating member and is brought into frictional contact with the input side rotating member to transmit torque is connected to the output side rotating member. In addition, a pressing plate that elastically presses the clutch disk toward the input side rotating member is disposed on the opposite side of the input side rotating member with the clutch disk interposed therebetween, and a rotating body and a pressing plate that rotate integrally with the input side rotating member Are configured to transmit torque by a coupling mechanism. Then, the connection mechanism pulls the first connection part that transmits torque from the rotating body to the pressing plate as a tensile load so as to increase the rotation speed of the output-side rotation member, and increases the rotation speed of the input-side rotation member. And a second connecting part that transmits torque from the pressing plate to the rotating body as a load. Therefore, even when torque is input from the input-side rotating member so as to increase the rotational speed of the output-side rotating member, torque is output from the output-side rotating member so as to increase the rotational speed of the input-side rotating member. Even if it is input, since the coupling mechanism is configured to transmit torque as a tensile load, it is possible to suppress or prevent the compression mechanism from acting excessively on the coupling mechanism and reducing the durability. Can do. Further, since it is possible to suppress or prevent the component force of the load acting on the coupling mechanism from acting in the direction of pressing the pressing plate in the axial direction, the controllability of the frictional force between the pressing plate and the clutch disk is reduced. This can be suppressed or prevented.

  In addition, when the clutch disk and the pressing plate are in contact with each other to transmit torque, the first fixing portion in which the connecting mechanism is connected to one of the clutch cover and the pressing plate, and the first fixing portion in the circumferential direction. The second fixing portion and the third fixing portion, in which the connecting mechanism is connected to the other of the clutch cover and the pressing plate on both sides of the fixing portion, are configured to be in the same position in the axial direction, thereby compressing the connecting mechanism. Or even if it is a case where a tensile load acts, it can suppress or prevent that the component of the load which acts on a connection mechanism acts in the direction in which a press plate presses a clutch disk. As a result, it is possible to suppress or prevent a decrease in controllability of the frictional force between the pressing plate and the clutch disk.

  A connection mechanism is connected to the first fixing portion and the second fixing portion and is elastically deformed in the axial direction; and a fourth connecting mechanism is connected to the first fixing portion and the third fixing portion and is elastically deformed in the axial direction. In the case where the third connecting portion and the fourth connecting portion are formed to have the same length, the friction that contacts the clutch disk in the pressing plate when the pressing plate moves in the axial direction. It is possible to suppress or prevent the surface from inclining. As a result, it is possible to suppress or prevent a torsional load or the like from acting on a portion connected to the pressing plate in the connection mechanism, and thus it is possible to suppress or prevent a decrease in durability of the connection mechanism.

  Further, when the first connecting portion includes the first bent portion protruding in the axial direction and the second connecting portion includes the second bent portion protruding in the axial direction, the pressing plate moves in the axial direction. In addition, each bent portion is elastically deformed. Therefore, it is possible to suppress or prevent the pressing plate from moving in the circumferential direction as each bent portion is elastically deformed. Therefore, the pressing plate and the clutch disk can be sufficiently separated. As a result, it is possible to suppress or prevent the pressure plate and the clutch disk from unintentionally contacting and transmitting torque. Further, by configuring in such a manner, it is possible to suppress or prevent relative movement in the circumferential direction between the member that presses the pressing plate with a load that changes the frictional force between the pressing plate and the clutch disk and the pressing plate. it can. As a result, it is possible to suppress or prevent a decrease in durability of the pressing plate.

  Furthermore, the amount of protrusion in the axial direction relative to the length in the longitudinal direction of one bent portion that transmits a relatively large torque as a tensile load is smaller than the amount of protrusion in the axial direction relative to the length in the longitudinal direction of the other bent portion. By doing, the rigidity with respect to a tensile load can be made high. As a result, it is possible to suppress or prevent a decrease in durability of the coupling mechanism.

  A fourth fixing portion that connects the first connecting portion and the second connecting portion to the pressing plate is provided, and when the pressing plate moves in the axial direction, the fourth fixing portion is elastically deformed so as to move only in the axial direction. In the case where the fifth fixing portion is provided with a sixth connecting portion that is elastically deformed so that the fourth fixing portion moves only in the axial direction when the pressing plate moves in the axial direction, When moving in the direction, it is possible to suppress or prevent simultaneous movement in the circumferential direction. Therefore, the pressing plate and the clutch disk can be sufficiently separated. As a result, it is possible to suppress or prevent the pressure plate and the clutch disk from unintentionally contacting and transmitting torque. Further, by configuring in such a manner, it is possible to suppress or prevent relative movement in the circumferential direction between the member that presses the pressing plate with a load that changes the frictional force between the pressing plate and the clutch disk and the pressing plate. it can. As a result, it is possible to suppress or prevent a decrease in durability of the pressing plate.

  A fixing means for connecting the coupling mechanism and the clutch cover or the pressing plate is provided, and the pressing plate is axially provided by providing the connecting mechanism so as to be able to move relative to the fixing means in the circumferential direction of the pressing plate. At the same time, it is possible to suppress or prevent the pressing plate from moving in the circumferential direction at the same time. Therefore, the pressing plate and the clutch disk can be sufficiently separated. As a result, it is possible to suppress or prevent the pressure plate and the clutch disk from unintentionally contacting and transmitting torque. Further, by configuring in such a manner, it is possible to suppress or prevent relative movement in the circumferential direction between the member that presses the pressing plate with a load that changes the frictional force between the pressing plate and the clutch disk and the pressing plate. it can. As a result, it is possible to suppress or prevent a decrease in durability of the pressing plate.

