WO2020110952A1 - Centrifugal clutch - Google Patents

Centrifugal clutch Download PDF

Info

Publication number
WO2020110952A1
WO2020110952A1 PCT/JP2019/045831 JP2019045831W WO2020110952A1 WO 2020110952 A1 WO2020110952 A1 WO 2020110952A1 JP 2019045831 W JP2019045831 W JP 2019045831W WO 2020110952 A1 WO2020110952 A1 WO 2020110952A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft member
clutch
clutch lever
centrifugal
shaft
Prior art date
Application number
PCT/JP2019/045831
Other languages
French (fr)
Japanese (ja)
Inventor
祐仁 嶌中
晃功 國田
Original Assignee
株式会社椿本チエイン
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社椿本チエイン filed Critical 株式会社椿本チエイン
Publication of WO2020110952A1 publication Critical patent/WO2020110952A1/en

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
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D43/18—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members with friction clutching members
    • 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
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D2043/145—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members the centrifugal masses being pivoting

Definitions

  • the present invention relates to a clutch that transmits the rotation of an input shaft to the output shaft side, and particularly to a centrifugal clutch that switches transmission and disconnection of power from an input shaft to an output shaft by centrifugal force.
  • clutches that transmit power from the input shaft to the output shaft side are arranged on the drive force transmission path of small drive devices such as small bikes, chainsaws, and engine-type radio-controlled helicopters, and various clutches are known. is there.
  • the centrifugal clutch described in Patent Document 1 has a first shaft member (input side rotating part 1) and a second shaft member (output side drum 5), and a first shaft member (input side rotating part 1). Is connected to a pair of clutch levers (friction shoes 2) and a centrifugal weight 7 via connection pins (support shafts 3). The pair of clutch levers (friction shoes 2) are connected to the second shaft member (output side). One end of each other is connected by a clutch spring 4 so as to urge the friction surface toward the drum 5). The pair of centrifugal weights 7 are urged by the weight springs 8 on their side surfaces in the direction in which the second shaft member (output side drum 5) is bound. Further, in the centrifugal weight 7, the cam surfaces 9 formed on the free end sides of each other are engaged with the detent spring 10 connected to the first shaft member (the input side rotating portion 1).
  • the centrifugal weight 7 also expands by gradually pushing back the detent spring 10 and the weight spring 8 by the centrifugal force, and when the engagement between the detent spring 10 and the cam surface 9 is released, a predetermined weight of the centrifugal weight 7 is obtained.
  • the engagement pin 11 provided at the position comes into contact with the clutch lever (friction shoe 2), disengages the clutch lever (friction shoe 2) from the second shaft member (output side drum 5), and the first shaft member (input side).
  • the power transmission from the rotating portion 1) to the second shaft member (output side drum 5) is released.
  • the disengagement timing of the clutch lever (friction shoe 2) can be changed.
  • the second shaft member M receives the driving force F1 in the rotational direction at the force point P and is pushed by the component force F2 of F in the central axis MS direction of the second shaft member M, and at the same time, the shoe CS.
  • a normal force (not shown) having the same magnitude as F2 and applied in the opposite direction is generated.
  • the clutch lever CS and the second shaft member M are in contact with each other at the force point P, if the static friction coefficient between the clutch lever CS and the second shaft member M is ⁇ , the maximum static friction force is ⁇ F2. is there. Therefore, ⁇ F2>F1 Then, even if the clutch lever CS is not pressed by a spring or the like, the clutch lever CS can transmit power to the second shaft member M without slipping.
  • the clutch lever CS is arranged so as to form an appropriate angle ⁇ according to the friction coefficient ⁇ at the power point P, or the clutch lever CS is arranged so as to have an appropriate friction coefficient ⁇ at the power point P according to the angle ⁇ .
  • the urging member for strongly pressing the friction shoe toward the output side drum is essentially an essential element, and it was necessary to secure a space for storing the urging member in the centrifugal clutch.
  • the centrifugal clutch known in Patent Document 1 changes the release timing of the friction shoe by pressing the friction shoe against the output side drum by the clutch spring and further adjusting the release timing of the centrifugal weight by the detent spring and the weight spring.
  • a space for providing the clutch spring, the detent spring, and the weight spring is required in the centrifugal clutch, and the centrifugal clutch may be complicated and large.
  • the contact state between the friction shoe and the output side drum changes from the static friction state to the dynamic friction state. There was a risk that the friction shoe would start to slip on the output side drum and the transmission torque would decrease.
  • the present invention solves these problems, and with a simple configuration, the clutch shoe can be brought into contact with the second shaft member, the transmission torque can be prevented from decreasing, the size can be reduced, and the manufacturing cost can be reduced.
  • An object of the present invention is to provide a centrifugal clutch whose increase can be suppressed.
  • the centrifugal clutch of the present invention has a first shaft member and a second shaft member that is independently rotatable on the same rotation shaft as the first shaft member, and is connected to the first shaft member.
  • a clutch lever connected via a pin so as to be relatively rotatable in a plane orthogonal to the rotation axis is provided, and the clutch lever is configured to be capable of abutting the second shaft member from the outer peripheral side.
  • a centrifugal clutch provided with a clutch shoe having a friction surface, the line connecting the center of the connecting pin and the force point of the friction surface in a state where the friction surface and the second shaft member are in contact with each other.
  • ⁇ is an angle formed by a line connecting the center of the second shaft member to the force point of the friction surface
  • ⁇ is a static friction coefficient when the friction surface and the second shaft member are in contact with each other.
  • the first shaft member is provided with a clutch lever that is relatively rotatably connected in a plane orthogonal to the rotation shaft via a connecting pin.
  • a centrifugal clutch provided with a clutch shoe having a friction surface configured to be capable of contacting the second shaft member from the outer peripheral side, and is a connection in a state where the friction surface and the second shaft member are in contact with each other.
  • the angle formed by the line connecting the center of the pin to the force point of the friction surface and the line connecting the center of the second shaft member to the force point of the friction surface is ⁇ , and the friction surface contacts the second shaft member.
  • the clutch lever When the coefficient of static friction when ⁇ >tan ⁇ When the first shaft member is rotated while the friction surface of the clutch shoe is in contact with the second shaft member, the clutch lever does not slip and the power is surely applied to the second shaft member. Can communicate. In addition, the transmission torque can be increased because the power transmission is not the frictional force caused by the pressing of the spring but the frictional force utilizing the engagement by the wedge effect.
  • a swing pin having a swing shaft parallel to the rotation shaft of the clutch lever is connected to the clutch lever, and the clutch shoe is connected to the swing pin so as to be swingable about the swing shaft.
  • the position of the power point can be stably kept near the swing pin of the clutch lever.
  • the clutch shoe swings and can be brought into contact with the second shaft member while facing the second shaft member, a wide friction surface can be provided without changing the force point position, and the surface pressure applied to the friction surface can be dispersed. The wear resistance can be improved and the service life can be extended without increasing the strength of the constituent material of the clutch shoe.
  • the shear area of the swing pin increases, and The shearing stress of the moving pin is reduced, which makes it possible to increase the transmittable torque without changing the materials of the swing pin, the clutch shoe, and the clutch lever.
  • the shear area of the swing pin can be easily increased by changing the number of clutch shoes. The shear stress can be reduced, and the torque that can be transmitted can be further increased. Further, by changing the number of clutch shoes, the area of the friction surface can be easily increased or decreased, and the surface pressure applied to the friction surface can be adjusted.
  • the shear area of the swing pin can be easily adjusted by changing the number of clutch levers. The stress can be reduced, and thus the torque that can be transmitted can be further increased.
  • at least one clutch lever is arranged in the opposite direction with the second shaft member interposed therebetween, it is possible to rotate the first shaft member in either the forward or reverse direction. , The corresponding clutch levers abut the second shaft member, and power can be transmitted.
  • the clutch lever since the clutch lever is biased toward the second shaft member side by the biasing member, when the first shaft member starts rotating, the clutch lever is surely moved to the second shaft member. It can be kept in contact with the member.
  • the biasing member since the biasing member is clamped by the clutch levers arranged at least one in the opposite direction with the second shaft member interposed therebetween, the number of the biasing members to be installed can be reduced. The number can be reduced and the centrifugal clutch can be downsized.
  • the first shaft member is provided with the outer ring having the cylindrical accommodation space therein, and the connection pin is disposed in the accommodation space. Even if the rotation speed increases and the clutch shoe disengages from the second shaft member, the clutch lever hits the outermost part in the housing space, so that the clutch lever is not swung largely outside the housing space, and the circumference of the centrifugal clutch is prevented. There is no need to provide a large space in.
  • one end of the connecting member along the rotation axis direction is fixed to the end of the first shaft member, and the connecting member is connected to the first end of the first shaft member via the reinforcing member at a position away from the end.
  • the stress applied to the connecting member can be dispersed, and the first shaft can be compared with the case where only one end portion of the connecting member is fixed to the first shaft member. It is possible to reduce the deflection of the member and the connecting member. As a result, the positional relationship between the first shaft member and the clutch lever does not shift, and stable torque transmission becomes possible.
  • the clutch lever when the clutch lever is at a predetermined position within the movable range, the combined center of gravity of all the members forming the first shaft member side is on the rotation axis of the first shaft member. Since it is located at, the vibration of the first shaft member due to the rotation operation of the centrifugal clutch can be suppressed, and the deviation between the rotation shaft of the first shaft member and the rotation shaft of the second shaft member can be prevented.
  • the friction surface of one clutch lever is, for example, When disengaged from the second shaft member, the friction surface of the other clutch lever also interlocks and disengages from the second shaft member at substantially the same time, so wear of the friction surface can be suppressed and torque transmission can be switched quickly. ..
  • the gravity of the clutch lever can be offset between the forward rotation side clutch lever and the reverse rotation side clutch lever that rotate in conjunction with each other. It is possible to further stabilize the operations of the forward rotation side clutch lever and the reverse rotation side clutch lever regardless of the direction of rotation of the clutch.
  • the front sectional view of centrifugal clutch 100 which is a reference example of the present invention.
  • the schematic front view which shows the state which the clutch lever 113 of the centrifugal clutch 100 which is a reference example of this invention contact
  • 6 is a schematic diagram for explaining a power transmission relationship between a clutch lever CS and a second shaft member M.
  • FIG. The connecting pin 217 side perspective view of the centrifugal clutch 200 which concerns on one Embodiment of this invention.
  • the perspective view of the rocking pin 218 side of centrifugal clutch 200 concerning one embodiment of the present invention.
  • FIG. 3 is a schematic diagram showing a connection relationship between a clutch lever 313 and an outer ring connecting portion 311a of a centrifugal clutch 300 according to an embodiment of the present invention.
  • FIG. 6 is a schematic diagram showing a connection relationship between a clutch lever 413 and a clutch shoe 414 of the centrifugal clutch 400 according to the embodiment of the present invention.
  • the perspective view of the centrifugal clutch 500 which concerns on one Embodiment of this invention.
  • the schematic front view of the centrifugal clutch 600 which concerns on one Embodiment of this invention.
  • a centrifugal clutch 100 that is a reference example of the present invention will be described below with reference to the drawings.
  • a schematic diagram of a configuration in which only one clutch lever 113 is provided and the centrifugal clutch 100 functions only in clockwise rotation will be used from FIG. 2 onward.
  • a centrifugal clutch 100 which is a reference example of the present invention, has a first shaft member 110 and a second shaft member 120 configured to be independently rotatable on the same rotation shaft as the first shaft member 110.
  • the first shaft member 110 has an outer ring 111 having a cylindrical housing space 112 therein, a connecting pin 117 arranged in the housing space 112, and a rotating shaft via the connecting pin 117.
  • a clutch lever 113 connected to the first shaft member 110 is provided so as to be relatively rotatable in a plane orthogonal to each other.
  • the clutch levers 113 are arranged one by one in opposite directions with the second shaft member 120 interposed therebetween.
  • the clutch lever 113 is inserted into the housing hole 118 opened to the outer ring 111 side and the housing hole 118, and the clutch lever 113 is inserted.
  • An urging member 119 for urging the second shaft member 120 toward the second shaft member 120 with a slight force, and a clutch shoe 114 having a friction surface 115 configured to be capable of contacting the second shaft member 120 are provided.
  • the power transmission relationship at the contact surface between the friction surface 115 of the clutch lever 113 and the second shaft member 120 is summarized in the power point 116 on the friction surface 115 to obtain the power transmission relationship at the power point 116. Can be replaced. Further, in the clutch lever 113, a line L1 connecting the force point 116 and the center of the connecting pin 117 and a line L2 connecting the force point 116 and the center of the second shaft member 120 have an inclination of an angle ⁇ . It is arranged. Further, the static friction coefficient ( ⁇ ) on the contact surface between the friction surface 115 of the clutch lever 113 and the second shaft member 120 is ⁇ >tan ⁇ To meet.
  • the power transmission of the centrifugal clutch 100 at the start of rotation of the first shaft member 110 will be described.
  • the outer ring 111 and the clutch lever 113 receive a force in a clockwise rotating direction.
  • the clutch lever 113 is biased toward the second shaft member 120 side by the biasing member 119 with a slight force, the friction surface 115 of the clutch shoe 114 is changed when the first shaft member 110 starts rotating.
  • the clutch lever 113 is in contact with the second shaft member 120, the clutch lever 113 can transmit power to the second shaft member 120 in the clockwise direction with respect to the force point 116. That is, the clutch lever 113 transmits the driving force (referred to as F1) in the direction of rotating the second shaft member 120 in the clockwise direction at the power point 116.
  • F1 driving force
  • the clutch lever 113 connects the second shaft member 120 at the power point 116.
  • a vertical reaction force (not shown) having the same magnitude as the component force F2 and applied in the opposite direction is generated on the clutch lever 113 at the power point 116, so the maximum static friction force at the power point 116 is ⁇ F2.
  • the clutch lever 113 can reliably transmit power to the second shaft member 120 without slipping. Further, due to the wedge effect, the clutch lever 113 maintains the state in which it is attracted to the second shaft member 120 side by the component force F2.
  • the clutch lever 113 separated from the second shaft member 120 receives a force swung toward the outside of the centrifugal clutch 100, but the clutch lever 113 is arranged in the accommodation space 112 surrounded by the outer ring 111. Since the clutch lever 113 can move only to a position where it abuts the outer ring 111, the clutch lever 113 does not pop out around the centrifugal clutch 100, and it is not necessary to secure a large space around the centrifugal clutch 100.
  • the centrifugal clutch 100 since there is no biasing member in the centrifugal clutch 100 other than the biasing member 119 that slightly biases the clutch lever 113 toward the second shaft member 120, the number of parts in the housing space 112 can be reduced, and It is not necessary to secure a large space in the centrifugal clutch 100, and the centrifugal clutch 100 can be downsized.
  • the clutch lever 113 disengaged from the second shaft member 120 is urged toward the outer ring 111 side by the centrifugal force while the first shaft member 110 is rotating, so that the clutch lever 113 may come into contact with the second shaft member 120. Absent. Furthermore, it suffices to provide a weak biasing member to control the reconnection, which makes it extremely easy to control the torque transmission at a low rotation speed. In addition, by increasing the static friction coefficient ⁇ of the contact surface between the friction surface 115 and the second shaft member 120, the power is transmitted from the first shaft member 110 to the second shaft member 120 without the clutch lever 113 slipping further. Can be communicated.
  • FIGS. 5 to 10 do not show the first shaft member 210 and the outer ring 211, and FIGS. 9 and 10 do not show the clutch lever 213b. Further, a part of the description common to the centrifugal clutch 100 which is the reference example of the present invention will be omitted.
  • a centrifugal clutch 200 that is an embodiment of the present invention includes a first shaft member 210 and a first shaft member 210 that is independently rotatable about the same rotation shaft as the first shaft member 210.
  • the biaxial member 220 is provided, and the first shaft member 210 has an outer ring 211 having a housing space 212 inside, and a connection pin 217 having both ends supported by an outer ring connecting portion 211 a arranged in the housing space 212.
  • the clutch levers 213a and 213b are connected to the first shaft member 210 via the connecting pin 217 so as to be relatively rotatable in a plane orthogonal to the rotation axis.
  • the clutch levers 213a and 213b are provided two by two in opposite directions with the second shaft member 220 interposed therebetween in the rotation axis direction of the clutch levers 213a and 213b.
  • a swing pin 218 having a swing shaft parallel to the shaft is connected, and clutch shoes 214a and 214b are connected to the swing pin 218 so as to be swingable about the swing shaft.
  • the clutch shoes 214a, 214b are provided with linings 221a, 221b having friction surfaces 215a, 215b at the contact portions with the second shaft member 220, and formed in an arc shape along the outer peripheral surface of the second shaft member 220. Has been done. Further, the clutch levers 213a and 213b are biased by a biasing member (not shown) toward the second shaft member 220 with a slight force.
  • the power transmission relationship at the contact surface between the friction surface 215a and the second shaft member 220 is concentrated at the power point 216 of the friction surface 215a, so that the power transmission at the power point 216 is transmitted. Can be replaced by a relationship.
  • the friction surface 215a is in stable surface contact over a wide range by adjusting the inclination with respect to the outer peripheral surface of the second shaft member 220 by the swing pin 218.
  • the clutch lever 213a has an angle between L1 and L2. It is arranged so as to have an inclination of ⁇ .
  • the static friction coefficient (referred to as ⁇ ) at the contact surface between the friction surface 215a of the lining 221a and the second shaft member 220 is ⁇ >tan ⁇ To meet.
  • the clutch lever 213a is biased by the biasing member (not shown) toward the second shaft member 220 side with a slight force. Therefore, at the start of rotation of the first shaft member 210, the friction surface of the lining 221a. 215a is in contact with the second shaft member 220, and the clutch lever 213a can transmit power to the second shaft member 220 in the clockwise rotation direction with reference to the force point 216. That is, the clutch lever 213a transmits the driving force (referred to as F1) in the direction of rotating the second shaft member 220 in the clockwise direction at the power point 216.
  • F1 driving force
  • the clutch shoe 214a is configured to be swingable with the center axis of the swing pin 218 as the swing axis, compared to the case where the clutch shoe 214a is directly and fixedly provided on the clutch lever 213a, the lining.
  • the 221a can change its direction according to the outer peripheral surface of the second shaft member 220 and come into contact with the outer peripheral surface of the second shaft member 220, and the position of the force point 216 can be stably maintained. Further, the contact surface of the friction surface 215a with the second shaft member 220 can be made large, and the surface pressure applied to the friction surface 215a can be reduced.
  • the clutch lever 213a causes the second shaft member 220 to move to the power point 216 at the power point 216.
  • a normal force (not shown) having the same magnitude as the component force F2 and applied in the opposite direction is generated on the clutch shoe 214a at the force point 216, the maximum static friction force at the force point 216 is ⁇ F2.
  • the clutch lever 213a can reliably transmit power to the second shaft member 220 without causing the friction surface 215a and the second shaft member 220 to slide. Further, due to the wedge effect, the clutch shoe 214a maintains the state of being attracted to the second shaft member 220 by the component force F2.
  • two clutch levers 213a are connected to the outer ring connecting portion 211a side by side through the connecting pin 217 so as to be relatively rotatable relative to each other in a plane orthogonal to the rotation axis. Therefore, as compared with the case where only one clutch lever 213a is connected to the outer ring connecting portion 211a, the clutch lever 213a can stably rotate about the central axis of the connecting pin 217 and the shearing area of the connecting pin 217 becomes smaller. As a result, the shear stress of the connecting pin 217 decreases. As a result, the torque that can be transmitted can be increased without increasing the strength by changing the materials of the connecting pin 217, the clutch lever 213a, and the outer ring connecting portion 211a.
  • a swing pin 218 having a swing shaft parallel to the rotation axis of the clutch lever 213a is connected to the two clutch levers 213a, and a clutch shoe 214a is centered around the swing shaft on the swing pin 218. Since only one clutch lever 213a is connected to the clutch shoe 214a, the clutch shoe 214a stably swings around the central axis of the swing pin 218 as compared with the case where only one clutch lever 213a is connected to the clutch shoe 214a. At the same time, the shear area of the swing pin 218 increases, and the shear stress of the swing pin 218 decreases. As a result, the torque that can be transmitted can be further increased without increasing the strength by changing the materials of the swing pin 218, the clutch lever 213a, and the clutch shoe 214a.
  • the clutch shoe 214a can be stably supported at a plurality of points by the clutch lever 213a. Further, since both ends of the connecting pin 217 are supported by the outer ring connecting portion 211a, the shearing area of the connecting pin 217 increases and the shear stress decreases, and the clutch lever 213a and the outer ring connecting portion 211a are operated during the operation of the clutch 200. Even if a force is applied in the bending direction of the connecting pin 217, the connecting pin 217 is unlikely to be deformed, and the clutch lever 213a can be reliably supported at a normal position.
  • the centrifugal clutch 200 that is an embodiment of the present invention, it is desirable that the combined center of gravity of all the members that form the first shaft member 210 side be located on the rotation axis of the first shaft member 210 as much as possible. .. With this, it is possible to suppress the vibration of the first shaft member 210 during the operation of the centrifugal clutch 200, and it is possible to prevent the deviation between the rotation shaft of the first shaft member 210 and the rotation shaft of the second shaft member 220.
  • the clutch levers 213a and 213b move around the connecting pin 217 as the center of rotation during the operation of the centrifugal clutch 200 and come into contact with or separate from the second shaft member 220, depending on the positions of the clutch levers 213a and 213b.
  • the positions of the combined center of gravity of all the members forming the first shaft member 210 side slightly change. Therefore, in consideration of the moving positions of the clutch levers 213a and 213b in the state where the vibration of the first shaft member 210 is most desired to be suppressed, the combined center of gravity of all the members forming the first shaft member 210 side is the first shaft member 210. It is desirable to set so as to match the rotation axis of.
  • centrifugal clutch 500 according to an embodiment of the present invention will be described with reference to FIG.
  • a part of the description common to the centrifugal clutch 100 and the centrifugal clutch 200 according to the embodiment of the present invention will be omitted.
  • a centrifugal clutch 500 includes a first shaft member 510 and a second shaft member that is independently rotatable on the same rotation shaft as the first shaft member 510. And 520 are provided.
  • One end of a connecting member 511a formed separately from the first shaft member 510 is directly connected to the first shaft member 510, and both ends of the clutch levers 513a and 513b are supported by the connecting member 511a. It is connected to the first shaft member 510 via a pin (not shown) so as to be relatively rotatable in a plane orthogonal to the rotation axis.
  • connection member 511 a Of the end portions of the connection member 511 a, the end portion on the side not directly connected to the first shaft member 510 is fixed to the first shaft member 510 via the reinforcing member 530. That is, both ends of the connecting member 511a are fixed to the first shaft member 510.
  • the reinforcing member 530 includes a reinforcing ring 532 that is directly connected to the end of the connecting member 511a, and a reinforcing column 531 that connects the first shaft member 510 and the reinforcing ring 532.
  • the stress applied to the connecting member 511a during the operation of the centrifugal clutch 500 can be dispersed from the both ends of the connecting member 511a to the first shaft member 510, and the deflection of the first shaft member 510 and the connecting member 511a can be reduced.
  • the positional relationship between the member 510 and the clutch levers 513a and 513b can be prevented from shifting, and stable torque transmission can be performed.
  • the reinforcing member 530 connects the reinforcing ring 531 and the first shaft member 510 with the plurality of reinforcing columns 532 arranged along the outer edge of the first shaft member 510, the stress applied to the connecting member 511a is It is possible to disperse the first shaft member 510 as a whole, it is possible to further prevent the displacement of the positional relationship between the first shaft member 510 and the clutch levers 513a, 513b, and it is possible to further stably transmit the torque.
  • FIG. 14 does not show the first shaft member and the connecting member. Further, a part of the description common to the centrifugal clutches 100, 200, and 500 according to the embodiment of the present invention will be omitted.
  • a centrifugal clutch 600 is configured to be independently rotatable on a first shaft member (not shown) and the same rotation shaft as the first shaft member (not shown).
  • Second shaft member 620 is provided.
  • An end of a connection member (not shown) is connected to the first shaft member (not shown), and both ends of the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b are supported by the connection member (not shown). It is connected to the first shaft member (not shown) so as to be relatively rotatable in the plane orthogonal to the rotation axis via the connecting pin.
  • a gear protrusion 631 is provided at an end of the forward rotation side clutch lever 613a supported by the connection pin 617, and a gear protrusion 631 is provided at an end of the reverse rotation side clutch lever 613b supported by the connection pin 617.
  • the interlocking gear 630 is formed by meshing with the gear recessed portion 632. By this interlocking gear 630, the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b rotate in the opposite direction about the connecting pin 617 as the center of rotation, and therefore, for example, the friction surface 615a of the forward rotation side clutch lever 613a.
  • the friction surface 615b of the reverse rotation side clutch lever 613b also interlocks and disengages from the second shaft member 620 almost at the same time, so that abrasion of the friction surfaces 615a and 615b can be suppressed and the torque transmission. Switching can be performed quickly.
  • the forward rotation side clutch lever and the reverse rotation side clutch lever always have their own weights in the direction in which gravity acts.
  • gravity acts in the direction in which the forward rotation side clutch lever contacts the second shaft member
  • gravity acts in the direction away from the second shaft member in the reverse rotation side clutch lever.
  • the contact and release timings of the forward rotation side clutch lever and the reverse rotation side clutch lever with respect to the second shaft member may become unstable.
  • the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b of the centrifugal clutch 600 are configured to be interlocked with each other by the interlocking gear 630, the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b can be rotated together with the gear protrusion 631.
  • the weights of the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b can be canceled each other through the gear recess 632, and the second shaft member 620 of the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b can be canceled. There is no disruption in the timing of contact and release.
  • the clutch levers are described as being arranged one by one in opposite directions with the second shaft member interposed therebetween, but the number and arrangement direction of the clutch levers are not limited to this, and for example, Only one clutch lever may be arranged in the forward rotation direction of the second shaft member, or two clutch levers may be arranged in opposite directions with the second shaft member interposed therebetween.
  • the clutch lever has the accommodation hole opened to the outer ring side and the urging member that is inserted into the accommodation hole and urges the clutch lever toward the second shaft member with a slight force.
  • the aspect of the clutch lever is not limited to this, and for example, the accommodation hole or the urging member may not be provided, and the urging member is provided from the accommodation hole provided in the outer ring to the clutch. It may be arranged to bias the lever.
  • first shaft member and the second shaft member are described as being rotatably opposed to each other independently of each other about the same rotation shaft as the central axis, but the first shaft member is described.
  • the arrangement of the second shaft member and the second shaft member is not limited to this.
  • the second shaft member may be arranged to be inserted into the hollow cylindrical first shaft member.
  • the clutch lever is described as being connected to the outer ring connecting portion side by side so as to be relatively rotatable in the plane orthogonal to the rotation axis via the connecting pin.
  • the number of levers is not limited to this, and, for example, three levers may be connected side by side to the outer ring connecting portion so as to be relatively axially rotatable in a plane orthogonal to the rotation axis via a connecting pin.
  • the clutch lever is described as being connected to the outer ring connecting portion side by side so as to be relatively rotatable in the plane orthogonal to the rotation axis via the connecting pin.
  • the connection state of the lever and the outer ring connecting portion is not limited to this.
  • the connecting portion of the clutch levers 313a and 313b with the connecting pin 317 is formed in a comb shape.
  • the outer ring connecting portion side may also be formed in a comb shape so as to match the connecting portion of the clutch lever formed in a comb shape with the connecting pin.
  • the clutch lever is connected to the swing pin having the swing shaft parallel to the rotation axis of the clutch lever, and the clutch shoe is connected to the swing pin about the swing shaft.
  • the clutch levers 413a and 413b are not connected to each other, for example, as in the centrifugal clutch 400 shown in FIG.
  • the clutch levers 413a and 413b may be formed in a comb shape at the connecting portion with the rocking pins 413a and 413b.
  • the clutch shoe side may also be formed in a comb shape in accordance with the connection portion of the above.
  • the clutch shoe is provided with a lining having a friction surface at the contact portion with the second shaft member, and is formed in an arc shape along the outer peripheral surface of the second shaft member.
  • the configuration of the clutch shoe is not limited to this, and for example, the lining may not be provided, the clutch shoe may be formed in a flat plate shape, and the lining capable of being deformed by a certain amount may have a predetermined thickness. It may be attached to the clutch shoe, and the lining may be deformed at the time of contact with the outer peripheral surface of the second shaft member to form a wide friction surface.
  • the first shaft member includes the outer ring having the accommodation space therein, the connection pins whose both ends are supported by the outer ring connection portion disposed in the accommodation space, and the rotating shaft via the connection pin.
  • the clutch lever that is connected to the first shaft member so as to be relatively rotatable in the plane orthogonal to the above has been described, but the configuration of each member provided in the first shaft member is the same.
  • the connection pins may be provided so that both ends are directly supported by the first shaft member without providing the outer ring or the outer ring connecting portion.
  • the reinforcing member has been described as being configured by the ring-shaped reinforcing ring and the reinforcing column, but the configuration of the reinforcing member is not limited to this, and for example, two reinforcing columns are provided.
  • the first shaft member extends in a direction along the rotation axis from the first shaft member so as to sandwich the connection member, and connects the end portion of the connection member and the end portion of the reinforcing column with a rod-shaped connecting member instead of the reinforcing ring.
  • the reinforcing member may be fixed to the end portion of the connection member and the end portion of the first shaft member so as to sandwich the connection member and the first shaft member from the rotation axis direction.
  • connection member is configured such that one end of the connection member is directly connected to the first shaft member and the other end is connected to the first shaft member via the reinforcing member.
  • connection form of the connection member and the first shaft member is not limited to this, and for example, one end of the connection member is directly connected to the first shaft member, and a position other than the end of the connection member is provided. May be connected to the first shaft member via the reinforcing member, or the connecting member, the first shaft member, and a part or all of the reinforcing member may be integrally formed.
  • connection member is positioned and connected to the first shaft member by providing the end portion of the connection pin on the first shaft member side so as to penetrate the connection member and connecting the connection pin to the first shaft member. It may be configured to do so.
  • the gear convex portion is provided at the end supported by the connecting pin of the forward rotation side clutch lever, and the gear convex portion is provided at the end supported by the connection pin of the reverse rotation side clutch lever.
  • the description has been given assuming that the gears mesh with the provided gear recesses to form the interlocking gears and rotate in conjunction with each other, but the relationship between the forward rotation side clutch lever and the reverse rotation side clutch lever is not limited to this.
  • the forward rotation side clutch lever and the reverse rotation side clutch lever do not have to rotate in conjunction without providing an interlocking gear, and the side supported by the connecting pin of the forward rotation side clutch lever and the reverse rotation side clutch lever.
  • the forward rotation side clutch lever and the reverse rotation side clutch lever may be configured to rotate interlocked with each other by coating the surface of the end portion with a rubber material and bringing them into contact with each other.
  • Centrifugal clutch 110 210, 510... 1st shaft member 111, 211... Outer ring 211a, 311a... Outer ring connection part 511a... Connection member 112, 212... Accommodation spaces 113, 213a, 213b, 313a, 313b, 413a, 413b, 513a, 513b, CS... Clutch levers 114, 214a, 214b, 314a, 314b, 414a, 414b, 514a, 514b, 614a, 614b... Clutch shoe 115, 215a, 215b, 615a, 615b... Friction surface 116, 216, P...