  A second plate member having a second through hole formed at one end thereof, and a third plate having a third through hole formed at one end portion thereof and adjacent to the second plate member in the circumferential direction And a second fixing member that is inserted into the second through hole and the third through hole and connects the second plate member and the third plate member to either the clutch cover or the pressing plate. The fixing means is provided, and in a state where torque is not input to either the second plate member or the third plate member, a gap between the inner wall surface on the third plate member side in the second through hole and the second fixing member is formed. When the third through hole is configured to be smaller than the gap between the inner wall surface facing the inner wall surface on the second plate member side and the second fixing member, one plate member transmits torque as a tensile load. . In other words, it is possible to suppress or prevent the compressive load from acting on the other plate member. As a result, it is possible to suppress or prevent a decrease in durability of the coupling mechanism.

It is sectional drawing for demonstrating the effect | action of the clutch which concerns on this invention, and is a figure which shows the state into which the torque is input from the clutch cover to the pressure plate so that the rotation speed of an output side rotation member may be increased. FIG. 2 is a cross-sectional view showing a state in which torque is input from the pressure plate to the clutch cover so as to increase the rotation speed of the input side rotation member in the clutch shown in FIG. 1. It is sectional drawing for demonstrating an example of the structure of the clutch which concerns on this invention, and is a figure which shows the state which the clutch is transmitting torque, (a) is formed so that the arch part might protrude in the clutch cover side An example is shown, (b) is a figure which shows the example in which the arch part protruded and formed in the pressure plate side. It is sectional drawing which shows the state which has interrupted transmission of torque with the clutch shown to Fig.3 (a). It is a side view for demonstrating an example of the structure of the clutch which concerns on this invention. It is a side view for demonstrating the other structural example of the clutch which concerns on this invention. It is sectional drawing which follows the VII-VII line in FIG. It is sectional drawing for demonstrating the further another structural example of the clutch which concerns on this invention, and is a figure which shows the state which is transmitting the torque. FIG. 9 is a cross-sectional view showing a state where the clutch shown in FIG. 8 is blocking transmission of torque. FIG. 6 is a cross-sectional view for explaining an example of a configuration of a clutch that can transmit torque only by one strap plate, and torque is input from the pressure plate to the clutch cover so as to increase the rotation speed of the input side rotation member. FIG. FIG. 11 is a cross-sectional view illustrating a state in which torque is input from the clutch cover to the pressure plate so as to increase the rotation speed of the output side rotation member in the clutch illustrated in FIG. 10. It is a figure for demonstrating the rigidity of a strap plate. It is sectional drawing for demonstrating an example of a structure of the clutch which can improve the rigidity of one connection part. It is sectional drawing for demonstrating an example of the structure which provided the several strap plate continuously. It is sectional drawing for demonstrating the other structural example which provided the several strap plate continuously. It is sectional drawing for demonstrating the further another structural example which provided the several strap plate continuously. It is sectional drawing for demonstrating an example of a structure of the clutch provided with the strap plate formed cyclically | annularly. It is a gear train diagram for explaining an example of a vehicle that can be equipped with a clutch according to the present invention. FIG. 6 is a gear train diagram for explaining another example of a vehicle in which the clutch according to the present invention can be mounted.

  An example of the configuration of the clutch according to the present invention is shown in FIG. 5 shows a side view as seen from the output side of the clutch 1, and the upper right portion shown in FIG. 5 shows the internal configuration of the clutch cover 2 corresponding to the rotating body in the present invention. The clutch 1 shown in FIG. 5 is a dry clutch that transmits torque to the friction surface without oil. The clutch according to the present invention transmits a torque as a tensile load so as to increase the rotational speed of the input side rotating member, and transmits a torque as a tensile load so as to increase the rotational speed of the output side rotating member. It is only necessary to include a connecting mechanism having a portion, and the configuration of other members can be configured in the same manner as a conventionally known clutch. Therefore, here, members other than the configuration of the strap plate corresponding to the connection mechanism in the present invention will be briefly described. A clutch 1 shown in FIG. 5 has a clutch cover 2 formed in an annular shape, and an inner peripheral portion 3 of the clutch cover 2 is formed so as to protrude to the output side in the axial direction. Further, the outer peripheral portion 4 of the clutch cover 2 is formed to be bent toward the input side at a predetermined interval in the circumferential direction, and the bent portion 5 and the input side rotating member are integrated by a rivet 6. ing. That is, the clutch cover 2 is configured to rotate integrally with the input side rotation member.

  An annular pressure plate (pressing plate) 7 configured to be movable in the axial direction is provided on the input side of the clutch cover 2. The pressure plate 7 is a member for sandwiching the clutch disk that rotates integrally with the output side rotating member with the input side rotating member. Therefore, the pressure plate 7 is disposed to face the input side rotating member, and the clutch disk is disposed between the pressure plate 7 and the input side rotating member.

  Further, a diaphragm spring 8 is provided for pressing the pressure plate 7 toward the clutch disc. The diaphragm spring 8 is formed in a ring shape, and slits 10 are formed radially on the inner peripheral portion 9 thereof. The outer peripheral portion 11 of the diaphragm spring 8 is configured to move integrally with the pressure plate 7 in the axial direction. Further, the inner peripheral portion 9 of the diaphragm spring 8 is connected to a release mechanism (not shown), and the release mechanism presses the inner peripheral portion 9 of the diaphragm spring 8 in the axial direction so as to clamp the clutch disc. It is comprised so that it may fall. That is, the outer peripheral part 11 connected with the pressure plate 7 moves to the output side in the axial direction by pressing the inner peripheral part 9 of the diaphragm spring 8. Depending on the relationship between the position of the force point that presses the diaphragm spring 8 and the position of the fulcrum where the diaphragm spring 8 bends, the direction of the load that presses the inner peripheral portion 9 of the diaphragm spring 8 by the release mechanism is It may be the input side or the output side. Further, the clutch according to the present invention is not limited to the one configured to press the pressure plate 7 toward the clutch disk side by the diaphragm spring 8 as described above, but the diaphragm spring 8 separates the pressure plate 7 from the clutch disk. In this way, the clutch may be configured to apply an elastic force. In the case of the clutch configured as described above, a mechanism for engaging the pressure plate 7 and the clutch disk may be provided.