Abstract

The present invention provides a centrifugal clutch that, with a simple configuration, makes it possible to place a clutch shoe in contact with a second shaft member, suppress a decrease in transmission torque, reduce the overall size, and suppress an increase in manufacturing costs.　A centrifugal clutch (200) is provided with a first shaft member (210), a second shaft member (220), and a clutch lever (213) that has a friction surface (215) capable of coming into contact with the second shaft member (220). Said elements are disposed such that μ>tanθ in a state in which the friction surface (215) and the second shaft member (220) are in contact, where θ is the angle formed by a line connecting the center of a connection pin (217) and a force point (216) of the friction surface (215) and a line connecting the center of the second shaft member (220) and the force point (216), and μ is the static friction coefficient when the friction surface (215) and the second shaft member (220) are in contact. The clutch lever (213) is connected to a pivot pin (218), and a clutch shoe (214) is pivotably connected to the pivot pin (218).

Description

遠心クラッチCentrifugal clutch
　本発明は、入力軸の回転を出力軸側に伝達するクラッチに関し、特に、遠心力によって入力軸から出力軸への動力の伝達および切断を切り替える遠心クラッチに関する。 The present invention relates to a clutch that transmits the rotation of an input shaft to the output shaft side, and particularly to a centrifugal clutch that switches transmission and disconnection of power from an input shaft to an output shaft by centrifugal force.
　従来、入力軸から出力軸側に動力伝達するクラッチは、小型バイク、チェーンソー、エンジン式ラジコンヘリ等の小型の駆動機器等の駆動力の伝達経路上に配されており、様々なものが公知である。 Conventionally, clutches that transmit power from the input shaft to the output shaft side are arranged on the drive force transmission path of small drive devices such as small bikes, chainsaws, and engine-type radio-controlled helicopters, and various clutches are known. is there.
　例えば、特許文献１に記載の遠心クラッチは、第１軸部材（入力側回転部１）と第２軸部材（出力側ドラム５）とを有し、第１軸部材（入力側回転部１）には、接続ピン（支軸３）を介して一対のクラッチレバー（摩擦シュー２）および遠心ウェイト７が接続されており、一対のクラッチレバー（摩擦シュー２）は、第２軸部材（出力側ドラム５）に向かって摩擦面を付勢するように、互いの一端がクラッチスプリング４で接続されている。
　一対の遠心ウェイト７は、第２軸部材（出力側ドラム５）を抱合する方向に、ウェイトスプリング８により、互いの側面を付勢されている。
　また、遠心ウェイト７は、互いの自由端側に形成されたカム面９が第１軸部材（入力側回転部１）に接続されたディテントスプリング１０に係合しているものである。 For example, the centrifugal clutch described in Patent Document 1 has a first shaft member (input side rotating part 1) and a second shaft member (output side drum 5), and a first shaft member (input side rotating part 1). Is connected to a pair of clutch levers (friction shoes 2) and a centrifugal weight 7 via connection pins (support shafts 3). The pair of clutch levers (friction shoes 2) are connected to the second shaft member (output side). One end of each other is connected by a clutch spring 4 so as to urge the friction surface toward the drum 5).
The pair of centrifugal weights 7 are urged by the weight springs 8 on their side surfaces in the direction in which the second shaft member (output side drum 5) is bound.
Further, in the centrifugal weight 7, the cam surfaces 9 formed on the free end sides of each other are engaged with the detent spring 10 connected to the first shaft member (the input side rotating portion 1).
　この特許文献１に記載の遠心クラッチは、クラッチスプリング４によってクラッチレバー（摩擦シュー２）の摩擦面が第２軸部材（出力側ドラム５）に密着しているため、第１軸部材（入力側回転部１）を回転させると、第２軸部材（出力側ドラム５）に動力伝達されるが、徐々に第１軸部材（入力側回転部１）の回転数が上がり遠心力が大きくなるにしたがって、クラッチスプリング４の付勢力との差が縮まり、クラッチレバー（摩擦シュー２）の摩擦面が第２軸部材（出力側ドラム５）から離脱する方向に力がかかるようになる。 In the centrifugal clutch described in Patent Document 1, since the friction surface of the clutch lever (friction shoe 2) is in close contact with the second shaft member (output side drum 5) by the clutch spring 4, the first shaft member (input side) When the rotating part 1) is rotated, power is transmitted to the second shaft member (output side drum 5), but the rotational speed of the first shaft member (input side rotating part 1) gradually increases and the centrifugal force increases. Therefore, the difference between the urging force of the clutch spring 4 and the urging force of the clutch spring 4 is reduced, and a force is applied in the direction in which the friction surface of the clutch lever (friction shoe 2) is disengaged from the second shaft member (output side drum 5).
　また、遠心ウェイト７も遠心力によって徐々にディテントスプリング１０およびウェイトスプリング８を押し返しながら拡開し、さらに、ディテントスプリング１０とカム面９との係合が解除されると、遠心ウェイト７の所定の位置に設けられた係合ピン１１がクラッチレバー（摩擦シュー２）に接触し、クラッチレバー（摩擦シュー２）を第２軸部材（出力側ドラム５）から離脱させ、第１軸部材（入力側回転部１）から第２軸部材（出力側ドラム５）への動力伝達を解除するものである。
　なお、クラッチスプリング４、ウェイトスプリング８、ディテントスプリング１０の調整で、クラッチレバー（摩擦シュー２）の離脱タイミングを変化させることができるものである。 Further, the centrifugal weight 7 also expands by gradually pushing back the detent spring 10 and the weight spring 8 by the centrifugal force, and when the engagement between the detent spring 10 and the cam surface 9 is released, a predetermined weight of the centrifugal weight 7 is obtained. The engagement pin 11 provided at the position comes into contact with the clutch lever (friction shoe 2), disengages the clutch lever (friction shoe 2) from the second shaft member (output side drum 5), and the first shaft member (input side). The power transmission from the rotating portion 1) to the second shaft member (output side drum 5) is released.
By adjusting the clutch spring 4, the weight spring 8, and the detent spring 10, the disengagement timing of the clutch lever (friction shoe 2) can be changed.
実開昭５９－１８６５３３号公報Japanese Utility Model Publication No. 59-186533
　ところが、上記特許文献等で公知の遠心クラッチは、未だ改善の余地があった。 However, there is still room for improvement in the centrifugal clutches known in the above patent documents.
　発明者は、鋭意検討の結果、遠心クラッチが回転した際の、クラッチレバーと第２軸部材との当接時の力の伝達関係について、以下に説明する知見を得た。 As a result of earnest studies, the inventor has obtained the following knowledge about the force transmission relationship between the clutch lever and the second shaft member when the centrifugal clutch rotates.
　遠心クラッチの第１軸部材が回転すると、図４に示すように、クラッチシューＣＳの摩擦面が第２軸部材Ｍと当接して発生する摩擦力は、摩擦面内の力点Ｐに集約して示すことができる。
　このとき、摩擦面内の力点Ｐにおいて、クラッチレバーＣＳは駆動力Ｆ１で第２軸部材Ｍを回転させようとするが、その際、駆動力Ｆ１は力点Ｐから接続ピンＳの方向へ引く力Ｆの分力として発生しているため、クラッチレバーＣＳは力点Ｐにおいて第２軸部材Ｍを接続ピンＳの方向に力Ｆで押していることになる。
　すなわち、第２軸部材Ｍは力点Ｐにおいて、回転方向に駆動力Ｆ１を受けるとともに、第２軸部材Ｍの中心軸ＭＳ方向にＦの分力Ｆ２で押されていることになり、同時にシューＣＳには接点ＰにおいてＦ２と同じ大きさで反対向きにかかる垂直抗力（図示しない）が発生している。 When the first shaft member of the centrifugal clutch rotates, as shown in FIG. 4, the friction force generated by the friction surface of the clutch shoe CS contacting the second shaft member M is concentrated at the force point P in the friction surface. Can be shown.
At this time, at the power point P in the friction surface, the clutch lever CS tries to rotate the second shaft member M with the driving force F1, but at that time, the driving force F1 is a force pulled from the power point P toward the connecting pin S. Since the force is generated as a component force of F, the clutch lever CS pushes the second shaft member M at the force point P in the direction of the connecting pin S with the force F.
That is, the second shaft member M receives the driving force F1 in the rotational direction at the force point P and is pushed by the component force F2 of F in the central axis MS direction of the second shaft member M, and at the same time, the shoe CS. At the contact point P, a normal force (not shown) having the same magnitude as F2 and applied in the opposite direction is generated.
　また、クラッチレバーＣＳと第２軸部材Ｍとが力点Ｐで接触しているため、クラッチレバーＣＳと第２軸部材Ｍとの間の静止摩擦係数をμとすると、最大静止摩擦力はμＦ２である。
　よって、
μＦ２＞Ｆ１
であれば、クラッチレバーＣＳをスプリングなどで押圧しなくても、クラッチレバーＣＳは滑ることなく第２軸部材Ｍに動力伝達できる。 Further, since the clutch lever CS and the second shaft member M are in contact with each other at the force point P, if the static friction coefficient between the clutch lever CS and the second shaft member M is μ, the maximum static friction force is μF2. is there.
Therefore,
μF2>F1
Then, even if the clutch lever CS is not pressed by a spring or the like, the clutch lever CS can transmit power to the second shaft member M without slipping.
　ただし、遠心クラッチは回転しているため、遠心力に起因して力点Ｐから垂直抗力と同じ方向にＦｒ（図示しない）が発生しており、遠心クラッチの回転速度が上昇するにしたがってＦｒ（図示しない）も大きくなるため、実際には、
μ（Ｆ２－Ｆｒ）＞Ｆ１
を維持している間、シューＣＳは滑ることなく第２軸部材Ｍに動力伝達できる。 However, since the centrifugal clutch is rotating, Fr (not shown) is generated from the force point P in the same direction as the normal force due to the centrifugal force, and as the rotational speed of the centrifugal clutch increases, Fr (not shown). (No) will also be larger, so in reality,
μ(F2-Fr)>F1
While maintaining, the shoe CS can transmit power to the second shaft member M without slipping.
　さらに、力点Ｐと接続ピンＳを結んだ線Ｌ１と、力点Ｐと第２軸部材Ｍの中心軸ＭＳとを結んだ線Ｌ２とがなす角を角度θとすると、
Ｆ１＝Ｆｓｉｎθ
Ｆ２＝Ｆｃｏｓθ
であるから、
Ｆ２＝Ｆ１／ｔａｎθ
となり、θが小さいほどＦ１に対してＦ２が大きくなる。
　すなわち、より回転速度が速くなっても
μ（Ｆ２－Ｆｒ）＞Ｆ１
を維持することができ、高速回転中でも滑ることなく動力伝達できる。 Further, when an angle formed by a line L1 connecting the force point P and the connecting pin S and a line L2 connecting the force point P and the central axis MS of the second shaft member M is an angle θ,
F1=Fsin θ
F2=Fcos θ
Therefore,
F2=F1/tan θ
Thus, the smaller θ is, the larger F2 is than F1.
That is, μ(F2-Fr)>F1 even if the rotation speed becomes faster
Can be maintained, and power can be transmitted without slipping even during high-speed rotation.
　また、回転開始時においては、
μＦ２＞Ｆ１
より、
μ＞ｔａｎθ
であれば、力点Ｐにおける摩擦係数μに合わせて適切な角度θをなすようにクラッチレバーＣＳを配置する、もしくは、角度θに合わせて力点Ｐに適切な摩擦係数μを有するようにクラッチレバーＣＳの摩擦面や第２軸部材Ｍの表面を形成することで、クラッチレバーＣＳが滑ることなく第２軸部材Ｍに動力伝達できる。 Also, at the start of rotation,
μF2>F1
Than,
μ>tan θ
Then, the clutch lever CS is arranged so as to form an appropriate angle θ according to the friction coefficient μ at the power point P, or the clutch lever CS is arranged so as to have an appropriate friction coefficient μ at the power point P according to the angle θ. By forming the friction surface and the surface of the second shaft member M, the power can be transmitted to the second shaft member M without the clutch lever CS slipping.
　ここで、特許文献１で公知の遠心クラッチは、摩擦シューと出力側ドラムとの接触面が出力側ドラムの円周方向に広範囲に分布しており、力点Ｐの位置が接続ピンＳ側に近づき、角度θが大きくなってしまうため、Ｆ１とＦ２との差が小さくなり、回転速度が上昇すると、すぐに、
μ（Ｆ２－Ｆｒ）≦Ｆ１
となり、摩擦シューと出力側ドラムとの当接が解除されてしまう。 Here, in the centrifugal clutch known in Patent Document 1, the contact surface between the friction shoe and the output side drum is widely distributed in the circumferential direction of the output side drum, and the position of the force point P approaches the connection pin S side. , As the angle θ becomes large, the difference between F1 and F2 becomes small, and as soon as the rotation speed increases,
μ(F2-Fr)≦F1
Then, the contact between the friction shoe and the output side drum is released.
　摩擦シューや出力側ドラムの材質を変更して静止摩擦係数μを上昇させることで、摩擦シューと出力側ドラムとの当接を維持することも考えられるが、摩擦面は既に一定以上の静止摩擦係数が発生するような仕様であるため、静止摩擦係数を上昇させる余地は少ない。
　したがって、摩擦シューを出力側ドラム側へ強く押圧するための付勢部材が事実上必須要素となっており、付勢部材を格納するための空間を遠心クラッチ内に確保する必要があった。 It is possible to maintain the contact between the friction shoe and the output side drum by changing the material of the friction shoe and the output side drum to increase the static friction coefficient μ, but the friction surface is already above a certain level. Since the specifications are such that a coefficient is generated, there is little room for increasing the static friction coefficient.
Therefore, the urging member for strongly pressing the friction shoe toward the output side drum is essentially an essential element, and it was necessary to secure a space for storing the urging member in the centrifugal clutch.
　すなわち、特許文献１で公知の遠心クラッチは、クラッチスプリングによって摩擦シューを出力側ドラムへ押し付け、さらに、ディテントスプリング、ウェイトスプリングによって遠心ウェイトの離脱タイミングを調整することで摩擦シューの離脱タイミングを変化させているが、クラッチスプリング、ディテントスプリング、ウェイトスプリングを設けるための空間が遠心クラッチ内に必要となり、遠心クラッチが複雑化し大型化してしまう虞があった。
　また、入力側回転部の回転数が上昇して遠心力が大きくなり、クラッチスプリングの付勢力との差が縮まると、摩擦シューと出力側ドラムとの接触状態が、静止摩擦状態から動摩擦状態へ移行してしまい、摩擦シューが出力側ドラム上で滑り始め、伝達トルクが低下してしまう虞があった。
　また、入力側回転部の回転数が上昇しても摩擦シューと出力側ドラムとの接触状態を静止摩擦状態のままにするには、より強力なクラッチスプリングを設ける必要があり、強力なクラッチスプリングの引張力に耐えられる特別強固な材料を使用することになるため、製造コストが増大してしまう虞があった。
　さらに、所定の回転数以下で再び摩擦面が接触するため、回転数が低い状態でトルクの伝達のコントロールが難しいという問題があった。 That is, the centrifugal clutch known in Patent Document 1 changes the release timing of the friction shoe by pressing the friction shoe against the output side drum by the clutch spring and further adjusting the release timing of the centrifugal weight by the detent spring and the weight spring. However, a space for providing the clutch spring, the detent spring, and the weight spring is required in the centrifugal clutch, and the centrifugal clutch may be complicated and large.
Also, when the rotational speed of the input side rotating part increases and the centrifugal force increases and the difference between the urging force of the clutch spring decreases, the contact state between the friction shoe and the output side drum changes from the static friction state to the dynamic friction state. There was a risk that the friction shoe would start to slip on the output side drum and the transmission torque would decrease.
In order to keep the contact state between the friction shoe and the output side drum in the static friction state even if the rotation speed of the input side rotating part increases, it is necessary to install a stronger clutch spring. Since a specially strong material that can withstand the tensile force is used, the manufacturing cost may increase.
Further, since the friction surfaces come into contact again at a predetermined rotation speed or less, there is a problem that it is difficult to control the transmission of torque when the rotation speed is low.
　本発明は、これらの問題点を解決するものであり、簡単な構成で、クラッチシューを第２軸部材に当接でき、伝達トルクが低下することを抑制でき、小型化が可能且つ製造コストの増加を抑制可能な遠心クラッチを提供することを目的とするものである。 The present invention solves these problems, and with a simple configuration, the clutch shoe can be brought into contact with the second shaft member, the transmission torque can be prevented from decreasing, the size can be reduced, and the manufacturing cost can be reduced. An object of the present invention is to provide a centrifugal clutch whose increase can be suppressed.
　本発明の遠心クラッチは、第１軸部材および前記第１軸部材と同一の回転軸で独立して回転可能に構成された第２軸部材とを有し、前記第１軸部材には、接続ピンを介して回転軸と直交する面内で相対的に軸回転可能に接続されたクラッチレバーが設けられ、前記クラッチレバーには、前記第２軸部材に外周側から当接可能に構成された摩擦面を有したクラッチシューが設けられた遠心クラッチであって、前記摩擦面と前記第２軸部材とが当接した状態における、前記接続ピンの中心から前記摩擦面の力点までを結んだ線と、前記第２軸部材の中心から前記摩擦面の力点までを結んだ線とがなす角度をθとし、前記摩擦面と前記第２軸部材とが当接した際の静止摩擦係数をμとしたとき、
μ＞ｔａｎθ
であるように配置されていることにより、前記課題を解決するものである。 The centrifugal clutch of the present invention has a first shaft member and a second shaft member that is independently rotatable on the same rotation shaft as the first shaft member, and is connected to the first shaft member. A clutch lever connected via a pin so as to be relatively rotatable in a plane orthogonal to the rotation axis is provided, and the clutch lever is configured to be capable of abutting the second shaft member from the outer peripheral side. A centrifugal clutch provided with a clutch shoe having a friction surface, the line connecting the center of the connecting pin and the force point of the friction surface in a state where the friction surface and the second shaft member are in contact with each other. And θ is an angle formed by a line connecting the center of the second shaft member to the force point of the friction surface, and μ is a static friction coefficient when the friction surface and the second shaft member are in contact with each other. When I did
μ>tan θ
By arranging as described above, the above problems are solved.
　請求項１にかかる発明の遠心クラッチは、第１軸部材には、接続ピンを介して回転軸と直交する面内で相対的に軸回転可能に接続されたクラッチレバーが設けられ、クラッチレバーには、第２軸部材に外周側から当接可能に構成された摩擦面を有したクラッチシューが設けられた遠心クラッチであって、摩擦面と第２軸部材とが当接した状態における、接続ピンの中心から摩擦面の力点までを結んだ線と、第２軸部材の中心から摩擦面の力点までを結んだ線とがなす角度をθとし、摩擦面と第２軸部材とが当接した際の静止摩擦係数をμとしたとき、
μ＞ｔａｎθ
であるように配置されているため、クラッチシューの摩擦面が第２軸部材に当接した状態で第１軸部材を回転させると、クラッチレバーは滑ることなく確実に第２軸部材に動力を伝達できる。
　また、スプリングの押し付けによる摩擦力ではなく、くさび効果による噛み込みを利用した摩擦力による動力伝達であるため、伝達トルクを大きくできる。
　さらに、遠心クラッチの回転数が上昇すると遠心力を起因としたＦｒが大きくなり、
μ（Ｆ２－Ｆｒ）≦Ｆ１
を満たすと、瞬時にクラッチレバーは第２軸部材から離脱するため、クラッチレバーと第２軸部材とが滑りながら当接する時間が短くなり、クラッチシューや第２軸部材の摩耗が少なく、メンテンナンス頻度を少なくできる。
　また、スプリングの押し付けによる摩擦力を必要としないため、遠心クラッチ内に摩擦力発生用のスプリングを設置する空間を設ける必要がなく、遠心クラッチを小型化できる。
　さらに、再接続をコントロールするために弱いスプリングを設けるだけでよく、回転数が低い状態でトルクの伝達のコントロールがきわめて容易となる。
　また、クラッチレバーには、クラッチレバーの回転軸と平行な揺動軸を有する揺動ピンが接続され、クラッチシューは、揺動軸を中心に揺動可能に揺動ピンと接続されているため、クラッチレバーにクラッチシューが固定的に設けられている場合に比べて、力点の位置を安定的にクラッチレバーの揺動ピン付近に留めることができる。
　さらに、クラッチシューが揺動して第２軸部材に向きを合わせて当接できるため、力点位置を変えることなく摩擦面を広く設けることができ、摩擦面にかかる面圧を分散でき、これによって、クラッチシューの構成材料の強度を上げることなく耐摩耗性を向上でき、高寿命化できる。 In the centrifugal clutch of the invention according to claim 1, the first shaft member is provided with a clutch lever that is relatively rotatably connected in a plane orthogonal to the rotation shaft via a connecting pin. Is a centrifugal clutch provided with a clutch shoe having a friction surface configured to be capable of contacting the second shaft member from the outer peripheral side, and is a connection in a state where the friction surface and the second shaft member are in contact with each other. The angle formed by the line connecting the center of the pin to the force point of the friction surface and the line connecting the center of the second shaft member to the force point of the friction surface is θ, and the friction surface contacts the second shaft member. When the coefficient of static friction when
μ>tan θ
When the first shaft member is rotated while the friction surface of the clutch shoe is in contact with the second shaft member, the clutch lever does not slip and the power is surely applied to the second shaft member. Can communicate.
In addition, the transmission torque can be increased because the power transmission is not the frictional force caused by the pressing of the spring but the frictional force utilizing the engagement by the wedge effect.
Furthermore, as the rotational speed of the centrifugal clutch increases, Fr due to centrifugal force increases,
μ(F2-Fr)≦F1
When the condition is satisfied, the clutch lever is instantly disengaged from the second shaft member, so that the time during which the clutch lever and the second shaft member are in sliding contact with each other is shortened, wear of the clutch shoe and the second shaft member is reduced, and the maintenance frequency is reduced. Can be reduced.
Further, since the frictional force due to the pressing of the spring is not required, it is not necessary to provide a space for installing the spring for generating the frictional force in the centrifugal clutch, and the centrifugal clutch can be miniaturized.
Further, it is only necessary to provide a weak spring to control the reconnection, and it becomes extremely easy to control the torque transmission at a low rotation speed.
Further, a swing pin having a swing shaft parallel to the rotation shaft of the clutch lever is connected to the clutch lever, and the clutch shoe is connected to the swing pin so as to be swingable about the swing shaft. Compared to the case where the clutch shoe is fixedly provided on the clutch lever, the position of the power point can be stably kept near the swing pin of the clutch lever.
Further, since the clutch shoe swings and can be brought into contact with the second shaft member while facing the second shaft member, a wide friction surface can be provided without changing the force point position, and the surface pressure applied to the friction surface can be dispersed. The wear resistance can be improved and the service life can be extended without increasing the strength of the constituent material of the clutch shoe.
　請求項２に記載の構成によれば、クラッチシューおよびクラッチレバーの少なくともいずれか一方は、揺動ピンと揺動軸方向に複数箇所で接続されているため、揺動ピンのせん断面積が増え、揺動ピンのせん断応力が小さくなり、これによって、揺動ピンやクラッチシュー、クラッチレバーの材質を変えることなく、伝達可能なトルクを増大させることができる。
　請求項３に記載の構成によれば、クラッチシューは、揺動軸方向に複数設けられているため、クラッチシューの数を変えることで、揺動ピンのせん断面積を簡単に増やすことができ、せん断応力を小さくでき、より一層伝達可能なトルクを増大させることができる。
　また、クラッチシューの数を変えることで、摩擦面の面積を簡単に増減でき、摩擦面にかかる面圧を調整できる。 According to the configuration of claim 2, since at least one of the clutch shoe and the clutch lever is connected to the swing pin at a plurality of positions in the swing axis direction, the shear area of the swing pin increases, and The shearing stress of the moving pin is reduced, which makes it possible to increase the transmittable torque without changing the materials of the swing pin, the clutch shoe, and the clutch lever.
According to the configuration described in claim 3, since the plurality of clutch shoes are provided in the swing axis direction, the shear area of the swing pin can be easily increased by changing the number of clutch shoes. The shear stress can be reduced, and the torque that can be transmitted can be further increased.
Further, by changing the number of clutch shoes, the area of the friction surface can be easily increased or decreased, and the surface pressure applied to the friction surface can be adjusted.
　請求項４に記載の構成によれば、クラッチレバーは、揺動軸方向に複数設けられているため、クラッチレバーの数を変えることで、揺動ピンのせん断面積を簡単に調整できることから、せん断応力を小さくでき、これによって、より一層伝達可能なトルクを増大させることができる。
　請求項５に記載の構成によれば、クラッチレバーは、第２軸部材を挟んで逆向きに少なくとも１つずつ配置されているため、第１軸部材の回転方向が正逆どちらであっても、それぞれに対応したクラッチレバーが第２軸部材に当接し、動力を伝達することができる。 According to the configuration of claim 4, since the plurality of clutch levers are provided in the swing axis direction, the shear area of the swing pin can be easily adjusted by changing the number of clutch levers. The stress can be reduced, and thus the torque that can be transmitted can be further increased.
According to the configuration of claim 5, since at least one clutch lever is arranged in the opposite direction with the second shaft member interposed therebetween, it is possible to rotate the first shaft member in either the forward or reverse direction. , The corresponding clutch levers abut the second shaft member, and power can be transmitted.
　請求項６に記載の構成によれば、クラッチレバーは、付勢部材によって第２軸部材側に付勢されているため、第１軸部材が回転を始める際に確実にクラッチレバーを第２軸部材に当接させておくことができる。
　請求項７に記載の構成によれば、付勢部材は、第２軸部材を挟んで逆向きに少なくとも１つずつ配置されているクラッチレバーに挟持されているため、付勢部材の設置数を削減できるとともに、遠心クラッチを小型化できる。 According to the configuration of claim 6, since the clutch lever is biased toward the second shaft member side by the biasing member, when the first shaft member starts rotating, the clutch lever is surely moved to the second shaft member. It can be kept in contact with the member.
According to the configuration of claim 7, since the biasing member is clamped by the clutch levers arranged at least one in the opposite direction with the second shaft member interposed therebetween, the number of the biasing members to be installed can be reduced. The number can be reduced and the centrifugal clutch can be downsized.
　請求項８に記載の構成によれば、第１軸部材には、内部に円筒状の収容空間を有した外輪が設けられ、接続ピンは、収容空間内に配置されているため、遠心クラッチの回転数が上昇してクラッチシューが第２軸部材から離脱しても、クラッチレバーは収容空間内の最外部へぶつかるため、クラッチレバーが収容空間外へ大きく振り回されることがなくなり、遠心クラッチの周囲に大きな空間を設ける必要がない。
　請求項９に記載の構成によれば、接続部材は、回転軸方向に沿った一方の端部が第１軸部材の端部に固定され、端部から離れた位置で補強部材を介して第１軸部材の端部に固定されているため、接続部材にかかる応力を分散することができ、接続部材の一方の端部のみ第１軸部材に固定している場合と比べて、第１軸部材や接続部材のたわみを低減することができる。
　これによって、第１軸部材とクラッチレバーとの位置関係がずれることがなく、安定したトルク伝達が可能となる。 According to the configuration of claim 8, the first shaft member is provided with the outer ring having the cylindrical accommodation space therein, and the connection pin is disposed in the accommodation space. Even if the rotation speed increases and the clutch shoe disengages from the second shaft member, the clutch lever hits the outermost part in the housing space, so that the clutch lever is not swung largely outside the housing space, and the circumference of the centrifugal clutch is prevented. There is no need to provide a large space in.
According to the configuration of claim 9, one end of the connecting member along the rotation axis direction is fixed to the end of the first shaft member, and the connecting member is connected to the first end of the first shaft member via the reinforcing member at a position away from the end. Since it is fixed to the end portion of the one-shaft member, the stress applied to the connecting member can be dispersed, and the first shaft can be compared with the case where only one end portion of the connecting member is fixed to the first shaft member. It is possible to reduce the deflection of the member and the connecting member.
As a result, the positional relationship between the first shaft member and the clutch lever does not shift, and stable torque transmission becomes possible.
　請求項１０に記載の構成によれば、クラッチレバーが移動可能な範囲の所定の位置にあるとき、第１軸部材側を構成する全ての部材の合成重心が、第１軸部材の回転軸上に位置するため、遠心クラッチの回転動作による第１軸部材の振動を抑制し、第１軸部材の回転軸と第２軸部材の回転軸とのズレを防止できる。
　請求項１１に記載の構成によれば、正回転側クラッチレバーと逆回転側クラッチレバーとは、互いに接続ピンを回転中心として逆方向に連動回転するため、例えば、一方のクラッチレバーの摩擦面が第２軸部材から離脱すると、他方のクラッチレバーの摩擦面も連動してほぼ同時に第２軸部材から離脱する動作をするため、摩擦面の摩耗を抑制でき、トルク伝達の切り替えを迅速に実施できる。
　また、重力によるクラッチレバーの自重がクラッチレバーに対してどの方向にかかっても、互いに連動回転する正回転側クラッチレバーと逆回転側クラッチレバーとの間でクラッチレバーの自重を相殺できるため、遠心クラッチの回転方向の向きに関わらず、正回転側クラッチレバーと逆回転側クラッチレバーの動作をさらに安定化できる。 According to the configuration of claim 10, when the clutch lever is at a predetermined position within the movable range, the combined center of gravity of all the members forming the first shaft member side is on the rotation axis of the first shaft member. Since it is located at, the vibration of the first shaft member due to the rotation operation of the centrifugal clutch can be suppressed, and the deviation between the rotation shaft of the first shaft member and the rotation shaft of the second shaft member can be prevented.
According to the configuration of claim 11, since the forward rotation side clutch lever and the reverse rotation side clutch lever rotate in the opposite direction with the connecting pin as the center of rotation, the friction surface of one clutch lever is, for example, When disengaged from the second shaft member, the friction surface of the other clutch lever also interlocks and disengages from the second shaft member at substantially the same time, so wear of the friction surface can be suppressed and torque transmission can be switched quickly. ..
In addition, no matter which direction the gravity of the clutch lever is applied to the clutch lever due to gravity, the gravity of the clutch lever can be offset between the forward rotation side clutch lever and the reverse rotation side clutch lever that rotate in conjunction with each other. It is possible to further stabilize the operations of the forward rotation side clutch lever and the reverse rotation side clutch lever regardless of the direction of rotation of the clutch.
本発明の参考例である遠心クラッチ１００の正面断面図。The front sectional view of centrifugal clutch 100 which is a reference example of the present invention. 本発明の参考例である遠心クラッチ１００のクラッチレバー１１３が第２軸部材１２０に当接した状態を示す概略正面図。The schematic front view which shows the state which the clutch lever 113 of the centrifugal clutch 100 which is a reference example of this invention contact|abutted to the 2nd shaft member 120. 本発明の参考例である遠心クラッチ１００のクラッチレバー１１３が第２軸部材１２０から離脱した状態を示す概略正面図。The schematic front view showing the state where clutch lever 113 of centrifugal clutch 100 which is a reference example of the present invention has separated from the 2nd shaft member 120. クラッチレバーＣＳと第２軸部材Ｍとの動力伝達の関係を説明するための概略図。6 is a schematic diagram for explaining a power transmission relationship between a clutch lever CS and a second shaft member M. FIG. 本発明の一実施形態に係る遠心クラッチ２００の接続ピン２１７側斜視図。The connecting pin 217 side perspective view of the centrifugal clutch 200 which concerns on one Embodiment of this invention. 本発明の一実施形態に係る遠心クラッチ２００の揺動ピン２１８側斜視図。The perspective view of the rocking pin 218 side of centrifugal clutch 200 concerning one embodiment of the present invention. 本発明の一実施形態に係る遠心クラッチ２００の上面図。The top view of the centrifugal clutch 200 which concerns on one Embodiment of this invention. 本発明の一実施形態に係る遠心クラッチ２００の正面図。The front view of the centrifugal clutch 200 which concerns on one Embodiment of this invention. 本発明の一実施形態に係る遠心クラッチ２００のクラッチレバー２１３が第２軸部材２２０に当接した状態を示す概略正面図。The schematic front view which shows the state which the clutch lever 213 of the centrifugal clutch 200 which concerns on one Embodiment of this invention contact|abutted to the 2nd shaft member 220. 本発明の一実施形態に係る遠心クラッチ２００のクラッチレバー２１３が第２軸部材２２０から離脱した状態を示す概略正面図。The schematic front view which shows the state which the clutch lever 213 of the centrifugal clutch 200 which concerns on one Embodiment of this invention separated from the 2nd shaft member 220. As shown in FIG. 本発明の一実施形態に係る遠心クラッチ３００のクラッチレバー３１３と外輪接続部３１１ａとの接続関係を示す概略図。FIG. 3 is a schematic diagram showing a connection relationship between a clutch lever 313 and an outer ring connecting portion 311a of a centrifugal clutch 300 according to an embodiment of the present invention. 本発明の一実施形態に係る遠心クラッチ４００のクラッチレバー４１３とクラッチシュー４１４との接続関係を示す概略図。FIG. 6 is a schematic diagram showing a connection relationship between a clutch lever 413 and a clutch shoe 414 of the centrifugal clutch 400 according to the embodiment of the present invention. 本発明の一実施形態に係る遠心クラッチ５００の斜視図。The perspective view of the centrifugal clutch 500 which concerns on one Embodiment of this invention. 本発明の一実施形態に係る遠心クラッチ６００の概略正面図。The schematic front view of the centrifugal clutch 600 which concerns on one Embodiment of this invention.
　以下に本発明の参考例である遠心クラッチ１００について、図面に基づいて説明する。
　なお、説明のため、図２以降はクラッチレバー１１３を一つのみ設けた、時計回りの回転でのみ遠心クラッチ１００が機能する構成の概略図を使用する。 A centrifugal clutch 100 that is a reference example of the present invention will be described below with reference to the drawings.
For the sake of explanation, a schematic diagram of a configuration in which only one clutch lever 113 is provided and the centrifugal clutch 100 functions only in clockwise rotation will be used from FIG. 2 onward.
　本発明の参考例である遠心クラッチ１００は、図１に示すように、第１軸部材１１０および第１軸部材１１０と同一の回転軸で独立して回転可能に構成された第２軸部材１２０とが設けられ、第１軸部材１１０には、内部に円筒状の収容空間１１２を有した外輪１１１と、収容空間内１１２に配置された接続ピン１１７と、接続ピン１１７を介して回転軸と直交する面内で相対的に軸回転可能に第１軸部材１１０に接続されたクラッチレバー１１３とが設けられている。
　クラッチレバー１１３は、第２軸部材１２０を挟んで逆向きに１つずつ配置され、クラッチレバー１１３には、外輪１１１側に開放された収容穴１１８と、収容穴１１８に挿入され、クラッチレバー１１３を第２軸部材１２０側に僅かな力で付勢する付勢部材１１９と、第２軸部材１２０に当接可能に構成された摩擦面１１５を有したクラッチシュー１１４とが設けられている。 As shown in FIG. 1, a centrifugal clutch 100, which is a reference example of the present invention, has a first shaft member 110 and a second shaft member 120 configured to be independently rotatable on the same rotation shaft as the first shaft member 110. Is provided, and the first shaft member 110 has an outer ring 111 having a cylindrical housing space 112 therein, a connecting pin 117 arranged in the housing space 112, and a rotating shaft via the connecting pin 117. A clutch lever 113 connected to the first shaft member 110 is provided so as to be relatively rotatable in a plane orthogonal to each other.
The clutch levers 113 are arranged one by one in opposite directions with the second shaft member 120 interposed therebetween. The clutch lever 113 is inserted into the housing hole 118 opened to the outer ring 111 side and the housing hole 118, and the clutch lever 113 is inserted. An urging member 119 for urging the second shaft member 120 toward the second shaft member 120 with a slight force, and a clutch shoe 114 having a friction surface 115 configured to be capable of contacting the second shaft member 120 are provided.