  In addition, the clutch 1 shown in FIG. 5 is provided with three strap plates 12 connected to the clutch cover 2 and the pressure plate 7 in the circumferential direction. The strap plate 12 is formed by laminating a plurality of plate members, and is configured to apply an elastic force in a direction in which the pressure plate 7 is separated from the clutch disk. The strap plate 12 is configured to transmit torque from the clutch cover 2 to the pressure plate 7.

  Here, a specific configuration of the strap plate 12 shown in FIG. 5 will be described. The strap plate 12 shown in FIG. 5 has a side face of the pressure plate 7 facing the clutch cover 2 and a central portion 13 of the strap plate 12 fixed by a rivet 14 and an inner wall surface of the clutch cover 2 facing the pressure plate 12. Both ends 15 and 16 of the strap plate 12 are fixed by rivets 17 and 18. The central portion 13 where the strap plate 12 is fixed to the pressure plate 7 and both end portions 15 and 16 where the strap plate 12 is fixed to the clutch cover 2 are provided at the same position in the circumferential direction of the clutch 1. Yes. In other words, the distance from the central axis of the clutch 1 to the central portion 13 and both end portions 15 and 16 is the same. The central portion 13 corresponds to the first fixing portion in the present invention, and both end portions 15 and 16 correspond to the second fixing portion and the third fixing portion in the present invention.

  FIG. 3A schematically shows a cross-sectional view taken along line III-III in FIG. In the example shown in FIG. 3A, the pressure plate 7 and the clutch disk 19 are in contact with each other. In the example shown in FIG. 3A, first and second arch portions 20 projecting toward the clutch cover 2 in the axial direction on both sides across the central portion 13 where the strap plate 12 and the pressure plate 7 are coupled, 21 is formed. The first arch portion 20 and the second arch portion 21 are formed with the same amount of protrusion in the axial direction and the length in the longitudinal direction. That is, the first arch portion 20 and the second arch portion 21 are formed to have the same radius of curvature. Further, in the example shown in FIG. 3A, when the pressure plate 7 moves in the axial direction, the position of the central portion 13 does not move in the circumferential direction, in other words, the central portion 13 is only in the axial direction. The length from the central portion 13 to the one end portion 15 and the length from the central portion 13 to the other end portion 16 are formed to be the same so as to move. When the pressure plate 7 is in contact with the clutch disk 19 and transmits torque, the central portion 13 and the end portions 15 and 16 are configured to have the same axial position. Note that the case where the pressure plate 7 and the clutch disk 19 transmit torque may be during half-engagement where torque is transmitted while slipping, and torque is transmitted at the same rotational speed. It may be at the time of complete engagement. That is, the central portion 13 and the both end portions 15 and 16 are in the same position in the axial direction in any state from the half-engagement where the clutch 1 starts to transmit torque to the complete engagement where torque is completely transmitted. It is comprised so that it may become. The first arch portion 20 corresponds to the third connecting portion, the fifth connecting portion, or the first bent portion in the present invention, and the second arch portion 21 corresponds to the fourth connecting portion, the sixth connecting portion, or the second in the present invention. It corresponds to a bent part.

  Further, FIG. 4 shows a state in which the transmission of torque is blocked by the separation of the pressure plate 7 and the clutch disk 19. When the pressure plate 7 is separated from the clutch disk 19 as in the example shown in FIG. 4, the central portion 13 moves in the circumferential direction because the arch portions 20 and 21 of the strap plate 12 are bent and deformed in the axial direction. It is configured not to.

  Next, the operation of the clutch 1 configured as described above will be described. The above-described clutch 1 is configured such that the elastic force of the diaphragm spring 8 and the elastic force of the strap plate 12 act on the pressure plate 7, and the pressure plate 7 moves in the axial direction according to the difference between the elastic forces. Configured to move to. Specifically, when the elastic force of the diaphragm spring 8 is larger than the elastic force of the strap plate 12, the pressure plate 7 is pressed against the clutch disk 19 and moves. On the contrary, when the elastic force of the diaphragm spring 8 is smaller than the elastic force of the strap plate 12, the pressure plate 7 is separated from the clutch disk 19. Therefore, in the above-described example, the friction force between the pressure plate 7 and the clutch disk 19 is reduced by pressing the diaphragm spring 8 by the release mechanism to reduce the elastic force of the diaphragm spring 8. In other words, the transmission torque capacity of the clutch 1 is controlled by controlling the load with which the release mechanism presses the diaphragm spring 8. Therefore, when the diaphragm spring 8 is pressed by the release mechanism and the elastic force of the diaphragm spring 8 becomes smaller than the elastic force of the strap plate 12, the pressure plate 7 is separated from the clutch disk 19 as shown in FIG. When the pressure plate 7 is separated from the clutch disk 19 in this way, the frictional force acting on the clutch disk 19 becomes “0”. As a result, the clutch 1 is released and the torque of the input side rotating member and the output side rotating member is reduced. Transmission is interrupted.

  On the contrary, when the release mechanism does not press the diaphragm spring 8 or when the release mechanism presses the diaphragm spring 8, the pressing force is relatively small, and the elastic force of the diaphragm spring 8 is the elasticity of the strap plate 12. When the force is larger than the force, the pressure plate 7 and the clutch disc 19 come into contact as shown in FIG. As a result, torque can be transmitted between the input side rotating member and the output side rotating member. Note that the transmission torque capacity between the input side rotating member and the output side rotating member changes according to the pressing force acting on the pressure plate 7.

  As shown in FIG. 3A, when the pressure plate 7 and the clutch disk 19 are in contact with each other to transmit torque, a compressive load and a tensile load act on the strap plate 12. FIG. 1 shows the direction of the load acting on each member by arrows when torque is being input from the input side rotating member to the clutch 1 so that the number of rotations of the output side rotating member is increased. In the example shown in FIG. 1, torque is input from the left side in the figure to the clutch cover 2 connected to the input side rotating member. On the other hand, the clutch disk 19 connected to the output side rotating member has its rotational speed increased by the torque transmitted from the clutch cover 2, and therefore, in the example shown in FIG. As a reaction force of the input torque, a load acts from the right side in the figure. As a result, a compressive load acts on the first connecting portion 22 between the central portion 13 and the one end portion 15, and pulls on the second connecting portion 23 between the central portion 13 and the other end portion 16. A load acts. In other words, the first connecting portion 22 transmits torque from the clutch cover 2 to the pressure plate 7 as a compressive load, and the second connecting portion 23 transmits torque from the clutch cover 2 to the pressure plate 7 as a tensile load.

  On the contrary, when the torque is input from the output side rotating member to the clutch 1 so that the rotational speed of the input side rotating member increases, the direction of the load acting on the strap plate 12 is reversed. FIG. 2 shows the direction of the load acting on each member with an arrow when torque is input to the clutch 1 from the output side rotating member so that the number of rotations of the input side rotating member increases. In the example shown in FIG. 2, the right torque shown in the figure is input to the clutch disk 19. Therefore, torque is transmitted to the pressure plate 7 in contact with the clutch disk 19 on the right side shown in the figure. On the other hand, since the input side rotating member and the inertia force coupled to the input side rotating member act on the clutch cover 2, a reaction force that opposes the torque transmitted from the clutch disk 19 acts, and the reaction force is It becomes the left side shown in the figure. As a result, a tensile load acts on the first connecting portion 22, and a compressive load acts on the second connecting portion 23. In other words, the first connecting portion 22 transmits torque from the pressure plate 7 to the clutch cover 2 as a tensile load, and the second connecting portion 23 transmits torque from the pressure plate 7 to the clutch cover 2 as a compressive load.

  In the clutch 1 configured as described above, even when torque is input from the input side rotating member so as to increase the rotational speed of the output side rotating member, the output side rotating member rotates the input side rotating member. Even when torque is input so as to increase the number, any one of the connecting portions 22 (23) in the strap plate 12 transmits the torque as a tensile load. Therefore, the compressive load acting on the other connecting portion 23 (22) in the strap plate 12 can be offset. In other words, it is possible to suppress or prevent an excessive compression load from acting on the strap plate 12, and as a result, it is possible to suppress or prevent the durability of the strap plate 12 from being lowered.

  Moreover, in the example mentioned above, the arch parts 20 and 21 are formed in each connection part 22 and 23, respectively. By forming the arch portions 20 and 21 in the strap plate 12 in this way, the arch portions 20 and 21 are bent and deformed when the pressure plate 7 is in contact with the clutch disk 19. In other words, there is no displacement in the axial direction between the first arch portion 20 and the one end portion 15 or between the second arch portion 21 and the other end portion 16. That is, the arch portions 20 and 21 are bent and deformed in the axial direction with a boundary position between the arch portions 20 and 21 as a fulcrum as a fulcrum. When the respective arch portions 20 and 21 are bent and deformed and the rigidity of the first connecting portion 22 and the second connecting portion 23 is the same, the central portion 13 does not move in the circumferential direction and is pressurized. The plate 7 approaches or separates from the clutch disk 19. Therefore, it is possible to suppress or prevent the axial displacement of the strap plate 7 from being reduced by the center portion 13 connecting the strap plate 12 and the pressure plate 7 being displaced in the circumferential direction. In other words, it is possible to suppress or prevent a decrease in the amount by which the pressure plate 7 is displaced in the axial direction. That is, the pressure plate 7 and the clutch disk 19 can be sufficiently separated. As a result, it is possible to suppress or prevent the occurrence of drag loss due to unintended contact between the pressure plate 7 and the clutch disk 19 and transmission of torque. In addition, it is possible to suppress or prevent wear caused by the contact position between the pressure plate 7 and the diaphragm spring 8 moving in the circumferential direction, thereby suppressing or preventing the durability of the pressure plate 7 from being lowered. be able to.

  3A shows an example in which the arch portions 20 and 21 are formed so as to protrude toward the clutch cover 2 side. However, the main point is that the arch portions 20 and 21 are bent and deformed. What is necessary is just to be able to suppress or prevent that 13 displaces in the circumferential direction. Therefore, as shown in FIG. 3B, the arch portions 20 and 21 may be formed so as to protrude to the pressure plate 7 side.

  Further, when the pressure plate 7 and the clutch disk 19 are in contact with each other to transmit torque, the central portion 13 and the end portions 15 and 16 are configured to have the same position in the axial direction. The component force of the compressive load and the tensile load acting on the portions 22 and 23 does not act so as to move the pressure plate 7 in the axial direction. Therefore, it is possible to suppress or prevent the component force from acting on the pressure plate 7 and changing the load that presses the clutch disk 19. As a result, it is possible to suppress or prevent the controllability of the frictional force between the pressure plate 7 and the clutch disk 19, in other words, the transmission torque capacity of the clutch 1.

  Further, by configuring the arch portions 20 and 21 to have the same length, it is possible to suppress or prevent the pressure plate 7 from moving only in the axial direction, in other words, from moving in the circumferential direction. As a result, it is possible to suppress or prevent the friction surface of the pressure plate 7 facing the clutch disk 19 from being inclined. Therefore, since it is possible to suppress or prevent the torsional load and the like from acting on the central portion 13 where the strap plate 12 and the pressure plate 7 are connected, it is possible to suppress or prevent the durability of the strap plate 12 from being lowered. be able to.

  Further, the distance between the central axis of the clutch 1 and the central portion 13 and both end portions 15 and 16 is formed to be the same. Therefore, as the distance between the central portion 13 and the one end portion 15 and the distance between the central portion 13 and the other end portion 15 are shortened, the longitudinal direction of the first connecting portion 22 and the second connecting portion 23 and the central portion 13 are reduced. And the tangential direction of the arc connecting the both end portions 15 and 16 can be made substantially the same. As a result, most of the load transmitted by the strap plate 12 acts in the longitudinal direction of the connecting portions 22 and 23. Therefore, since it can suppress or prevent that a load acts on the width direction of the strap plate 12, it can suppress or prevent that the durability of the strap plate 12 falls.