　なお、クラッチレバー１１３の摩擦面１１５と第２軸部材１２０との当接面での動力の伝達関係は、摩擦面１１５上の力点１１６に集約することで、力点１１６での動力の伝達関係に置き換えることができる。
　また、クラッチレバー１１３は、力点１１６と接続ピン１１７の中心とを結んだ線Ｌ１と、力点１１６と第２軸部材１２０の中心とを結んだ線Ｌ２とが、角度θの傾きを有するように配置されている。
　また、クラッチレバー１１３の摩擦面１１５と第２軸部材１２０との当接面における静止摩擦係数（μとする）は、
μ＞ｔａｎθ
を満たすものである。 The power transmission relationship at the contact surface between the friction surface 115 of the clutch lever 113 and the second shaft member 120 is summarized in the power point 116 on the friction surface 115 to obtain the power transmission relationship at the power point 116. Can be replaced.
Further, in the clutch lever 113, a line L1 connecting the force point 116 and the center of the connecting pin 117 and a line L2 connecting the force point 116 and the center of the second shaft member 120 have an inclination of an angle θ. It is arranged.
Further, the static friction coefficient (μ) on the contact surface between the friction surface 115 of the clutch lever 113 and the second shaft member 120 is
μ>tan θ
To meet.
　次に、本発明の参考例である遠心クラッチ１００の、第１軸部材１１０を回転させた際の動作について、図２乃至図４を用いて説明する。 Next, the operation of the centrifugal clutch 100 that is a reference example of the present invention when the first shaft member 110 is rotated will be described with reference to FIGS. 2 to 4.
　まず、第１軸部材１１０の回転開始時における遠心クラッチ１００の動力伝達について説明する。
　第１軸部材１１０が時計回りに回転を始めると、図２に示すように、外輪１１１およびクラッチレバー１１３は時計回りに回転する方向へ力を受ける。
　このとき、付勢部材１１９によって、クラッチレバー１１３は第２軸部材１２０側に僅かな力で付勢されているため、第１軸部材１１０の回転開始時において、クラッチシュー１１４の摩擦面１１５は第２軸部材１２０に当接しており、クラッチレバー１１３は力点１１６を基準として、第２軸部材１２０に対して時計回りへ回転する方向へ動力を伝達することができる。
　すなわち、クラッチレバー１１３は、力点１１６で第２軸部材１２０を時計回りへ回転する方向へ駆動力（Ｆ１とする）を伝達している。 First, the power transmission of the centrifugal clutch 100 at the start of rotation of the first shaft member 110 will be described.
When the first shaft member 110 starts to rotate clockwise, as shown in FIG. 2, the outer ring 111 and the clutch lever 113 receive a force in a clockwise rotating direction.
At this time, since the clutch lever 113 is biased toward the second shaft member 120 side by the biasing member 119 with a slight force, the friction surface 115 of the clutch shoe 114 is changed when the first shaft member 110 starts rotating. Since the clutch lever 113 is in contact with the second shaft member 120, the clutch lever 113 can transmit power to the second shaft member 120 in the clockwise direction with respect to the force point 116.
That is, the clutch lever 113 transmits the driving force (referred to as F1) in the direction of rotating the second shaft member 120 in the clockwise direction at the power point 116.
　また、駆動力Ｆ１は、力点１１６から接続ピン１１７の中心軸に向かって引く力（Ｆとする）の分力として発生しているため、クラッチレバー１１３は力点１１６において第２軸部材１２０を接続ピン１１７の中心軸の方向に力Ｆで押していることになる。
　すなわち、第２軸部材１２０は、力点１１６において回転方向に駆動力Ｆ１（＝Ｆｓｉｎθ）を受けるとともに、第２軸部材１２０の中心軸の方向に分力Ｆ２（＝Ｆｃｏｓθ）で押されていることになり、同時にクラッチレバー１１３には力点１１６において分力Ｆ２と同じ大きさで反対向きにかかる垂直抗力（図示しない）が発生しているため、力点１１６における最大静止摩擦力はμＦ２である。 Further, since the driving force F1 is generated as a component force of a force (referred to as F) pulled from the power point 116 toward the central axis of the connecting pin 117, the clutch lever 113 connects the second shaft member 120 at the power point 116. This means that the force F is being pushed in the direction of the central axis of the pin 117.
That is, the second shaft member 120 receives the driving force F1 (=Fsinθ) in the rotational direction at the power point 116 and is pressed by the component force F2 (=Fcosθ) in the direction of the central axis of the second shaft member 120. At the same time, a vertical reaction force (not shown) having the same magnitude as the component force F2 and applied in the opposite direction is generated on the clutch lever 113 at the power point 116, so the maximum static friction force at the power point 116 is μF2.
　ここで、
μ＞ｔａｎθ
であるから、
μｃｏｓθ＞ｓｉｎθ
μＦｃｏｓθ＞Ｆｓｉｎθ
μＦ２＞Ｆ１
となることから、回転開始時において、確実にクラッチレバー１１３は滑ることなく第２軸部材１２０に動力伝達が可能である。
　また、くさび効果により、クラッチレバー１１３は第２軸部材１２０側に分力Ｆ２で引きつけられた状態を維持する。 here,
μ>tan θ
Therefore,
μcos θ>sin θ
μFcosθ>Fsinθ
μF2>F1
Therefore, at the start of rotation, the clutch lever 113 can reliably transmit power to the second shaft member 120 without slipping.
Further, due to the wedge effect, the clutch lever 113 maintains the state in which it is attracted to the second shaft member 120 side by the component force F2.
　次に、第１軸部材１１０の回転速度が上昇した状態における遠心クラッチ１００の動力伝達について説明する。
　第１軸部材１１０が回転すると、遠心力に起因して力点１１６から垂直抗力（図示しない）の方向にＦｒ（図示しない）が発生し、遠心クラッチ１００の回転速度が上昇するに従ってＦｒ（図示しない）も大きくなる。
　また、Ｆｒ（図示しない）はクラッチレバー１１３を第２軸部材１２０から離脱させる方向へ作用するため、クラッチレバー１１３は、
μ（Ｆ２－Ｆｒ）＞Ｆ１
を維持している間、滑ることなく第２軸部材１２０に動力伝達が可能である。
　このとき、第１軸部材１１０の回転速度が上昇し、より大きなＦｒ（図示しない）が発生した場合においても、クラッチレバー１１３が滑ることなく第２軸部材１２０に動力を伝達するには、Ｆ２がより大きく、且つ、Ｆ１がより小さくなるように各部材を配置する必要がある。
　ここで、
Ｆ１＝Ｆｓｉｎθ
Ｆ２＝Ｆｃｏｓθ
であるから、
Ｆ２＝Ｆ１／ｔａｎθ
となり、θが小さいほどＦ１に対してＦ２が大きくなる。
　すなわち、θがより小さくなるように力点１１６の位置を調整することで、第１軸部材１１０が速く回転してもクラッチレバー１１３が滑りにくくなり、第２軸部材１２０への動力伝達の効率を向上できる。 Next, power transmission of the centrifugal clutch 100 when the rotation speed of the first shaft member 110 is increased will be described.
When the first shaft member 110 rotates, Fr (not shown) is generated in the direction of vertical reaction force (not shown) from the force point 116 due to the centrifugal force, and Fr (not shown) as the rotational speed of the centrifugal clutch 100 increases. ) Will also grow.
Further, since Fr (not shown) acts in the direction of separating the clutch lever 113 from the second shaft member 120, the clutch lever 113 is
μ(F2-Fr)>F1
While maintaining, the power can be transmitted to the second shaft member 120 without slipping.
At this time, even if the rotation speed of the first shaft member 110 increases and a larger Fr (not shown) is generated, in order to transmit power to the second shaft member 120 without slipping the clutch lever 113, F2 It is necessary to arrange the respective members so that F1 is larger and F1 is smaller.
here,
F1=Fsin θ
F2=Fcos θ
Therefore,
F2=F1/tan θ
Thus, the smaller θ is, the larger F2 is than F1.
That is, by adjusting the position of the power point 116 so that θ becomes smaller, the clutch lever 113 is less likely to slip even if the first shaft member 110 rotates quickly, and the efficiency of power transmission to the second shaft member 120 is improved. Can be improved.
　第１軸部材１１０が高速回転し、Ｆｒ（図示しない）が大きくなりＦ２に近づくと、
μ（Ｆ２－Ｆｒ）≦Ｆ１
となり、クラッチレバー１１３は第２軸部材１２０上を僅かな時間滑り、さらに第１軸部材１１０の回転数が上昇すると、Ｆｒ（図示しない）はＦ２よりも大きくなることで、図３に示すように、クラッチレバー１１３は第２軸部材１２０から離脱し、第１軸部材１１０から第２軸部材１２０への動力の伝達を終了する。
　このとき、θを十分に小さくし、Ｆ１に対してＦ２を十分に大きくすることで、クラッチレバー１１３が第２軸部材１２０上を滑る時間を大幅に短縮することができ、クラッチシュー１１４の摩擦面１１５や第２軸部材１２０の摩耗を抑制できる。 When the first shaft member 110 rotates at high speed and Fr (not shown) increases and approaches F2,
μ(F2-Fr)≦F1
Then, the clutch lever 113 slides on the second shaft member 120 for a short time, and when the rotation speed of the first shaft member 110 further increases, Fr (not shown) becomes larger than F2, as shown in FIG. Then, the clutch lever 113 is disengaged from the second shaft member 120, and the transmission of power from the first shaft member 110 to the second shaft member 120 ends.
At this time, by sufficiently reducing θ and sufficiently increasing F2 with respect to F1, the time taken for the clutch lever 113 to slide on the second shaft member 120 can be significantly shortened, and the friction of the clutch shoe 114 can be reduced. Wear of the surface 115 and the second shaft member 120 can be suppressed.
　また、第２軸部材１２０から離脱したクラッチレバー１１３は、遠心クラッチ１００の外方に向けて振り回される力を受けるが、クラッチレバー１１３は外輪１１１に囲まれた収容空間１１２内に配置されており、クラッチレバー１１３は外輪１１１に当接する位置までしか移動できないため、遠心クラッチ１００の周囲にクラッチレバー１１３が飛び出すことはなく、遠心クラッチ１００の周囲に大きな空間を確保する必要がない。
　さらに、遠心クラッチ１００内には、僅かにクラッチレバー１１３を第２軸部材１２０側に付勢する付勢部材１１９以外の付勢部材がないため、収容空間１１２内の部品点数を削減できるとともに、遠心クラッチ１００内に大きな空間を確保する必要がなくなり、遠心クラッチ１００を小型化できる。 Further, the clutch lever 113 separated from the second shaft member 120 receives a force swung toward the outside of the centrifugal clutch 100, but the clutch lever 113 is arranged in the accommodation space 112 surrounded by the outer ring 111. Since the clutch lever 113 can move only to a position where it abuts the outer ring 111, the clutch lever 113 does not pop out around the centrifugal clutch 100, and it is not necessary to secure a large space around the centrifugal clutch 100.
Furthermore, since there is no biasing member in the centrifugal clutch 100 other than the biasing member 119 that slightly biases the clutch lever 113 toward the second shaft member 120, the number of parts in the housing space 112 can be reduced, and It is not necessary to secure a large space in the centrifugal clutch 100, and the centrifugal clutch 100 can be downsized.
　また、第２軸部材１２０から離脱したクラッチレバー１１３は、第１軸部材１１０が回転している間は遠心力によって外輪１１１側へ付勢されるため、第２軸部材１２０に当接することがない。
　さらに、再接続をコントロールするために弱い付勢部材を設けるだけでよく、回転数が低い状態でトルクの伝達のコントロールがきわめて容易となる。
　なお、摩擦面１１５と第２軸部材１２０との当接面の静止摩擦係数μを大きくすることで、より一層クラッチレバー１１３が滑ることなく第１軸部材１１０から第２軸部材１２０に動力を伝達することができる。 Further, the clutch lever 113 disengaged from the second shaft member 120 is urged toward the outer ring 111 side by the centrifugal force while the first shaft member 110 is rotating, so that the clutch lever 113 may come into contact with the second shaft member 120. Absent.
Furthermore, it suffices to provide a weak biasing member to control the reconnection, which makes it extremely easy to control the torque transmission at a low rotation speed.
In addition, by increasing the static friction coefficient μ of the contact surface between the friction surface 115 and the second shaft member 120, the power is transmitted from the first shaft member 110 to the second shaft member 120 without the clutch lever 113 slipping further. Can be communicated.
　次に、本発明の一実施形態である遠心クラッチ２００について、図５乃至図１０を用いて説明する。
　なお、説明のため、図５乃至図７は第１軸部材２１０および外輪２１１を図示しておらず、図９および図１０はクラッチレバー２１３ｂを図示していない。
　また、本発明の参考例である遠心クラッチ１００と共通する部分については、一部説明を省略する。 Next, a centrifugal clutch 200 that is an embodiment of the present invention will be described with reference to FIGS. 5 to 10.
For the sake of explanation, FIGS. 5 to 7 do not show the first shaft member 210 and the outer ring 211, and FIGS. 9 and 10 do not show the clutch lever 213b.
Further, a part of the description common to the centrifugal clutch 100 which is the reference example of the present invention will be omitted.
　本発明の一実施形態である遠心クラッチ２００は、図５乃至図８に示すように、第１軸部材２１０および第１軸部材２１０と同一の回転軸で独立して回転可能に構成された第２軸部材２２０とが設けられ、第１軸部材２１０には、内部に収容空間２１２を有した外輪２１１と、収容空間２１２に配置された外輪接続部２１１ａに両端を支持された接続ピン２１７と、接続ピン２１７を介して回転軸と直交する面内で相対的に軸回転可能に第１軸部材２１０に接続されたクラッチレバー２１３ａ、２１３ｂとが設けられている。 As shown in FIGS. 5 to 8, a centrifugal clutch 200 that is an embodiment of the present invention includes a first shaft member 210 and a first shaft member 210 that is independently rotatable about the same rotation shaft as the first shaft member 210. The biaxial member 220 is provided, and the first shaft member 210 has an outer ring 211 having a housing space 212 inside, and a connection pin 217 having both ends supported by an outer ring connecting portion 211 a arranged in the housing space 212. The clutch levers 213a and 213b are connected to the first shaft member 210 via the connecting pin 217 so as to be relatively rotatable in a plane orthogonal to the rotation axis.
　クラッチレバー２１３ａ、２１３ｂは、第２軸部材２２０を挟んで逆向きに２つずつ、クラッチレバー２１３ａ、２１３ｂの回転軸方向に設けられ、クラッチレバー２１３ａ、２１３ｂには、クラッチレバー２１３ａ、２１３ｂの回転軸と平行な揺動軸を有する揺動ピン２１８が接続されるとともに、揺動ピン２１８には、クラッチシュー２１４ａ、２１４ｂが揺動軸を中心に揺動可能に接続されている。 The clutch levers 213a and 213b are provided two by two in opposite directions with the second shaft member 220 interposed therebetween in the rotation axis direction of the clutch levers 213a and 213b. A swing pin 218 having a swing shaft parallel to the shaft is connected, and clutch shoes 214a and 214b are connected to the swing pin 218 so as to be swingable about the swing shaft.
　クラッチシュー２１４ａ、２１４ｂには、第２軸部材２２０との当接部に摩擦面２１５ａ、２１５ｂを有したライニング２２１ａ、２２１ｂが設けられ、第２軸部材２２０の外周面に沿うような弧状に形成されている。
　また、クラッチレバー２１３ａ、２１３ｂは、それぞれ付勢部材（図示しない）によって第２軸部材２２０側へ僅かな力で付勢されている。 The clutch shoes 214a, 214b are provided with linings 221a, 221b having friction surfaces 215a, 215b at the contact portions with the second shaft member 220, and formed in an arc shape along the outer peripheral surface of the second shaft member 220. Has been done.
Further, the clutch levers 213a and 213b are biased by a biasing member (not shown) toward the second shaft member 220 with a slight force.
　なお、図９に示すように、摩擦面２１５ａと第２軸部材２２０との当接面での動力の伝達関係は、摩擦面２１５ａの力点２１６に集約することで、力点２１６での動力の伝達関係に置き換えることができる。
　このとき、摩擦面２１５ａは、揺動ピン２１８によって第２軸部材２２０の外周面に対して傾きを調整されることで広範囲にわたって安定的に面接触している。
　また、力点２１６と接続ピン２１７の中心とを結んだ線をＬ１とし、力点２１６と第２軸部材２２０の中心とを結んだ線をＬ２とすると、クラッチレバー２１３ａは、Ｌ１とＬ２とが角度θの傾きを有するように配置されている。 As shown in FIG. 9, the power transmission relationship at the contact surface between the friction surface 215a and the second shaft member 220 is concentrated at the power point 216 of the friction surface 215a, so that the power transmission at the power point 216 is transmitted. Can be replaced by a relationship.
At this time, the friction surface 215a is in stable surface contact over a wide range by adjusting the inclination with respect to the outer peripheral surface of the second shaft member 220 by the swing pin 218.
When the line connecting the force point 216 and the center of the connecting pin 217 is L1, and the line connecting the force point 216 and the center of the second shaft member 220 is L2, the clutch lever 213a has an angle between L1 and L2. It is arranged so as to have an inclination of θ.
　また、ライニング２２１ａの摩擦面２１５ａと第２軸部材２２０との当接面における静止摩擦係数（μとする）は、
μ＞ｔａｎθ
を満たすものである。 The static friction coefficient (referred to as μ) at the contact surface between the friction surface 215a of the lining 221a and the second shaft member 220 is
μ>tan θ
To meet.
　次に、本発明の遠心クラッチ２００の、第１軸部材２１０を回転させた際の動作について、図９および図１０を用いて説明する。
　なお、クラッチレバー２１３ａ側の動作のみ説明する。 Next, the operation of the centrifugal clutch 200 of the present invention when the first shaft member 210 is rotated will be described with reference to FIGS. 9 and 10.
Only the operation on the clutch lever 213a side will be described.
　まず、第１軸部材２１０の回転開始時における遠心クラッチ２００の動力伝達について説明する。
　第１軸部材２１０が時計回りに回転を始めると、図９に示すように、外輪２１１、外輪接続部２１１ａ、クラッチレバー２１３ａは時計回りに回転する方向へ力を受ける。 First, the power transmission of the centrifugal clutch 200 at the start of rotation of the first shaft member 210 will be described.
When the first shaft member 210 starts to rotate clockwise, as shown in FIG. 9, the outer ring 211, the outer ring connecting portion 211a, and the clutch lever 213a receive a force in the clockwise direction.
　このとき、付勢部材（図示しない）によって、クラッチレバー２１３ａは第２軸部材２２０側に僅かな力で付勢されているため、第１軸部材２１０の回転開始時において、ライニング２２１ａの摩擦面２１５ａは第２軸部材２２０に当接しており、クラッチレバー２１３ａは力点２１６を基準として、第２軸部材２２０に対して時計回りへ回転する方向へ動力を伝達することができる。
　すなわち、クラッチレバー２１３ａは、力点２１６で第２軸部材２２０を時計回りへ回転する方向へ駆動力（Ｆ１とする）を伝達している。 At this time, the clutch lever 213a is biased by the biasing member (not shown) toward the second shaft member 220 side with a slight force. Therefore, at the start of rotation of the first shaft member 210, the friction surface of the lining 221a. 215a is in contact with the second shaft member 220, and the clutch lever 213a can transmit power to the second shaft member 220 in the clockwise rotation direction with reference to the force point 216.