  Note that the clutch according to the present invention increases the rotational speed of the output-side rotating member even when torque is transmitted from the clutch cover 2 to the pressure plate 7 so as to increase the rotational speed of the input-side rotating member. Even when the torque is transmitted from the pressure plate 7 to the clutch cover 2 as described above, any one of the coupling portions in the coupling mechanism may be configured to transmit the torque as a tensile load. Therefore, the arch portions 20 and 21 may not be formed as shown in FIG. Moreover, the 1st connection part 22 and the 2nd connection part 23 are not restricted to what was integrated. Specifically, when torque is input to the clutch 1 from the input side rotating member so as to increase the number of rotations of the output side rotating member, a strap plate that transmits the torque as a tensile load is provided, and the input side rotation When torque is input to the clutch 1 from the output side rotating member so as to increase the number of rotations of the member, another strap plate that transmits the torque as a tensile load may be provided. That is, a plurality of strap plates may be provided and at least one of the strap plates may be configured to transmit torque as a tensile load. Furthermore, the strap plate 12 and the pressure plate are not limited to the configuration in which both ends 15 and 16 for connecting the clutch cover 2 and the pressure plate 7 are provided on both sides of the central portion 13 for connecting the strap plate 12 and the pressure plate 7. 7 may be fixed at two locations, and the strap plate 12 and the clutch cover 2 may be connected between the fixing portions in the circumferential direction.

  6 and 7 show an example of the clutch 1 configured as described above. FIG. 7 schematically shows a cross-sectional view taken along line VII-VII in FIG. Further, the same configurations as those in FIGS. 3 to 5 are denoted by the same reference numerals, and the description thereof is omitted. In the example shown in FIGS. 6 and 7, a first strap plate 24 and a second strap plate 25 having one end connected to the clutch cover 2 and the other end connected to the pressure plate 7 are provided. Yes. In the example shown in FIG. 7, the left end portion of the first strap plate 24 and the pressure plate 7 are connected, and the right end portion and the clutch cover 2 are connected. Further, the left end portion of the second strap plate 25 and the clutch cover 2 are connected, and the right end portion and the pressure plate 7 are connected. That is, the first strap plate 24, the second strap plate 25, and the pressure plate 7 are connected to each other with a portion connecting the clutch cover 2 and the first strap plate 24 and the second strap plate 25 in the circumferential direction. Yes. In the example shown in FIGS. 6 and 7, the first strap plate 24 and the second strap plate 25 are configured as a pair of connecting members, and three pairs of the connecting members are provided in the circumferential direction.

  When the clutch cover 2 and the pressure plate 7 are connected in this manner, when torque is input from the input side rotating member so as to increase the rotation speed of the output side rotating member, the first strap plate 24 and One strap plate 24 (25) of the second strap plate 25 transmits torque to the pressure plate 7 as a tensile load. On the other hand, when torque is transmitted from the output side rotating member so as to increase the rotational speed of the input side rotating member, the other strap plate 25 (24) transmits torque to the pressure plate 7 as a tensile load. To do. Therefore, similarly to the example shown in FIG. 1, even when torque is input from the input side rotating member so as to increase the rotational speed of the output side rotating member, the rotation of the input side rotating member from the output side rotating member is performed. Even when the torque is input so as to increase the number, one of the strap plates 24 (25) transmits the torque to the pressure plate 7 as a tensile load. Therefore, when the clutch 1 is transmitting torque, a tensile load can be applied to the connecting member that connects the clutch cover 2 and the pressure plate 7. Therefore, the compressive load acting on either one of the strap plates 24 (25) can be offset. In other words, it is possible to suppress or prevent an excessive compression load from acting on the strap plate 24 (25), and as a result, it is possible to suppress or prevent a decrease in durability of the strap plate 24 (25). it can.

  In the example shown in FIGS. 1 to 4, the example in which the arch portions 20 and 21 are formed on the strap plate 7 has been described in order to suppress or prevent the pressure plate 7 from moving in the circumferential direction. In short, it is only necessary to suppress or prevent the elastic force of the strap plate 12 from acting in the circumferential direction. FIGS. 8 and 9 show another example configured to suppress or prevent the elastic force of the strap plate 12 from acting in the circumferential direction. 8 shows a state where the clutch disk 19 and the pressure plate 7 are in contact with each other to transmit torque. FIG. 9 shows a state where the clutch disk 19 and the pressure plate 7 are separated from each other to interrupt transmission of torque. It shows the state. Further, the same components as those in FIGS. 1 to 4 are denoted by the same reference numerals, and the description thereof is omitted. In the example shown in FIGS. 8 and 9, a third strap plate 26 having one end connected to the clutch cover 2 and the other end connected to the pressure plate 7, and one end connected to the pressure plate 7. A fourth strap plate 27 is provided which is connected and has the other end connected to the clutch cover 2. Further, a first through hole 28 having a long hole shape is formed at the other end portion of the third strap plate 26, and a second through hole having a long hole shape is formed at the one end portion of the fourth strap plate 27. A hole 29 is formed. The rivets 30 are inserted into the through holes 28 and 29 so that the pressure plate 7 and the strap plates 26 and 27 can move together in the axial direction. The rivet 30 corresponds to the fixing means in the present invention, the third strap plate 26 corresponds to the first plate member or the second plate member in the present invention, and the fourth strap plate 27 corresponds to the third plate member in the present invention. Equivalent to.

  By forming the through holes 28 and 29 in the strap plates 26 and 27 and connecting the strap plates 26 and 27 and the pressure plate 7 in this manner, the inner wall surface of the through hole and the outer peripheral surface of the rivet 30 are formed. There is a gap. Therefore, the other end of the third strap plate 26 and the rivet 30 can move relative to each other in the circumferential direction, and the one end of the fourth strap plate 27 and the rivet 30 can move in the circumferential direction. It can move relatively. Therefore, when the pressure plate 7 is separated from the clutch disk 19, it is possible to suppress or prevent the circumferential load from acting on the pressure plate 7 from the strap plates 26 and 27. In other words, only the load in the direction of moving the pressure plate 7 in the axial direction acts from the strap plates 26 and 27. As a result, the pressure plate 7 can be suppressed or prevented from moving in the circumferential direction.