That is, the clutch lever 213a transmits the driving force (referred to as F1) in the direction of rotating the second shaft member 220 in the clockwise direction at the power point 216.
　さらに、クラッチシュー２１４ａは揺動ピン２１８の中心軸を揺動軸として揺動可能に構成されているため、クラッチシュー２１４ａがクラッチレバー２１３ａに直接固定的に設けられている場合に比べて、ライニング２２１ａが第２軸部材２２０の外周面に合わせて向きを変えて当接することが可能となり、力点２１６の位置が安定的に維持される。
　また、摩擦面２１５ａの第２軸部材２２０との当接面を大きくとることができ、摩擦面２１５ａにかかる面圧を低減することができる。 Further, since the clutch shoe 214a is configured to be swingable with the center axis of the swing pin 218 as the swing axis, compared to the case where the clutch shoe 214a is directly and fixedly provided on the clutch lever 213a, the lining. The 221a can change its direction according to the outer peripheral surface of the second shaft member 220 and come into contact with the outer peripheral surface of the second shaft member 220, and the position of the force point 216 can be stably maintained.
Further, the contact surface of the friction surface 215a with the second shaft member 220 can be made large, and the surface pressure applied to the friction surface 215a can be reduced.
　また、駆動力Ｆ１は、力点２１６から接続ピン２１７の中心に向かって引く力（Ｆとする）の分力として発生しているため、クラッチレバー２１３ａは力点２１６において、第２軸部材２２０を力点２１６から接続ピン２１７の中心軸へ向かう方向に力Ｆで押していることになる。
　すなわち、第２軸部材２２０は、力点２１６において回転方向に駆動力Ｆ１（＝Ｆｓｉｎθ）を受けるとともに、第２軸部材２２０の中心軸の方向に分力Ｆ２（＝Ｆｃｏｓθ）で押されていることになり、同時にクラッチシュー２１４ａには力点２１６において分力Ｆ２と同じ大きさで反対向きにかかる垂直抗力（図示しない）が発生しているため、力点２１６における最大静止摩擦力はμＦ２である。 Further, since the driving force F1 is generated as a component force of a force (referred to as F) pulled from the power point 216 toward the center of the connecting pin 217, the clutch lever 213a causes the second shaft member 220 to move to the power point 216 at the power point 216. The force F pushes in the direction from 216 toward the central axis of the connecting pin 217.
That is, the second shaft member 220 receives the driving force F1 (=Fsin θ) in the rotational direction at the force point 216 and is pressed by the component force F2 (=Fcos θ) in the direction of the central axis of the second shaft member 220. At the same time, since a normal force (not shown) having the same magnitude as the component force F2 and applied in the opposite direction is generated on the clutch shoe 214a at the force point 216, the maximum static friction force at the force point 216 is μF2.
　よって、本発明の一実施形態の遠心クラッチ２００においても、
μＦ２＞Ｆ１
となり、回転開始時において、確実にクラッチレバー２１３ａは摩擦面２１５ａと第２軸部材２２０とを滑らせることなく、第２軸部材２２０に動力伝達が可能である。
　また、くさび効果により、クラッチシュー２１４ａは第２軸部材２２０に分力Ｆ２で引きつけられた状態を維持する。 Therefore, also in the centrifugal clutch 200 according to the embodiment of the present invention,
μF2>F1
Therefore, at the start of rotation, the clutch lever 213a can reliably transmit power to the second shaft member 220 without causing the friction surface 215a and the second shaft member 220 to slide.
Further, due to the wedge effect, the clutch shoe 214a maintains the state of being attracted to the second shaft member 220 by the component force F2.
　次に、第１軸部材２２０の回転速度が上昇した状態における遠心クラッチ２００の動力伝達について説明する。
　第１軸部材２１０が回転すると、遠心力に起因して力点２１６から垂直抗力（図示しない）の方向にＦｒ（図示しない）が発生し、遠心クラッチ２００の回転速度が上昇するに従ってＦｒ（図示しない）も大きくなる。
　また、Ｆｒ（図示しない）はクラッチシュー２１４ａをクラッチレバー２１３ａごと第２軸部材２２０から離脱させる方向へ作用するため、クラッチシュー２１４ａは、
μ（Ｆ２－Ｆｒ）＞Ｆ１
を維持している間、滑ることなく第２軸部材２２０に動力伝達が可能である。 Next, the power transmission of the centrifugal clutch 200 when the rotation speed of the first shaft member 220 is increased will be described.
When the first shaft member 210 rotates, Fr (not shown) is generated in the direction of vertical reaction force (not shown) from the force point 216 due to the centrifugal force, and Fr (not shown) increases as the rotation speed of the centrifugal clutch 200 increases. ) Will also grow.
Further, since Fr (not shown) acts in the direction of separating the clutch shoe 214a together with the clutch lever 213a from the second shaft member 220, the clutch shoe 214a is
μ(F2-Fr)>F1
While maintaining, the power can be transmitted to the second shaft member 220 without slipping.
　このとき、第１軸部材２１０の回転速度が上昇し、より大きなＦｒ（図示しない）が発生した場合においても、クラッチレバー２１３ａが滑ることなく第２軸部材２２０に動力を伝達するには、Ｆ２がより大きく、且つ、Ｆ１がより小さくなるように各部材を配置する必要があり、
Ｆ２＝Ｆ１／ｔａｎθ
の関係から、θが小さいほどＦ１に対してＦ２が大きくなる。
　すなわち、θがより小さくなるように力点２１６の位置を調整することで、第１軸部材２１０が速く回転してもクラッチシュー２１４ａが滑りにくくなり、第２軸部材２２０への動力伝達の効率を向上できる。 At this time, even if the rotational speed of the first shaft member 210 increases and a larger Fr (not shown) occurs, in order to transmit power to the second shaft member 220 without slipping the clutch lever 213a, F2 It is necessary to arrange each member so that is larger and F1 is smaller,
F2=F1/tan θ
From the relationship, the smaller θ is, the larger F2 is than F1.
That is, by adjusting the position of the power point 216 so that θ becomes smaller, even if the first shaft member 210 rotates quickly, the clutch shoe 214a becomes less slippery, and the efficiency of power transmission to the second shaft member 220 is improved. Can be improved.
　第１軸部材２１０が高速回転し、Ｆｒ（図示しない）が大きくなりＦ２に近づくと、
μ（Ｆ２－Ｆｒ）≦Ｆ１
となり、クラッチシュー２１４ａは第２軸部材２２０上を僅かな時間滑り、さらに第１軸部材２１０の回転数が上昇すると、Ｆｒ（図示しない）はＦ２よりも大きくなることで、図１０に示すように、クラッチシュー２１４ａはクラッチレバー２１３ａごと第２軸部材２２０から離脱し、第１軸部材２１０から第２軸部材２２０への動力の伝達を終了する。 When the first shaft member 210 rotates at high speed and Fr (not shown) increases and approaches F2,
μ(F2-Fr)≦F1
Then, the clutch shoe 214a slides on the second shaft member 220 for a short time, and when the rotation speed of the first shaft member 210 further increases, Fr (not shown) becomes larger than F2, as shown in FIG. Then, the clutch shoe 214a is disengaged from the second shaft member 220 together with the clutch lever 213a, and the transmission of power from the first shaft member 210 to the second shaft member 220 is completed.
　本発明の一実施形態である遠心クラッチ２００は、クラッチレバー２１３ａが、接続ピン２１７を介して回転軸と直交する面内で相対的に軸回転可能に外輪接続部２１１ａに２つ並べて接続されているため、クラッチレバー２１３ａを１つだけ外輪接続部２１１ａに接続する場合に比べて、クラッチレバー２１３ａが安定的に接続ピン２１７の中心軸を回転軸として回転できるとともに、接続ピン２１７のせん断面積が増え、接続ピン２１７のせん断応力が小さくなる。
　これによって、接続ピン２１７やクラッチレバー２１３ａ、外輪接続部２１１ａの材質を変えるなどして強度を上げることなく、伝達可能なトルクを増大させることができる。 In the centrifugal clutch 200 which is one embodiment of the present invention, two clutch levers 213a are connected to the outer ring connecting portion 211a side by side through the connecting pin 217 so as to be relatively rotatable relative to each other in a plane orthogonal to the rotation axis. Therefore, as compared with the case where only one clutch lever 213a is connected to the outer ring connecting portion 211a, the clutch lever 213a can stably rotate about the central axis of the connecting pin 217 and the shearing area of the connecting pin 217 becomes smaller. As a result, the shear stress of the connecting pin 217 decreases.
As a result, the torque that can be transmitted can be increased without increasing the strength by changing the materials of the connecting pin 217, the clutch lever 213a, and the outer ring connecting portion 211a.
　また、２つのクラッチレバー２１３ａには、クラッチレバー２１３ａの回転軸と平行な揺動軸を有する揺動ピン２１８が接続されるとともに、揺動ピン２１８には、クラッチシュー２１４ａが揺動軸を中心に揺動可能に接続されているため、クラッチレバー２１３ａを１つだけクラッチシュー２１４ａに接続する場合に比べて、クラッチシュー２１４ａが安定的に揺動ピン２１８の中心軸を揺動軸として揺動できるとともに、揺動ピン２１８のせん断面積が増え、揺動ピン２１８のせん断応力が小さくなる。
　これによって、揺動ピン２１８やクラッチレバー２１３ａ、クラッチシュー２１４ａの材質を変えるなどして強度を上げることなく、伝達可能なトルクをさらに増大させることができる。 A swing pin 218 having a swing shaft parallel to the rotation axis of the clutch lever 213a is connected to the two clutch levers 213a, and a clutch shoe 214a is centered around the swing shaft on the swing pin 218. Since only one clutch lever 213a is connected to the clutch shoe 214a, the clutch shoe 214a stably swings around the central axis of the swing pin 218 as compared with the case where only one clutch lever 213a is connected to the clutch shoe 214a. At the same time, the shear area of the swing pin 218 increases, and the shear stress of the swing pin 218 decreases.
As a result, the torque that can be transmitted can be further increased without increasing the strength by changing the materials of the swing pin 218, the clutch lever 213a, and the clutch shoe 214a.
　また、ライニング２２１ａの、第２軸部材２２０との当接範囲を大きくしても、クラッチシュー２１４ａをクラッチレバー２１３ａによって複数箇所で安定的に支持することができる。
　また、接続ピン２１７は、外輪接続部２１１ａに両端を支持されているため、接続ピン２１７のせん断面積が増えせん断応力が小さくなるとともに、クラッチ２００の動作中にクラッチレバー２１３ａや外輪接続部２１１ａから接続ピン２１７の曲げ方向に力がかかっても変形しにくく、クラッチレバー２１３ａを確実に正常な位置で支持できる。 Further, even if the contact range of the lining 221a with the second shaft member 220 is increased, the clutch shoe 214a can be stably supported at a plurality of points by the clutch lever 213a.
Further, since both ends of the connecting pin 217 are supported by the outer ring connecting portion 211a, the shearing area of the connecting pin 217 increases and the shear stress decreases, and the clutch lever 213a and the outer ring connecting portion 211a are operated during the operation of the clutch 200. Even if a force is applied in the bending direction of the connecting pin 217, the connecting pin 217 is unlikely to be deformed, and the clutch lever 213a can be reliably supported at a normal position.
　なお、本発明の一実施形態である遠心クラッチ２００は、第１軸部材２１０側を構成する全ての部材の合成重心を、可能な限り第１軸部材２１０の回転軸上に位置させることが望ましい。
　これによって、遠心クラッチ２００の動作中に第１軸部材２１０の振動を抑制することができ、第１軸部材２１０の回転軸と第２軸部材２２０の回転軸とのズレを防止できる。 In the centrifugal clutch 200 that is an embodiment of the present invention, it is desirable that the combined center of gravity of all the members that form the first shaft member 210 side be located on the rotation axis of the first shaft member 210 as much as possible. ..
With this, it is possible to suppress the vibration of the first shaft member 210 during the operation of the centrifugal clutch 200, and it is possible to prevent the deviation between the rotation shaft of the first shaft member 210 and the rotation shaft of the second shaft member 220.
　このとき、クラッチレバー２１３ａ、２１３ｂは、遠心クラッチ２００の動作中に接続ピン２１７を回転中心として移動して第２軸部材２２０に当接または離脱しているため、クラッチレバー２１３ａ、２１３ｂの位置によって第１軸部材２１０側を構成する全ての部材の合成重心の位置がわずかに変化する。
　そのため、最も第１軸部材２１０の振動を抑制したい状態でのクラッチレバー２１３ａ、２１３ｂの移動位置を考慮して、第１軸部材２１０側を構成する全ての部材の合成重心が第１軸部材２１０の回転軸に合うように設定することが望ましい。 At this time, since the clutch levers 213a and 213b move around the connecting pin 217 as the center of rotation during the operation of the centrifugal clutch 200 and come into contact with or separate from the second shaft member 220, depending on the positions of the clutch levers 213a and 213b. The positions of the combined center of gravity of all the members forming the first shaft member 210 side slightly change.
Therefore, in consideration of the moving positions of the clutch levers 213a and 213b in the state where the vibration of the first shaft member 210 is most desired to be suppressed, the combined center of gravity of all the members forming the first shaft member 210 side is the first shaft member 210. It is desirable to set so as to match the rotation axis of.
　次に、本発明の一実施形態に係る遠心クラッチ５００について、図１３を用いて説明する。
　なお、本発明の一実施形態に係る遠心クラッチ１００および遠心クラッチ２００と共通する部分については、一部説明を省略する。 Next, a centrifugal clutch 500 according to an embodiment of the present invention will be described with reference to FIG.
In addition, a part of the description common to the centrifugal clutch 100 and the centrifugal clutch 200 according to the embodiment of the present invention will be omitted.
　本発明の一実施形態に係る遠心クラッチ５００は、図１３に示すように、第１軸部材５１０および第１軸部材５１０と同一の回転軸で独立して回転可能に構成された第２軸部材５２０とが設けられている。
　第１軸部材５１０には、第１軸部材５１０と別体に形成された接続部材５１１ａの一方の端部が直接接続され、クラッチレバー５１３ａ、５１３ｂは、接続部材５１１ａに両端を支持された接続ピン（図示しない）を介して回転軸と直交する面内で相対的に軸回転可能に第１軸部材５１０に接続されている。 As shown in FIG. 13, a centrifugal clutch 500 according to an embodiment of the present invention includes a first shaft member 510 and a second shaft member that is independently rotatable on the same rotation shaft as the first shaft member 510. And 520 are provided.
One end of a connecting member 511a formed separately from the first shaft member 510 is directly connected to the first shaft member 510, and both ends of the clutch levers 513a and 513b are supported by the connecting member 511a. It is connected to the first shaft member 510 via a pin (not shown) so as to be relatively rotatable in a plane orthogonal to the rotation axis.
　接続部材５１１ａの端部のうち、第１軸部材５１０に直接接続されていない側の端部は、補強部材５３０を介して第１軸部材５１０に固定されている。
　すなわち、接続部材５１１ａは、両端を第１軸部材５１０に固定していることとなる。
　なお、補強部材５３０は、接続部材５１１ａの端部に直接接続している補強リング５３２と、第１軸部材５１０と補強リング５３２とを接続する補強柱５３１とで構成されている。 Of the end portions of the connection member 511 a, the end portion on the side not directly connected to the first shaft member 510 is fixed to the first shaft member 510 via the reinforcing member 530.
That is, both ends of the connecting member 511a are fixed to the first shaft member 510.
The reinforcing member 530 includes a reinforcing ring 532 that is directly connected to the end of the connecting member 511a, and a reinforcing column 531 that connects the first shaft member 510 and the reinforcing ring 532.
　これによって、遠心クラッチ５００作動時の接続部材５１１ａにかかる応力を接続部材５１１ａの両端から第１軸部材５１０へ分散でき、第１軸部材５１０や接続部材５１１ａのたわみを低減できるため、第１軸部材５１０とクラッチレバー５１３ａ、５１３ｂとの位置関係がずれることを防止でき、安定したトルク伝達が可能となる。
　また、補強部材５３０は、第１軸部材５１０の外縁に沿って配置した複数の補強柱５３２で補強リング５３１と第１軸部材５１０とを接続しているため、接続部材５１１ａにかかる応力を、第１軸部材５１０全体に分散させることができ、第１軸部材５１０とクラッチレバー５１３ａ、５１３ｂとの位置関係のズレをより一層防止でき、さらに安定したトルク伝達が可能となる。 Thereby, the stress applied to the connecting member 511a during the operation of the centrifugal clutch 500 can be dispersed from the both ends of the connecting member 511a to the first shaft member 510, and the deflection of the first shaft member 510 and the connecting member 511a can be reduced. The positional relationship between the member 510 and the clutch levers 513a and 513b can be prevented from shifting, and stable torque transmission can be performed.
Further, since the reinforcing member 530 connects the reinforcing ring 531 and the first shaft member 510 with the plurality of reinforcing columns 532 arranged along the outer edge of the first shaft member 510, the stress applied to the connecting member 511a is It is possible to disperse the first shaft member 510 as a whole, it is possible to further prevent the displacement of the positional relationship between the first shaft member 510 and the clutch levers 513a, 513b, and it is possible to further stably transmit the torque.
　次に、本発明の一実施形態に係る遠心クラッチ６００について、図１４を用いて説明する。
　なお、説明のため、図１４は第１軸部材、接続部材を図示していない。
　また、本発明の一実施形態に係る遠心クラッチ１００、２００、および５００と共通する部分については、一部説明を省略する。 Next, a centrifugal clutch 600 according to an embodiment of the present invention will be described with reference to FIG.
For the sake of explanation, FIG. 14 does not show the first shaft member and the connecting member.
Further, a part of the description common to the centrifugal clutches 100, 200, and 500 according to the embodiment of the present invention will be omitted.
　本発明の一実施形態に係る遠心クラッチ６００は、図１４に示すように、第１軸部材（図示しない）および第１軸部材（図示しない）と同一の回転軸で独立して回転可能に構成された第２軸部材６２０とが設けられている。
　第１軸部材（図示しない）には、接続部材（図示しない）の端部が接続され、正回転側クラッチレバー６１３ａおよび逆回転側クラッチレバー６１３ｂは、接続部材（図示しない）に両端を支持された接続ピンを介して回転軸と直交する面内で相対的に軸回転可能に第１軸部材（図示しない）に接続されている。 As shown in FIG. 14, a centrifugal clutch 600 according to an embodiment of the present invention is configured to be independently rotatable on a first shaft member (not shown) and the same rotation shaft as the first shaft member (not shown). Second shaft member 620 is provided.
An end of a connection member (not shown) is connected to the first shaft member (not shown), and both ends of the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b are supported by the connection member (not shown). It is connected to the first shaft member (not shown) so as to be relatively rotatable in the plane orthogonal to the rotation axis via the connecting pin.