  A through hole is formed at one end of the third strap plate 26, and the third strap plate 26 and the clutch cover 2 are connected to each other by a rivet having an outer diameter smaller than the inner diameter of the through hole. A through hole is formed at the other end of the four strap plate 27, and the fourth strap plate 27 and the clutch cover 2 are connected by a rivet having an outer diameter smaller than the inner diameter of the through hole. Also good. That is, a through hole is formed in a portion where the strap plate is connected to the clutch cover 2 or the pressure plate 7, and the strap plate and the clutch cover 2 or the pressure plate 7 are connected by a fixing member having an outer diameter smaller than the inner diameter of the through hole. What is necessary is just to comprise so that it may connect.

  Further, in a state where no torque is input to each strap plate 26, 27, the position of the inner wall surface on the front end side in the first through hole 28 is the inner wall surface on the side connected to the clutch cover 2 in the second through hole 29. The position of the inner wall surface on the distal end side in the second through hole 29 is more than the position of the inner wall surface on the side connected to the clutch cover 2 in the first through hole 28. By being configured to approach the rivet 30, torque is transmitted as a tensile load to the pressure plate 7 only by one of the strap plates 26 (27). FIGS. 10 and 11 show the state in which the strap plates 26 and 27 configured as described above transmit torque. FIG. 10 shows a state in which torque is input from the input-side rotating member so as to increase the rotational speed of the output-side rotating member, and FIG. 11 shows that the rotational speed of the input-side rotating member is increased. Fig. 5 shows a state in which torque is inputted from the output side rotating member.

  As shown in FIG. 10, when torque is input from the input side rotating member so as to increase the rotation speed of the output side rotating member, the inner wall surface of the fourth strap plate 27 and the outer peripheral surface of the rivet 30 are The inner wall surface of the third strap plate 26 and the outer peripheral surface of the rivet 30 are not in contact with each other. That is, torque is transmitted only by the fourth strap plate 27. Accordingly, a tensile load acts on the fourth strap plate 27 and no longitudinal load acts on the third strap plate 26. Further, as shown in FIG. 11, when torque is input from the output-side rotating member so as to increase the rotation speed of the input-side rotating member, the inner wall surface of the third strap plate 26 and the outer peripheral surface of the rivet 30 And the inner wall surface of the fourth strap plate 27 and the outer peripheral surface of the rivet 30 are not in contact with each other. That is, torque is transmitted only by the third strap plate 26. Accordingly, a tensile load acts on the third strap plate 26 and a longitudinal load does not act on the fourth strap plate 27. Therefore, by configuring as described above, only one of the strap plates 26 (27) transmits torque as a tensile load and suppresses or prevents the compressive load from acting on the other strap plate 27 (26). can do. As a result, it is possible to suppress or prevent the durability of the strap plates 26 and 27 from decreasing. Furthermore, since it is possible to suppress or prevent the compressive load from acting on the strap plates 26 and 27, the controllability of the frictional force between the pressure plate 7 and the clutch disk 19, that is, the transmission torque capacity of the clutch 1 is reduced. Can be suppressed or prevented.

  Furthermore, each of the strap plates 12, 24, 25, 26, and 27 described above is preferably configured such that the rigidity against a tensile load is larger than the rigidity against a compressive load as shown in FIG. In other words, it is preferable that the structure be easily distorted when a load is applied in the compression direction. The horizontal axis in FIG. 12 shows the amount of strain, the right side shows the amount of strain in the tensile direction, and the left side shows the amount of strain in the compression direction. The vertical axis in FIG. 12 indicates the load acting on the strap plate, the upper side indicates the load in the tensile direction, and the lower side indicates the load in the compression direction. Furthermore, as shown in FIG. 12, the rigidity in the pulling direction and the rigidity in the compression direction can be changed depending on the shape and material of the strap plate.

  Thus, when torque is transmitted by the strap plates 12, 24, 25, 26, and 27 by making the rigidity with respect to the tensile load larger than the rigidity with respect to the compression load, the torque is applied to the strap plate or the connecting portion on which the tensile load acts. The ratio at which the torque is transmitted is larger than the ratio at which the torque is transmitted at the strap plate or the connecting portion to which the compressive load acts. As a result, it is possible to suppress or prevent an excessive compressive load from acting on the strap plate, so that the durability of the strap plate can be improved.

  Further, the magnitude of torque input from the output-side rotating member to the clutch 1 so as to increase the rotational speed of the input-side rotating member, and the input-side rotating member from the input-side rotating member to the clutch 1 so as to increase the rotational speed of the output-side rotating member. When the magnitude of the input torque is different, it is preferable to increase the rigidity of the portion of the strap plate 12 to which the tensile load acts when a relatively large torque is input to the clutch 1. FIG. 13 shows an example of the configuration of the strap plate 12 configured as described above. The configuration shown in FIG. 13 is obtained by changing the radius of curvature of the first arch portion 20 shown in FIG. 1, and the other configurations can be configured in the same manner as the configuration shown in FIG. Further, in FIG. 13, the torque is applied so that the clutch disk 19 rotates to the left side, and the rotational speed of the clutch cover 2 from the clutch disk 19 to the right side in the drawing through the pressure plate 7 and the strap plate 12 increases. In this example, a large tensile load is applied to the first arch portion 20 of the strap plate 12 when transmitting the torque.