　また、正回転側クラッチレバー６１３ａの接続ピン６１７に支持される側の端部にはギア凸部６３１が設けられ、逆回転側クラッチレバー６１３ｂの接続ピン６１７に支持される側の端部に設けられたギア凹部６３２と噛み合って連動ギア６３０を形成している。
　この連動ギア６３０によって、正回転側クラッチレバー６１３ａと逆回転側クラッチレバー６１３ｂとは、互いに接続ピン６１７を回転中心として逆方向に連動回転するため、例えば、正回転側クラッチレバー６１３ａの摩擦面６１５ａが第２軸部材６２０から離脱すると、逆回転側クラッチレバー６１３ｂの摩擦面６１５ｂも連動してほぼ同時に第２軸部材６２０から離脱するため、摩擦面６１５ａ、６１５ｂの摩耗を抑制でき、トルク伝達の切り替えを迅速に実施できる。 Further, a gear protrusion 631 is provided at an end of the forward rotation side clutch lever 613a supported by the connection pin 617, and a gear protrusion 631 is provided at an end of the reverse rotation side clutch lever 613b supported by the connection pin 617. The interlocking gear 630 is formed by meshing with the gear recessed portion 632.
By this interlocking gear 630, the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b rotate in the opposite direction about the connecting pin 617 as the center of rotation, and therefore, for example, the friction surface 615a of the forward rotation side clutch lever 613a. When the second shaft member 620 disengages from the second shaft member 620, the friction surface 615b of the reverse rotation side clutch lever 613b also interlocks and disengages from the second shaft member 620 almost at the same time, so that abrasion of the friction surfaces 615a and 615b can be suppressed and the torque transmission. Switching can be performed quickly.
　なお、正回転側クラッチレバーと逆回転側クラッチレバーとは、重力の作用する方向へそれぞれの自重が常にかかっている。
　これによって、例えば、正回転側クラッチレバーが第２軸部材に接触する方向へ重力が作用しているとき、逆回転側クラッチレバーには、第２軸部材から遠ざかる方向へ重力が作用することとなり、正回転側クラッチレバーと逆回転側クラッチレバーの第２軸部材への接触および離脱タイミングが不安定になる虞があった。
　しかし、本発明の一実施形態である遠心クラッチ６００の正回転側クラッチレバー６１３ａと逆回転側クラッチレバー６１３ｂとは、連動ギア６３０で互いに連動回転可能に構成されているため、ギア凸部６３１とギア凹部６３２とを介して正回転側クラッチレバー６１３ａと逆回転側クラッチレバー６１３ｂとにかかる自重を互いに打ち消すことができ、正回転側クラッチレバー６１３ａおよび逆回転側クラッチレバー６１３ｂの第２軸部材６２０への接触および離脱タイミングは乱れることがない。 It should be noted that the forward rotation side clutch lever and the reverse rotation side clutch lever always have their own weights in the direction in which gravity acts.
As a result, for example, when gravity acts in the direction in which the forward rotation side clutch lever contacts the second shaft member, gravity acts in the direction away from the second shaft member in the reverse rotation side clutch lever. However, there is a risk that the contact and release timings of the forward rotation side clutch lever and the reverse rotation side clutch lever with respect to the second shaft member may become unstable.
However, since the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b of the centrifugal clutch 600 according to the embodiment of the present invention are configured to be interlocked with each other by the interlocking gear 630, the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b can be rotated together with the gear protrusion 631. The weights of the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b can be canceled each other through the gear recess 632, and the second shaft member 620 of the forward rotation side clutch lever 613a and the reverse rotation side clutch lever 613b can be canceled. There is no disruption in the timing of contact and release.
　以上、本発明の実施形態を詳述したが、本発明は上記実施形態に限定されるものではなく、請求の範囲に記載された本発明を逸脱することなく種々の設計変更を行うことが可能である。 Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the claims. Is.
　なお、上述した実施形態では、クラッチレバーは、第２軸部材を挟んで逆向きに１つずつ配置されているものとして説明したが、クラッチレバーの数や配置方向はこれに限定されず、例えば、クラッチレバーが１つのみ、第２軸部材の正回転方向に配置されていてもよく、クラッチレバーが第２軸部材を挟んで逆向きに２つずつ配置されていてもよい。
　また、上述した実施形態では、クラッチレバーには、外輪側に開放された収容穴と、収容穴に挿入され、クラッチレバーを第２軸部材側に僅かな力で付勢する付勢部材とが設けられているものとして説明したが、クラッチレバーの態様はこれに限定されず、例えば、収容穴や付勢部材がなくてもよく、付勢部材が、外輪に設けられた収容穴から、クラッチレバーを付勢するように配置されていてもよい。 In addition, in the above-described embodiment, the clutch levers are described as being arranged one by one in opposite directions with the second shaft member interposed therebetween, but the number and arrangement direction of the clutch levers are not limited to this, and for example, Only one clutch lever may be arranged in the forward rotation direction of the second shaft member, or two clutch levers may be arranged in opposite directions with the second shaft member interposed therebetween.
Further, in the above-described embodiment, the clutch lever has the accommodation hole opened to the outer ring side and the urging member that is inserted into the accommodation hole and urges the clutch lever toward the second shaft member with a slight force. Although described as being provided, the aspect of the clutch lever is not limited to this, and for example, the accommodation hole or the urging member may not be provided, and the urging member is provided from the accommodation hole provided in the outer ring to the clutch. It may be arranged to bias the lever.
　また、上述した実施形態では、第１軸部材と第２軸部材とは、同一の回転軸を中心軸として互いに独立して回転可能に対向配置されているものとして説明したが、第１軸部材と第２軸部材の配置はこれに限定されず、例えば、中空筒状の第１軸部材に、第２軸部材が挿通されるように配置されていてもよい。
　また、上述した実施形態では、クラッチレバーが、接続ピンを介して回転軸と直交する面内で相対的に軸回転可能に外輪接続部に２つ並べて接続されているものとして説明したが、クラッチレバーの数はこれに限定されず、例えば、接続ピンを介して回転軸と直交する面内で相対的に軸回転可能に外輪接続部に３つ並べて接続されていてもよい。 Further, in the above-described embodiment, the first shaft member and the second shaft member are described as being rotatably opposed to each other independently of each other about the same rotation shaft as the central axis, but the first shaft member is described. The arrangement of the second shaft member and the second shaft member is not limited to this. For example, the second shaft member may be arranged to be inserted into the hollow cylindrical first shaft member.
Further, in the above-described embodiment, the clutch lever is described as being connected to the outer ring connecting portion side by side so as to be relatively rotatable in the plane orthogonal to the rotation axis via the connecting pin. The number of levers is not limited to this, and, for example, three levers may be connected side by side to the outer ring connecting portion so as to be relatively axially rotatable in a plane orthogonal to the rotation axis via a connecting pin.
　また、上述した実施形態では、クラッチレバーが、接続ピンを介して回転軸と直交する面内で相対的に軸回転可能に外輪接続部に２つ並べて接続されているものとして説明したが、クラッチレバーや外輪接続部の接続状態はこれに限定されず、例えば、図１１に示す遠心クラッチ３００のように、クラッチレバー３１３ａ、３１３ｂの接続ピン３１７との接続部が、櫛状に形成されていてもよく、櫛状に形成されたクラッチレバーの、接続ピンとの接続部に合わせて、外輪接続部側も櫛状に形成されていてもよい。
　また、上述した実施形態では、クラッチレバーには、クラッチレバーの回転軸と平行な揺動軸を有する揺動ピンが接続されるとともに、揺動ピンには、クラッチシューが揺動軸を中心に揺動可能に接続されているものとして説明したが、クラッチレバーやクラッチシューの接続状態はこれに限定されず、例えば、図１２に示す遠心クラッチ４００のように、クラッチレバー４１３ａ、４１３ｂがそれぞれ１つの大きなクラッチレバーとして設けられているとともに、クラッチレバー４１３ａ、４１３ｂの揺動ピン４１８との接続部が、櫛状に形成されていてもよく、櫛状に形成されたクラッチレバーの、揺動ピンとの接続部に合わせて、クラッチシュー側も櫛状に形成されていてもよい。 Further, in the above-described embodiment, the clutch lever is described as being connected to the outer ring connecting portion side by side so as to be relatively rotatable in the plane orthogonal to the rotation axis via the connecting pin. The connection state of the lever and the outer ring connecting portion is not limited to this. For example, as in the centrifugal clutch 300 shown in FIG. 11, the connecting portion of the clutch levers 313a and 313b with the connecting pin 317 is formed in a comb shape. Alternatively, the outer ring connecting portion side may also be formed in a comb shape so as to match the connecting portion of the clutch lever formed in a comb shape with the connecting pin.
Further, in the above-described embodiment, the clutch lever is connected to the swing pin having the swing shaft parallel to the rotation axis of the clutch lever, and the clutch shoe is connected to the swing pin about the swing shaft. Although it has been described that the clutch levers and the clutch shoes are connected so as to be swingable, the clutch levers 413a and 413b are not connected to each other, for example, as in the centrifugal clutch 400 shown in FIG. The clutch levers 413a and 413b may be formed in a comb shape at the connecting portion with the rocking pins 413a and 413b. The clutch shoe side may also be formed in a comb shape in accordance with the connection portion of the above.
　また、上述した実施形態では、クラッチシューは、第２軸部材との当接部に摩擦面を有したライニングが設けられ、第２軸部材の外周面に沿うような弧状に形成されているものとして説明したが、クラッチシューの構成はこれに限定されず、例えば、ライニングがなくてもよく、クラッチシューを平板状に形成して、一定量の変形が可能なライニングを所定の厚みをもたせてクラッチシューに貼り付け、第２軸部材の外周面との当接時にライニングが変形して摩擦面を広く形成するようにしてもよい。
　また、上述した実施形態では、第１軸部材には、内部に収容空間を有した外輪と、収容空間に配置された外輪接続部に両端を支持された接続ピンと、接続ピンを介して回転軸と直交する面内で相対的に軸回転可能に第１軸部材に接続されたクラッチレバーとが設けられているものとして説明したが、第１軸部材に設けられている各部材の構成はこれに限定されず、例えば、外輪や外輪接続部を設けずに、接続ピンが第１軸部材に直接両端を支持されるように設けられていてもよい。 Further, in the above-described embodiment, the clutch shoe is provided with a lining having a friction surface at the contact portion with the second shaft member, and is formed in an arc shape along the outer peripheral surface of the second shaft member. However, the configuration of the clutch shoe is not limited to this, and for example, the lining may not be provided, the clutch shoe may be formed in a flat plate shape, and the lining capable of being deformed by a certain amount may have a predetermined thickness. It may be attached to the clutch shoe, and the lining may be deformed at the time of contact with the outer peripheral surface of the second shaft member to form a wide friction surface.
Further, in the above-described embodiment, the first shaft member includes the outer ring having the accommodation space therein, the connection pins whose both ends are supported by the outer ring connection portion disposed in the accommodation space, and the rotating shaft via the connection pin. The clutch lever that is connected to the first shaft member so as to be relatively rotatable in the plane orthogonal to the above has been described, but the configuration of each member provided in the first shaft member is the same. However, the connection pins may be provided so that both ends are directly supported by the first shaft member without providing the outer ring or the outer ring connecting portion.
　また、上述した実施形態では、補強部材は、リング状の補強リングと補強柱とで構成されているものとして説明したが、補強部材の構成はこれに限定されず、例えば、２つの補強柱が接続部材を挟むように第１軸部材から回転軸に沿った方向へ伸び、接続部材の端部と補強柱の端部とを補強リングの代わりに棒状の連結部材で接続して第１軸部材に固定してもよく、補強部材が、回転軸方向から接続部材と第１軸部材とを挟みこむように接続部材の端部および第１軸部材の端部に固定されていてもよい。
　また、上述した実施形態では、接続部材は、接続部材の端部の一方を第１軸部材と直接接続され、端部の他方を補強部材を介して第１軸部材と接続されているものとして説明したが、接続部材と第１軸部材との接続形態はこれに限定されず、例えば、接続部材の一方の端部を第１軸部材と直接接続するとともに、接続部材の端部以外の位置で補強部材を介して第１軸部材と接続されていてもよく、接続部材と、第１軸部材と、補強部材の一部または全部が一体形成されていてもよい。 Further, in the above-described embodiment, the reinforcing member has been described as being configured by the ring-shaped reinforcing ring and the reinforcing column, but the configuration of the reinforcing member is not limited to this, and for example, two reinforcing columns are provided. The first shaft member extends in a direction along the rotation axis from the first shaft member so as to sandwich the connection member, and connects the end portion of the connection member and the end portion of the reinforcing column with a rod-shaped connecting member instead of the reinforcing ring. The reinforcing member may be fixed to the end portion of the connection member and the end portion of the first shaft member so as to sandwich the connection member and the first shaft member from the rotation axis direction.
Further, in the above-described embodiment, the connection member is configured such that one end of the connection member is directly connected to the first shaft member and the other end is connected to the first shaft member via the reinforcing member. Although described, the connection form of the connection member and the first shaft member is not limited to this, and for example, one end of the connection member is directly connected to the first shaft member, and a position other than the end of the connection member is provided. May be connected to the first shaft member via the reinforcing member, or the connecting member, the first shaft member, and a part or all of the reinforcing member may be integrally formed.
　また、上述した実施形態では、第１軸部材には、第１軸部材と別体に形成された接続部材の一方の端部が直接接続され、クラッチレバーは、接続部材に両端を支持された接続ピンを介して回転軸と直交する面内で相対的に軸回転可能に第１軸部材に接続されているものとして説明したが、第１軸部材と接続部材との接続方法はこれに限定されず、例えば、接続ピンの第１軸部材側の端部を接続部材を貫通するように設けて、接続ピンを第１軸部材に接続することで、接続部材を第１軸部材に位置決め接続するように構成してもよい。
　また、上述した実施形態では、正回転側クラッチレバーの接続ピンに支持される側の端部にはギア凸部が設けられ、逆回転側クラッチレバーの接続ピンに支持される側の端部に設けられたギア凹部と噛み合って連動ギアを形成して互いに連動回転するように構成しているものとして説明したが、正回転側クラッチレバーと逆回転側クラッチレバーとの関係はこれに限定されず、例えば、連動ギアを設けずに、正回転側クラッチレバーと逆回転側クラッチレバーとが連動回転しなくてもよく、正回転側クラッチレバーおよび逆回転側クラッチレバーの接続ピンに支持される側の端部の表面にゴム材を被覆して互いを当接させることで、正回転側クラッチレバーと逆回転側クラッチレバーとが連動回転するように構成してもよい。 Further, in the above-described embodiment, one end of the connecting member formed separately from the first shaft member is directly connected to the first shaft member, and both ends of the clutch lever are supported by the connecting member. Although it has been described that the first shaft member is connected to the first shaft member via the connection pin so as to be relatively rotatable in the plane orthogonal to the rotation shaft, the connection method of the first shaft member and the connection member is not limited to this. Instead, for example, the connection member is positioned and connected to the first shaft member by providing the end portion of the connection pin on the first shaft member side so as to penetrate the connection member and connecting the connection pin to the first shaft member. It may be configured to do so.
Further, in the above-described embodiment, the gear convex portion is provided at the end supported by the connecting pin of the forward rotation side clutch lever, and the gear convex portion is provided at the end supported by the connection pin of the reverse rotation side clutch lever. The description has been given assuming that the gears mesh with the provided gear recesses to form the interlocking gears and rotate in conjunction with each other, but the relationship between the forward rotation side clutch lever and the reverse rotation side clutch lever is not limited to this. , For example, the forward rotation side clutch lever and the reverse rotation side clutch lever do not have to rotate in conjunction without providing an interlocking gear, and the side supported by the connecting pin of the forward rotation side clutch lever and the reverse rotation side clutch lever. Alternatively, the forward rotation side clutch lever and the reverse rotation side clutch lever may be configured to rotate interlocked with each other by coating the surface of the end portion with a rubber material and bringing them into contact with each other.
　１００、２００、３００、４００、５００、６００　・・・　遠心クラッチ
　１１０、２１０、５１０　　　・・・　第１軸部材
　１１１、２１１　　　　　　　・・・　外輪
　２１１ａ、３１１ａ　　　　　・・・　外輪接続部
　５１１ａ　　　　　　　　　　・・・　接続部材
　１１２、２１２　　　　　　　・・・　収容空間
　１１３、２１３ａ、２１３ｂ、３１３ａ、３１３ｂ、４１３ａ、４１３ｂ、
　５１３ａ、５１３ｂ、ＣＳ　　・・・　クラッチレバー
　１１４、２１４ａ、２１４ｂ、３１４ａ、３１４ｂ、４１４ａ、４１４ｂ、
　５１４ａ、５１４ｂ、６１４ａ、６１４ｂ　・・・　クラッチシュー
　１１５、２１５ａ、２１５ｂ、６１５ａ、６１５ｂ　・・・　摩擦面
　１１６、２１６、Ｐ　　　　　・・・　力点
　１１７、２１７、３１７、６１７、Ｓ　・・・　接続ピン
　１１８　　　　　　　　　　　・・・　収容穴
　１１９　　　　　　　　　　　・・・　付勢部材
　１２０、２２０、３２０、４２０、５２０、６２０、Ｍ　・・・　第２軸部材
　２１８、３１８、４１８、５１８、６１８　・・・　揺動ピン
　２２１ａ、２２１ｂ、３１５ａ、３１５ｂ、
　６２１ａ、６２１ｂ　　　　　・・・　ライニング
　５３０　　　　　　　　　　　・・・　補強部材
　５３１　　　　　　　　　　　・・・　補強リング
　５３２　　　　　　　　　　　・・・　補強柱
　６３０　　　　　　　　　　　・・・　連動ギア
　６３１　　　　　　　　　　　・・・　ギア凸部
　６３２　　　　　　　　　　　・・・　ギア凹部
　ＭＳ　　　　　　　　　　　　・・・　第２軸部材の中心
　μ　　　　　　　　　　　　　・・・　力点での静止摩擦係数
　Ｆ　　　　　　　　　　　　　・・・　力点から接続ピンの中心方向へかかる力
　Ｆ１　　　　　　　　　　　　・・・　力点から第２軸部材の接線方向へかかる力
　Ｆ２　　　　　　　　　　　　・・・　力点から第２軸部材の中心方向へかかる力
　μＦ２　　　　　　　　　　　・・・　力点での最大静止摩擦力
　Ｌ１　　　　　　　　　　　　・・・　力点から接続ピンの中心まで伸ばした直線
　Ｌ２　　　　　　　　　　　　・・・　力点から第２軸部材の中心方向へ伸ばした直線

  100, 200, 300, 400, 500, 600... Centrifugal clutch 110, 210, 510... 1st shaft member 111, 211... Outer ring 211a, 311a... Outer ring connection part 511a... Connection member 112, 212... Accommodation spaces 113, 213a, 213b, 313a, 313b, 413a, 413b,
513a, 513b, CS... Clutch levers 114, 214a, 214b, 314a, 314b, 414a, 414b,
514a, 514b, 614a, 614b... Clutch shoe 115, 215a, 215b, 615a, 615b... Friction surface 116, 216, P... Power point 117, 217, 317, 617, S... Connection pin 118 ... accommodation hole 119 ... biasing member 120, 220, 320, 420, 520, 620, M ... second shaft member 218, 318, 418, 518, 618 ... rocking pin 221a, 221b 315a, 315b,
621a, 621b ・・・ Lining 530 ・・・ Reinforcing member 531 ・・・ Reinforcing ring 532 ・・・ Reinforcing column 630 ・・・ Interlocking gear 631 ・・・ Gear convex 632 ・・・ Gear concave MS ・・・ Second Center of shaft member μ ・・・ Static friction coefficient at power point F ・・・ Force applied from the power point toward the center of the connecting pin F1 ・・・ Force applied from the power point to the tangential direction of the second shaft member F2 ・・・ From the power point Force applied to the center of the second shaft member μF2 ・・・ Maximum static frictional force at the power point L1 ・・・ Straight line extending from the power point to the center of the connecting pin L2 ・・・ Extending from the power point toward the center of the second shaft member Straight line