  In the example shown in FIG. 13, the radius of curvature of the first arch portion 20 is formed larger than the radius of curvature of the second arch portion 21. Further, the amount of the first arch portion 20 and the second arch portion 21 projecting toward the clutch cover 2 in the axial direction is the same. In other words, the protruding amount in the axial direction with respect to the length in the longitudinal direction of the first arch portion 20 is configured to be smaller than the protruding amount in the axial direction with respect to the length in the longitudinal direction of the second arch portion 21. Accordingly, the length from one end 15 to the central portion 13 is configured to be longer than the length from the central portion 13 to the other end 16. Thus, by making the radius of curvature of the first arch portion 20 larger than that of the second arch portion 21, the rigidity with respect to the tensile load in the first arch portion 20 becomes larger than the rigidity with respect to the tensile load in the second arch portion 21. Therefore, the durability of the strap plate 12 can be improved.

  In FIG. 13, an example in which the first arch portion 20 and the second arch portion 21 are configured to have different rigidity depending on the shape of the strap plate 12 has been described. The material of the part 21 may be changed to vary the rigidity. Further, when two strap plates are connected to the pressure plate 7, the strap plate to which a relatively large tensile load acts may be configured to have higher rigidity.

  Furthermore, in the configuration shown in FIG. 1, the example in which three strap plates are provided with a predetermined interval in the circumferential direction has been described. However, as shown in FIGS. You may provide continuously without leaving. In the example illustrated in FIG. 16, an example in which the arch portions 20 and 21 are not provided is illustrated. Specifically, as shown in FIG. 14, one end of the sixth strap plate 31 and one end of the seventh strap plate 32 are connected to the clutch cover 2 by one rivet 33. May be. Further, as shown in FIG. 15, the center portion of the eighth strap plate 34 is connected to the clutch cover 2, and both end portions of the eighth strap plate 34 are connected to the pressure plate 7 and adjacent to the eighth strap plate 34. One end of the matching ninth strap plate 35 may be integrally connected to a portion where the eighth strap plate 34 is connected to the pressure plate 7. Further, as shown in FIG. 16, a plurality of strap plates 36, 36 configured such that one end is connected to the clutch cover 2 and the other end is connected to the pressure plate 7 are arranged in the circumferential direction. You may provide continuously. Each of the strap plates in FIGS. 14 and 15 is configured in the same manner as the strap plate 12 shown in FIG.

  Further, in each of the above configuration examples, an example in which a plurality of strap plates are provided has been described. However, as shown in FIG. 17, the strap plate 37 is formed in an annular shape and connected to the clutch cover 2 and the pressure plate 7 at a plurality of locations. You may comprise. In that case, it is preferable to provide the location connected to the clutch cover 2 and the location connected to the pressure plate 7 alternately in the circumferential direction.

  Next, an example of a vehicle that can be mounted with the clutch configured as described above will be described. FIG. 18 is a gear train diagram for explaining an example thereof. The vehicle shown in FIG. 18 includes the clutch 1 that can be the subject of the present invention on the output shaft 39 of the engine 38, and the first motor / generator 41 is provided on the output shaft 40 of the clutch 1. Drive wheels 45 are connected to the output shaft 42 of the first motor / generator 41 via another clutch 43 and a transmission 44. FIG. 19 shows another configuration of the vehicle that can be equipped with the clutch. In the example shown in FIG. 19, a dual clutch transmission 48 is connected to the output shaft 47 of the engine 46 via the clutch 1 that can be the subject of the present invention, and a differential gear 50 is connected to the output shaft 49 of the dual clutch transmission 48. The drive wheels 51 and 51 are connected via the. Furthermore, a second motor / generator 52 is connected to the dual clutch transmission 48. The vehicle configured as shown in FIGS. 18 and 19 can travel by outputting torque from the first motor / generator 41 or the second motor / generator 52, and at that time, the clutch 1 is released. As a result, power loss due to the accompanying rotation of the engine 38 (46) can be reduced. That is, the engine 38 (46) can be stopped when torque is output only from the motor generator 41 (52). Further, the engine 38 (46) and the motor / generator 41 (52) can output torque and travel. Further, the engine 38 (56) can be cranked by engaging the clutch 1 and outputting torque from the motor / generator 41 (52). Therefore, even if torque is transmitted from the input side so as to increase the rotation speed of the output side of the clutch 1 in order to suppress or prevent the durability of the clutch 1 from being lowered, the rotation on the input side Even when the torque is transmitted from the output side so as to increase the number, a tensile load acts on the strap plate.

  In FIGS. 18 and 19, an example in which torque is transmitted from the output side so as to increase the rotational speed of the input side of the clutch 1 by cranking the engine 38 (46) has been described. In short, any clutch may be used as long as torque is transmitted from the output side so as to increase the rotational speed of the input side of the clutch 1. Accordingly, when the engine brake is applied to the drive wheels, torque may be transmitted from the output side so as to increase the input side rotational speed. Therefore, as shown in FIGS. 18 and 19, the clutch according to the present invention can be mounted even in a vehicle other than a vehicle provided with a motor / generator for cranking the engine 38 (46) on the output side of the clutch 1. .

  DESCRIPTION OF SYMBOLS 1 ... Clutch, 2 ... Clutch cover, 7 ... Pressure plate, 8 ... Diaphragm spring, 12, 24, 25, 26, 27, 31, 32, 34, 35, 36, 37 ... Strap plate, 13 ... Center part, 14 , 17, 18, 30, 33 ... rivets, 15, 16 ... end, 19 ... clutch disc, 20, 21 ... arch, 22, 23 ... connecting part, 28, 29 ... through hole, 38, 46 ... engine, 41, 52: Motor generator.

Here, a specific configuration of the strap plate 12 shown in FIG. 5 will be described. The strap plate 12 shown in FIG. 5 has a side surface of the pressure plate 7 facing the clutch cover 2 and a central portion 13 of the strap plate 12 fixed by a rivet 14, and an inner wall surface of the clutch cover 2 facing the pressure plate 12. Both ends 15 and 16 of the strap plate 12 are fixed by rivets 17 and 18. Further, a central portion 13 the strap plate 12 is fixed to the pressure plate 7 and the end portions 15, 16 the strap plate 12 is fixed to the clutch cover 2, provided in the same position in the radial direction toward the clutch 1 Yes. In other words, the distance from the central axis of the clutch 1 to the central portion 13 and both end portions 15 and 16 is the same. The central portion 13 corresponds to the first fixing portion in the present invention, and both end portions 15 and 16 correspond to the second fixing portion and the third fixing portion in the present invention.

As shown in FIG. 3A, when the pressure plate 7 and the clutch disk 19 are in contact with each other to transmit torque, a compressive load and a tensile load act on the strap plate 12. FIG. 1 shows the direction of the load acting on each member by arrows when torque is being input from the input side rotating member to the clutch 1 so that the number of rotations of the output side rotating member is increased. In the example shown in FIG. 1, torque is input from the left side in the figure to the clutch cover 2 connected to the input side rotating member. On the other hand, the clutch disk 19 connected to the output side rotating member has its rotational speed increased by the torque transmitted from the clutch cover 2, and therefore, in the example shown in FIG. to a right or et operation in FIG as a reaction force of the input torque. As a result, a compressive load acts on the first connecting portion 22 between the central portion 13 and the one end portion 15, and pulls on the second connecting portion 23 between the central portion 13 and the other end portion 16. A load acts. In other words, the first connecting portion 22 transmits torque from the clutch cover 2 to the pressure plate 7 as a compressive load, and the second connecting portion 23 transmits torque from the clutch cover 2 to the pressure plate 7 as a tensile load.

Claims (13)

A clutch disk that is disposed opposite to the input side rotating member and is brought into frictional contact with the input side rotating member and transmits torque is coupled to the output side rotating member, and the clutch disk is elastically moved toward the input side rotating member. A pressing plate that presses the clutch disk is disposed on the opposite side of the input-side rotating member, and the rotating body that rotates integrally with the input-side rotating member and the pressing plate include the rotating body and the pressing plate. In the clutch connected by a connecting mechanism that transmits torque to the plate,
The connection mechanism increases a rotation speed of the input rotation member and a first connection portion that transmits torque from the rotating body to the pressing plate as a tensile load so as to increase the rotation speed of the output rotation member. And a second connecting portion for transmitting torque from the pressing plate to the rotating body as a tensile load.   The connection mechanism includes a first fixing portion connected to one of the rotating body and the pressing plate, and the other of the rotating body and the pressing plate on both sides of the first fixing portion in the circumferential direction. The clutch according to claim 1, further comprising a second fixing portion and a third fixing portion to be connected.   The first fixing portion, the second fixing portion, and the third fixing portion are configured to be in the same position in the axial direction when the clutch disk and the pressing plate are in contact with each other to transmit torque. The clutch according to claim 2, wherein the clutch is provided. The connection mechanism includes a third connection portion that is connected to the first fixing portion and the second fixing portion and elastically deforms in the axial direction, and is connected to the first fixing portion and the third fixing portion and in the axial direction. A fourth connecting part that elastically deforms,
The clutch according to claim 2 or 3, wherein the third connecting portion and the fourth connecting portion are formed to have the same length. The first connecting portion has a first bent portion protruding in the axial direction;
The clutch according to any one of claims 1 to 4, wherein the second connecting portion has a second bent portion protruding in an axial direction.   Torque transmitted from the rotating body to the pressing plate as a tensile load so as to increase the rotational speed of the output side rotating member, and from the pressing plate as a tensile load so as to increase the rotational speed of the input side rotating member. The amount of protrusion in the axial direction with respect to the length in the longitudinal direction of either one of the first bent portion and the second bent portion that transmits a large torque as the tensile load to the rotating body is the other. The clutch according to claim 5, wherein the clutch is formed smaller than a protruding amount in an axial direction with respect to a length in a longitudinal direction of the bent portion. A fourth fixing portion that connects the first connecting portion and the second connecting portion to the pressing plate;
The first connecting portion includes a fifth connecting portion that elastically deforms so that the fourth fixing portion moves only in the axial direction when the pressing plate moves in the axial direction,
The second connection part includes a sixth connection part that elastically deforms so that the fourth fixing part moves only in the axial direction when the pressing plate moves in the axial direction. The clutch in any one of thru | or 6. A fixing means for connecting the connecting mechanism and the rotating body or the pressing plate;
The clutch according to any one of claims 1 to 7, wherein the coupling mechanism is provided so as to be able to move relative to the fixing means in a circumferential direction of the pressing plate. The connection mechanism includes a first plate member in which a first through hole is formed at a position connected to the rotating body or the pressing plate,
The fixing means includes a first fixing member inserted into the first through hole,
The outer diameter of the first fixing member is smaller than the inner diameter of the first through hole so that the pressing plate can move relative to the first plate member in the circumferential direction. 9. The clutch according to claim 8, wherein The coupling mechanism includes a second plate member having a second through hole formed at one end thereof, a third through hole formed at one end portion thereof, and adjacent to the second plate member in the circumferential direction. A third plate member provided,
The fixing means is inserted into the second through hole and the third through hole to connect the second plate member and the third plate member to one of the rotating body and the pressing plate. Including two fixing members,
In a state where no torque is input to either the second plate member or the third plate member, a gap between the inner wall surface on the third plate member side and the second fixing member in the second through hole is formed. The clutch according to claim 8, wherein the clutch is configured to be smaller than a gap between an inner wall surface facing the inner wall surface on the second plate member side in the third through hole and the second fixing member.   Torque transmitted from the rotating body to the pressing plate as a tensile load so as to increase the rotational speed of the output side rotating member, and from the pressing plate as a tensile load so as to increase the rotational speed of the input side rotating member. The rigidity of any one of the first connecting part and the second connecting part that transmits a large torque as a tensile load to the rotating body is higher than the rigidity of the other connecting part. The clutch according to any one of claims 1 to 10, wherein the clutch is provided. The input side rotating member includes an output shaft of an engine mounted on a vehicle,
The clutch according to any one of claims 1 to 11, wherein the output-side rotating member is connected to a cranking unit that rotates the output shaft to crank the engine.   The clutch according to claim 12, wherein the cranking means includes a motor mounted on the vehicle.

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