Claims (11)

  1. 　第１軸部材および前記第１軸部材と同一の回転軸で独立して回転可能に構成された第２軸部材とを有し、
    　前記第１軸部材には、接続ピンを介して回転軸と直交する面内で相対的に軸回転可能に接続されたクラッチレバーが設けられ、
    　前記クラッチレバーには、前記第２軸部材に外周側から当接可能に構成された摩擦面を有したクラッチシューが設けられた遠心クラッチであって、
    　前記摩擦面と前記第２軸部材とが当接した状態における、前記接続ピンの中心から前記摩擦面の力点までを結んだ線と、前記第２軸部材の中心から前記摩擦面の力点までを結んだ線とがなす角度をθとし、前記摩擦面と前記第２軸部材とが当接した際の静止摩擦係数をμとしたとき、
    μ＞ｔａｎθ
    であるように配置され、
    　前記クラッチレバーには、前記クラッチレバーの回転軸と平行な揺動軸を有する揺動ピンが接続され、
    　前記クラッチシューは、前記揺動軸を中心に揺動可能に前記揺動ピンと接続されていることを特徴とする遠心クラッチ。     A first shaft member and a second shaft member configured to be independently rotatable on the same rotation shaft as the first shaft member,
    The first shaft member is provided with a clutch lever connected via a connection pin so as to be relatively rotatable in a plane orthogonal to the rotation shaft.
    A centrifugal clutch in which the clutch lever is provided with a clutch shoe having a friction surface configured to be capable of contacting the second shaft member from an outer peripheral side,
    A line connecting the center of the connecting pin to the force point of the friction surface and the center of the second shaft member to the force point of the friction surface in the state where the friction surface and the second shaft member are in contact with each other. When the angle formed by the joined lines is θ and the static friction coefficient when the friction surface and the second shaft member are in contact is μ,
    μ>tan θ
    Is arranged as
    A swing pin having a swing axis parallel to the rotation axis of the clutch lever is connected to the clutch lever,
    The centrifugal clutch, wherein the clutch shoe is connected to the swing pin so as to swing about the swing shaft.
  2. 　前記クラッチシューおよび前記クラッチレバーの少なくともいずれか一方は、前記揺動ピンと揺動軸方向に複数箇所で接続されていることを特徴とする請求項１に記載の遠心クラッチ。 The centrifugal clutch according to claim 1, wherein at least one of the clutch shoe and the clutch lever is connected to the swing pin at a plurality of positions in the swing axis direction.
  3. 　前記クラッチシューは、前記揺動軸方向に複数設けられていることを特徴とする請求項１または請求項２に記載の遠心クラッチ。 The centrifugal clutch according to claim 1 or 2, wherein a plurality of the clutch shoes are provided in the swing axis direction.
  4. 　前記クラッチレバーは、前記揺動軸方向に複数設けられていることを特徴とする請求項１乃至請求項３のいずれかに記載の遠心クラッチ。 The centrifugal clutch according to any one of claims 1 to 3, wherein a plurality of the clutch levers are provided in the swing axis direction.
  5. 　前記クラッチレバーは、前記第２軸部材を挟んで逆向きに少なくとも１つずつ配置されていることを特徴とする請求項１乃至請求項４のいずれかに記載の遠心クラッチ。 The centrifugal clutch according to any one of claims 1 to 4, wherein at least one clutch lever is arranged in the opposite direction with the second shaft member interposed therebetween.
  6. 　前記クラッチレバーは、付勢部材によって前記第２軸部材側に付勢されていることを特徴とする請求項１乃至請求項５のいずれかに記載の遠心クラッチ。 The centrifugal clutch according to any one of claims 1 to 5, wherein the clutch lever is biased toward the second shaft member side by a biasing member.
  7. 　前記付勢部材は、前記第２軸部材を挟んで逆向きに少なくとも１つずつ配置されている前記クラッチレバーに挟持されていることを特徴とする請求項６に記載の遠心クラッチ。 The centrifugal clutch according to claim 6, wherein the urging member is sandwiched by the clutch levers arranged at least one in the opposite direction with the second shaft member sandwiched therebetween.
  8. 　前記第１軸部材には、内部に円筒状の収容空間を有した外輪が設けられ、
    　前記接続ピンは、前記収容空間内に配置されていることを特徴とする請求項１乃至請求項７のいずれかに記載の遠心クラッチ。     An outer ring having a cylindrical accommodation space is provided inside the first shaft member,
    The centrifugal clutch according to any one of claims 1 to 7, wherein the connecting pin is arranged in the accommodation space.
  9. 　前記接続ピンは、接続部材に支持され、
    　前記接続部材は、回転軸方向に沿った一方の端部が前記第１軸部材の端部に固定され、前記端部から離れた位置で補強部材を介して前記第１軸部材の端部に固定されていることを特徴とする請求項１乃至請求項８のいずれかに記載の遠心クラッチ。     The connection pin is supported by a connection member,
    One end of the connecting member along the rotation axis direction is fixed to the end of the first shaft member, and is connected to the end of the first shaft member via a reinforcing member at a position apart from the end. The centrifugal clutch according to any one of claims 1 to 8, which is fixed.
  10. 　前記クラッチレバーが移動可能な範囲内の所定の位置にあるとき、前記第１軸部材側を構成する全ての部材の合成重心が、前記第１軸部材の回転軸上に位置することを特徴とする請求項１乃至請求項９のいずれかに記載の遠心クラッチ。 When the clutch lever is at a predetermined position within a movable range, the combined center of gravity of all the members forming the first shaft member side is located on the rotation axis of the first shaft member. The centrifugal clutch according to any one of claims 1 to 9.
  11. 　前記クラッチレバーは、正回転側クラッチレバーと、前記第２軸部材を挟んで前記正回転側クラッチレバーと逆向きに配置された逆回転側クラッチレバーとを有し、
    　前記正回転側クラッチレバーと前記逆回転側クラッチレバーとは、互いに前記接続ピンを回転中心として逆方向に連動回転するように構成されていることを特徴とする請求項１乃至請求項１０のいずれかに記載の遠心クラッチ。     The clutch lever includes a forward rotation side clutch lever, and a reverse rotation side clutch lever arranged in a direction opposite to the forward rotation side clutch lever with the second shaft member interposed therebetween,
    11. The forward rotation-side clutch lever and the reverse-rotation-side clutch lever are configured so as to interlock with each other in opposite directions about the connecting pin as a center of rotation. Centrifugal clutch described in Crab.
PCT/JP2019/045831 2018-11-30 2019-11-22 Centrifugal clutch WO2020110952A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2018224432 2018-11-30
JP2018-224432 2018-11-30
JP2019002718 2019-01-10
JP2019-002718 2019-01-10

Publications (1)

Publication Number Publication Date
WO2020110952A1 true WO2020110952A1 (en) 2020-06-04

Family

ID=70853709

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/045831 WO2020110952A1 (en) 2018-11-30 2019-11-22 Centrifugal clutch

Country Status (1)

Country Link
WO (1) WO2020110952A1 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4726768Y1 (en) * 1971-11-01 1972-08-17
JPS4832532B1 (en) * 1969-03-03 1973-10-06
JPS5980531A (en) * 1982-07-06 1984-05-10 Honda Motor Co Ltd Centrifugal clutch
WO2015182544A1 (en) * 2014-05-26 2015-12-03 株式会社ツバキＥ＆Ｍ Clutch

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4832532B1 (en) * 1969-03-03 1973-10-06
JPS4726768Y1 (en) * 1971-11-01 1972-08-17
JPS5980531A (en) * 1982-07-06 1984-05-10 Honda Motor Co Ltd Centrifugal clutch
WO2015182544A1 (en) * 2014-05-26 2015-12-03 株式会社ツバキＥ＆Ｍ Clutch

Similar Documents

Publication Publication Date Title
US11255385B2 (en) Clutch, in particular for a motorcycle, with pressure plate and centrifugal assembly
CN110454513B (en) Power transmission device
JP4990254B2 (en) Multi-plate clutch
WO2013061959A1 (en) Clutch device
WO2016143370A1 (en) Clutch device
WO2018083908A1 (en) Centrifugal clutch
WO2016088152A1 (en) Drum brake device
WO2020110952A1 (en) Centrifugal clutch
CN110520644B (en) Friction clutch
WO2020110950A1 (en) Centrifugal clutch
WO2014112163A1 (en) Multi-disk transmission
JP7017190B2 (en) Reverse input cutoff clutch
WO2018079505A1 (en) Toroidal continuously variable transmission
EP2899420B1 (en) Clutch device and straddle-type vehicle
JP4072741B2 (en) Synchronizer
CN104220777A (en) Torque fluctuation absorbing device and transmission
US20230160440A1 (en) Clutch
WO2022168466A1 (en) Reverse input blocking clutch
JP7311048B2 (en) reverse input cutoff clutch
JP7446516B2 (en) Centrifugal clutch and straddle vehicle
CN103542013A (en) Torque transmission device
JP5431530B2 (en) Twin clutch device
US1984797A (en) Variable speed power transmission mechanism
WO2018061628A1 (en) Clutch device
WO2018061640A1 (en) Clutch device

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: 19891184

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19891184

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP