JP2011220407A - One-way clutch device and pulley device provided with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a one-way clutch device which is compact in a radial direction and can suppress the deterioration in a function due to wear or the like.SOLUTION: The one-way clutch device 11 arranged between a pulley member 13 and a pulley boss 12 includes: a first clutch member 19 integrally rotatably connected to the pulley member 13; a second clutch member 20 which is connected to the pulley boss 12 integrally rotatably and relatively movably in the axial direction and is arranged opposite to the first clutch member 19 in the axial direction; a torsional coil spring 22 which energizes the second clutch member 20 in the axial direction to the first clutch member 19 side; an operation means which separates the second clutch member 20 from the first clutch member 19 in the axial direction according to the relative rotation in one direction between the first member 19 and the second clutch member 20; and a connecting means which connects the second clutch member 20 to the pulley member 13 in the axial direction when the second clutch member 20 is separated from the first clutch member 19.

Description

  The present invention relates to a one-way clutch device and a pulley device including the same.

  An alternator used as an auxiliary machine for an engine of an automobile or the like is driven by a rotational force extracted from a crankshaft and supplies electric power necessary for running the automobile. An alternator pulley device is attached to the input shaft of the alternator. A belt is laid between the alternator pulley device and a pulley attached to the crankshaft to transmit engine torque to the alternator. Yes.

  In general, a crankshaft of an engine such as an automobile is given a rotational force by an explosive force generated intermittently in a cylinder, so that the rotational speed fluctuates. On the other hand, an alternator has a relatively heavy armature or the like that rotates integrally with the input shaft inside the alternator. Therefore, if the crankshaft rotation speed fluctuates rapidly, the armature is caused by the inertial force generated by its own rotation. There may be a case where the rotational speed difference of the crankshaft cannot be followed and a rotational speed difference is temporarily generated between the crankshaft and the alternator. Such a difference in rotational speed causes slippage between the alternator pulley device and the belt and an excessive load on the belt, causing abnormal noise of the belt and shortening the service life. Further, if the initial tension of the belt is set to be relatively high in order to prevent the belt from slipping, there arises a problem that the rotational resistance of the crankshaft increases and the fuel efficiency performance of the engine is lowered.

  Under such circumstances, the conventional pulley device for an alternator includes a pulley member around which a belt is wound and a pulley boss fixed to the input shaft of the alternator in order to absorb fluctuations in rotational speed transmitted from the crankshaft. A one-way clutch device is provided between them.

  As this kind of one-way clutch device, the one described in Patent Document 1 is known, and this one-way clutch device is connected to be rotatable relative to each other via a rolling bearing 101 and a bush 102 as shown in FIG. The pulley boss 103 and the pulley member 104 are provided. A torsion coil spring 105 is fitted on the outer periphery of the pulley boss 103, and one end of the torsion coil spring 105 is in contact with a flange portion 106 formed at the other axial end of the pulley boss 103. The other end of the torsion coil spring 105 abuts on a carrier 107 disposed on the outer peripheral side of the pulley boss 103, and this carrier 107 is further biased by a thrust washer 108 coupled to the pulley boss 103 so as to be integrally rotatable. Are in pressure contact. One end of a clutch spring 109 is connected to the carrier 107, and the clutch spring 109 is fitted to the inner peripheral surface of the pulley member 104.

In the above configuration, when the rotation from the crankshaft is transmitted to the pulley member 104 via the belt, the outer diameter of the clutch spring 109 wound in the direction opposite to the rotation direction is expanded, and the inner diameter of the pulley member 104 is increased. Strongly adheres to the peripheral surface. As a result, the frictional force on the pulley member 104 is increased, and the carrier 107 is rotated integrally. Since the carrier 107 is frictionally coupled to the thrust washer 108 and the flange portion 106 by the biasing force of the torsion coil spring 105, the pulley boss 103 also rotates integrally.
When the rotational speed of the pulley boss 103 is higher than that of the pulley member 104 due to relatively large fluctuations in the rotational speed of the crankshaft, the outer diameter of the clutch spring 109 is reduced and the frictional force against the inner peripheral surface of the pulley member 104 is weakened. The pulley boss 103 and the pulley member 104 are configured to absorb the fluctuations by relative rotation. Note that minute fluctuations in the rotational speed of the crankshaft are absorbed by elastic deformation of the torsion coil spring 105 in the torsional direction.

Special table 2008-528906

  In the conventional one-way clutch device shown in FIG. 10, even when the outer diameter of the clutch spring 109 is reduced and the pulley member 104 and the pulley boss 103 rotate relative to each other, the outer peripheral surface of the clutch spring 109 becomes the inner peripheral surface of the pulley member 104. Touching and sliding. Therefore, wear of the clutch spring 109 becomes remarkable, and abnormal noise may be generated due to this wear, or the clutch function may be impaired due to seizure.

  Further, the conventional one-way clutch device has a drawback that the radial dimension is increased because the torsion coil spring 105 is provided on the outer periphery of the pulley boss 103 and the clutch spring 109 is provided on the outer periphery thereof. In other words, if the pulley member 104 is to be accommodated in a predetermined diameter, a sufficient storage space for the clutch spring 109 and the torsion coil spring 105 cannot be secured, and the wire diameter and outer diameter of these springs must be reduced. . For this reason, the degree of freedom in selecting parts is reduced, and it becomes difficult to obtain a desired spring constant and strength.

  The present invention has been made in view of the above circumstances, and is a one-way clutch device that can be compact in the radial direction and can suppress functional deterioration due to wear and the like, and a pulley including the same. An object is to provide an apparatus.

  The present invention is a one-way clutch device disposed between an outer peripheral side rotating body and an inner peripheral side rotating body disposed in the same axial center on the radially inner side of the outer peripheral side rotating body. A first clutch member coupled to one rotating body of the rotating body and the inner circumferential side rotating body so as to be integrally rotatable, and coupled to the other rotating body so as to be integrally rotatable and relatively movable in the axial direction; A second clutch member that is axially opposed to the first clutch member; an urging means that urges the second clutch member toward the first clutch member in the axial direction; and Operating means for causing the second clutch member to move away from the first clutch member in the axial direction by relative rotation of the clutch member and the second clutch member in one direction; and When separated from the clutch member 1 Characterized in that it comprises a coupling means for coupling said one rotary member and the second clutch member axially.

  In the one-way clutch device according to the present invention, when one rotating body and the other rotating body rotate relative to each other in one direction, the first clutch member and the second clutch member coupled to each other so as to rotate integrally are also moved in one direction. The relative rotation causes the actuating means to separate the second clutch member from the first clutch member in the axial direction. Then, the second clutch member is coupled to one of the rotating bodies in the axial direction by this separation operation, whereby the one rotating body and the other rotating body rotate integrally. From this state, when one rotating body and the other rotating body are rotated relative to each other in the other direction, the first clutch member and the second clutch member coupled to be integrally rotatable with each other also rotate in the other direction. Therefore, the second clutch member approaches the first clutch member by the urging force of the urging means, and the coupling with the one rotating body is released. As a result, the one rotating body and the other rotating body are separated from each other, and both can rotate relative to each other in the other direction.

  As described above, in the present invention, the second clutch member and the one rotating body are coupled in the axial direction by the relative rotation in one direction between the one rotating body and the other rotating body, and the first rotation by the relative rotation in the other direction. Since the coupling between the two clutch members and one of the rotating bodies can be completely released, the clutch spring is always in contact with the inner peripheral surface of the pulley member as in the conventional one-way clutch device shown in FIG. Compared with, there is less wear of parts, and the occurrence of abnormal noise and seizure of functions due to seizure are prevented. Further, since the second clutch member and the one rotary member are coupled in the axial direction, the clutch spring is accommodated on the inner peripheral side of the outer peripheral side rotary member such as a pulley member as in the conventional one-way clutch device. There is no need to secure a space, and the outer diameter of the outer peripheral rotating body can be reduced.

The actuating means includes the rolling element disposed to be capable of rolling between the first clutch member and the second clutch member, and the one of the first clutch member and the second clutch member. And a cam surface that moves the rolling element toward the second clutch member by relative rotation in a direction.
With such a configuration, the operation of separating the second clutch member from the first clutch member in the axial direction by a relative rotation in one direction between the first clutch member and the second clutch member is performed with a simple structure. Can do.

The rolling element may be constituted by a cylindrical roller that rolls on the cam surface in the circumferential direction, or may be constituted by a ball.
When the rolling element is constituted by a cylindrical roller, the contact range of the rolling element with respect to the first clutch member and the second clutch member can be expanded, and the allowable load of the rolling element can be increased and the durability can be improved. . Further, when the rolling elements are constituted by balls, it is possible to reduce the radial width of the first and second clutch members as compared to the cylindrical roller, and the radial dimension of the device incorporating this one-way clutch device Can be made smaller.

The actuating means may include a sprag disposed between the first clutch member and the second clutch member so that the posture can be changed.
With such a configuration, it is not necessary to form a cam surface or the like on the first clutch member, and the structure can be simplified.

The coupling means includes a contact surface provided on the second clutch member, and a contact surface provided on the one rotating body so as to face the contact surface in the axial direction, It is preferable that the second clutch member and the one rotating body are frictionally coupled by axial contact between the contact surface and the contacted surface.
According to this configuration, the second clutch member and the one rotating body can be smoothly coupled and released by contact and separation between the contact surface and the contacted surface.

The biasing means is interposed between the second clutch member and the other rotating body, and is frictionally coupled between the second clutch member and the other rotating body by being in pressure contact with both. It is preferable that
With such a configuration, not only can the second clutch member be urged toward the first clutch member by the urging means, but the second clutch member and the other rotating body can be coupled so as to be integrally rotatable. it can.

The pulley device of the present invention includes a pulley member around which a belt is wound around an outer periphery, a pulley boss disposed on the inner peripheral side of the pulley member in the same axial center as the pulley member, and the pulley member as an outer peripheral rotating body. And the one-way clutch device having any one of the above-described configurations, in which the pulley boss is provided as an inner peripheral side rotator.
The pulley device of the present invention has the same effects as the one-way clutch devices having the above-described configurations.

  ADVANTAGE OF THE INVENTION According to this invention, while being able to comprise a one-way clutch apparatus and a pulley apparatus compactly in radial direction, the function fall resulting from abrasion etc. can be suppressed.

It is front sectional drawing of the pulley apparatus (one-way clutch apparatus) which concerns on the 1st Embodiment of this invention. It is a side view of the 1st clutch member. It is a perspective view of the 1st clutch member. It is an expanded sectional view of the principal part of a one-way clutch apparatus. It is AA sectional drawing of FIG. It is an expanded sectional view of the important section of the one way clutch device concerning a 2nd embodiment of the present invention. It is BB sectional drawing of FIG. It is an expanded sectional view of the principal part of the one-way clutch apparatus which concerns on the 3rd Embodiment of this invention. It is CC sectional drawing of FIG. It is sectional drawing of the pulley apparatus which concerns on a prior art.

  FIG. 1 is a front sectional view of a pulley device (one-way clutch device) according to a first embodiment of the present invention. This pulley apparatus 10 is used by being attached to an input shaft of an alternator used as an engine auxiliary machine such as an automobile. The pulley device 10 includes a pulley boss 12 formed in a cylindrical shape, a cylindrical pulley member 13 disposed coaxially on the outer peripheral side of the pulley boss 12, and a one-way clutch device 11 interposed therebetween. ing.

  A wavy groove is formed on the outer peripheral surface 15 of the pulley member 13, and a belt for transmitting a rotational force from the crankshaft of the engine is wound around the outer peripheral surface 15. An input shaft protruding from an alternator (not shown) is inserted and fixed to the inner periphery of the pulley boss 12. Rolling bearings 16 and 17 are provided at both ends in the axial direction between the pulley member 13 and the pulley boss 12, and the pulley member 13 and the pulley boss 12 are connected by the rolling bearings 16 and 17 so as to be relatively rotatable. The rotation of the crankshaft is transmitted to the pulley member 13 through the belt, and the rotation of the pulley member 13 is transmitted to the pulley boss 12 through the one-way clutch device 11 to rotate the input shaft of the alternator.

  The one-way clutch device 11 includes a pair of clutch members (a first clutch member 19 and a second clutch member 20) facing each other in the axial direction, and a rolling element 21 disposed between the pair of clutch members 19 and 20. , And a torsion coil spring 22 disposed adjacent to the pair of clutch members 19 and 20.

FIG. 2 is a side view of the first clutch member 19, and FIG. 3 is a perspective view of the first clutch member 19.
As shown in FIGS. 1 to 3, the first clutch member 19 is an annular disc formed of a metal material such as bearing steel, and is fixed to the inner peripheral surface of the pulley member 13 so as to be integrally rotatable. Yes. As shown in FIGS. 2 and 3, a plurality of recesses 24 are formed at intervals in the circumferential direction on the side surface of the first clutch member 19 that faces the second clutch member 20. . The bottom surface 25 of each recess 24 is an inclined surface that is inclined so that one side in the circumferential direction is deep and the other side is shallow, and this inclined surface constitutes a cam surface described later. Further, as shown in FIG. 1, the opposite side surface of the first clutch member 19 is a flat surface without irregularities, and is in contact with the outer ring of the rolling bearing 16.

  As shown in FIG. 1, the second clutch member 20 is an annular member formed of a metal material such as bearing steel, and includes a disc portion 27 disposed along the radial direction, and the disc portion 27. Is formed in a substantially L-shaped cross section from a cylindrical portion 28 extending in the axial direction from the radially outer end portion to the opposite side to the first clutch member 19.

  The disc portion 27 is disposed so as to face the first clutch member 19 in the axial direction, and functions as a spring receiving portion that receives a biasing force from the torsion coil spring 22. The cylindrical portion 28 is a pulley as will be described later. It functions as a friction coupling portion for the member 13. Further, the side surface of the disc portion 27 facing the first clutch member 19 is formed as a flat surface without any irregularities.

  As shown in FIG. 1, the torsion coil spring 22 includes a side surface (contacted surface) 30 </ b> A of the flange portion 30 that protrudes radially outward from one end portion (right end portion) of the pulley boss 12, and a circle of the second clutch member 20. It arrange | positions between 27 A of side surfaces (contact surface) 27 A of the board part 27, and is compressed to the axial direction by these flange parts 30 and the disk part 27. FIG. The second clutch member 20 is pressed against the first clutch member 19 via the rolling elements 21 by the axial urging force of the torsion coil spring 22 and is frictionally rotatable with the flange portion 30 (the pulley boss 12). Are combined. The first clutch member 19 is pressed against the outer ring of the rolling bearing 16 by the axial biasing force of the torsion coil spring 22.

  One end (left end) of the torsion coil spring 22 engages with the second clutch member 20 in the circumferential direction, and the other end (right end) of the torsion coil spring 22 engages with the pulley boss 12 in the circumferential direction. ing. Therefore, when the second clutch member 20 rotates in one direction (forward rotation), the second clutch member 20 pushes one end of the torsion coil spring 22 in the circumferential direction, and the other end of the torsion coil spring 22 further The pulley boss 12 is pushed in the circumferential direction to transmit the rotation. Thereby, the 2nd clutch member 20 and the pulley boss | hub 12 can rotate integrally in one direction. The torsion coil spring 22 is elastically deformed in the direction of expanding the diameter by the integral rotation of the second clutch member 20 and the pulley boss 12 in one direction.

  As shown in FIG. 2, the rolling elements 21 are formed of cylindrical rollers, and one rolling element 21 is disposed in each recess 24 of the first clutch member 19 at substantially equal intervals in the circumferential direction. And the rolling element 21 is pinched | interposed between the 1st clutch member 19 and the 2nd clutch member 20, and is comprised so that it may roll in the circumferential direction by both relative rotation.

  4 is an enlarged cross-sectional view of a main part of the one-way clutch device 11, and FIG. 5 is a cross-sectional view taken along the line AA in FIG. The cylindrical portion 28 of the second clutch member 20 is disposed with a gap on the radially inner side of the inner peripheral surface of the pulley member 13. Further, the cylindrical portion 28 has an axial front end surface 33 opposed to the step surface 34 formed on the inner peripheral surface of the pulley member 13 with a gap therebetween in the axial direction.

  The first clutch member 19 rotates (forward rotation) in the direction of arrow a in FIG. 5 as the pulley member 13 is rotated by the power transmitted from the crankshaft. As a result, the rolling element 21 rolls on the cam surface 25 in the direction of the arrow c in the direction in which the gap S between the cam surface 25 and the disc portion 27 becomes narrow, and the second clutch member 20 moves in the direction of the arrow d. That is, it pushes in the direction away from the first clutch member 19. As a result, the facing distance between the first clutch member 19 and the second clutch member 20 is increased. Here, the cam surface 25 formed on the first clutch member 19 and the rolling element 21 rolling on the cam surface 25 separate the second clutch member 20 from the first clutch member 19 in the axial direction. The actuating means to be configured is configured.

  As shown in FIG. 4, when the second clutch member 20 moves in the direction of the arrow d, the front end surface 33 of the cylindrical portion 28 comes into contact with the step surface 34 of the pulley member 13, and both are frictionally coupled. Since the second clutch member 20 is coupled to the pulley boss 12 by the torsion coil spring 22 so as to be integrally rotatable, the rotation of the pulley member 13 is transmitted to the pulley boss 12 via the second clutch member 20 and the torsion coil spring 22. The pulley boss 12 rotates integrally with the pulley member 13. Here, the front end surface 33 of the cylindrical portion 28 and the stepped surface 34 of the pulley member 13 constitute a coupling means for coupling the second clutch member 20 and the pulley member 13.

  On the other hand, when the rotation speed of the pulley member 13 decreases due to the rotation fluctuation of the crankshaft and the pulley boss 12 cannot follow the rotation of the pulley member 13 due to the inertial force of the alternator, and rotates at a higher speed than the pulley member 13, As shown in FIG. 5, the first clutch member 19 rotates (reversely rotates) in the direction of the arrow b relative to the second clutch member 20, and the rolling element 21 is relatively in the direction opposite to the arrow c. Roll to. As a result, the second clutch member 20 moves in the direction opposite to the arrow d by the biasing force of the torsion coil spring 22, and the coupling with the pulley member 13 is released as shown in FIG. As a result, the pulley member 13 and the pulley boss 12 rotate relative to each other, and fluctuations in the rotational speed of the pulley member 13 are absorbed by the one-way clutch device 11. Therefore, it is possible to prevent slip between the pulley member 13 and the belt and an excessive load on the belt, and it is possible to prevent occurrence of abnormal noise of the belt and a decrease in service life.

  It should be noted that more minute rotational fluctuations of the pulley member 13 (crankshaft) can be released by allowing the relative rotation between the pulley member 13 and the pulley boss 12 by the elastic deformation of the torsion coil spring 22 in the torsional direction. It is absorbed without accompanying.

  In the pulley device 10 according to the present embodiment described above, the one-way clutch device 11 disposed between the pulley member 13 and the pulley boss 12 causes the second clutch member 20, the pulley member 13, Are coupled in the axial direction, and the coupling between the second clutch member 20 and the pulley member 13 is released by the reverse rotation of the pulley member 13. Therefore, compared with the case where the clutch spring is always in contact with the inner peripheral surface of the pulley member 13 as in the conventional one-way clutch device 11 shown in FIG. Reduction is prevented. Further, in the present embodiment, unlike the conventional one-way clutch device (see FIG. 10), it is not necessary to secure an accommodation space for the clutch spring on the inner peripheral side of the pulley member, so the outer diameter of the pulley member 13 is reduced. Thus, a more compact pulley device 10 can be formed.

Moreover, in this embodiment, since the cylindrical roller is used as the rolling element 21, the contact range with the 1st clutch member 19 and the 2nd clutch member 20 can be expanded, and these wear damages are suppressed. Life can be extended.
Further, the first clutch member 19 needs to be processed into a recess 24 (cam surface 25) that requires a certain degree of accuracy, but the other second clutch member 20, pulley member 13, pulley boss 12, etc. Since there is no complicated processing for operating the clutch, the manufacturing cost can be reduced.

FIG. 6 is an enlarged cross-sectional view of the main part of the one-way clutch device 11 according to the second embodiment of the present invention, and FIG. 7 is a cross-sectional view taken along line BB in FIG.
This embodiment is different from the first embodiment in that the rolling elements 21 arranged between the first and second clutch members 19 and 20 are not cylindrical rollers but balls. Further, in order to form this ball trajectory, a holding groove 39 is formed in the circumferential direction on the bottom surface (cam surface) 25 of the recess 24. Since other configurations and operational effects are substantially the same as those of the first embodiment, detailed description thereof is omitted.
In the present embodiment, a ball having a smaller radial dimension than the cylindrical roller is used as the rolling element 21, so that the radial width and outer diameter dimension of the first clutch member 19 and the second clutch member 20 are reduced. There are advantages that can be done.

FIG. 8 is an enlarged cross-sectional view of the main part of the one-way clutch device 11 according to the third embodiment of the present invention, and FIG. 9 is a cross-sectional view taken along the line CC in FIG.
In the present embodiment, the sprag 41 is disposed between the first and second clutch members 19 and 20, and the side surface of the first clutch member 19 facing the second clutch member 20 is flat without a recess. Formed on the surface. A plurality of sprags 41 are provided at intervals in the circumferential direction, and the circumferential intervals are held by a retainer 44.

  As shown in FIG. 9, the sprag 41 includes a first contact surface 42 that contacts the first clutch member 19 and a second contact surface 43 that contacts the second clutch member 20. The contact surface 42 and the second contact surface 43 are each formed in a convex and substantially arc shape. Further, the distance between the first contact surface 42 and the second contact surface 43 that are in contact with the first clutch member 19 and the second clutch member 20 varies depending on the inclination of the sprag 41, and the first clutch When the member 19 rotates in the direction of arrow a, the sprag 41 tilts in the direction of arrow e, and the distance between the first contact surface 42 and the second contact surface 43 increases. Conversely, when the first clutch member 19 rotates in the direction of arrow b, the sprag 41 tilts in the direction opposite to the arrow e, and the distance between the first contact surface 42 and the second contact surface 43 decreases. .

When the distance between the first contact surface 42 and the second contact surface 43 is increased, the second clutch member 20 is pushed in the direction of the arrow d and frictionally coupled to the pulley member 13. When the distance between the surface 42 and the second contact surface 43 is reduced, the second clutch member 20 returns in the direction opposite to the arrow d, and the coupling with the pulley member 13 is released.
In the present embodiment, in addition to the same effects as in the first embodiment, it is not necessary to form a recess (cam surface) in the first clutch member 19, so that the manufacturing cost can be reduced.

The present invention is not limited to the above-described embodiment, and the design can be changed as appropriate.
For example, the one-way clutch device 11 of the present invention is not limited to the pulley device 10 described above, and can be used for various applications. In particular, the one-way clutch device 11 is preferably used for a device in which the radial dimension of the rotating body is limited. it can.

The second clutch member 20 and the pulley boss 12 are frictionally coupled by a torsion coil spring (biasing means) 22, but are coupled so as to be integrally rotatable by other means (engagement means, connection means, etc.) different from this. May be.
The biasing means 22 that biases the second clutch member 20 toward the first clutch member 19 is not limited to a torsion coil spring, and other components such as a leaf spring and a rubber-like elastic body can be applied. .

  In the said 1st, 2nd embodiment, in order to hold | maintain the space | interval and attitude | position of the some rolling element 21 to predetermined, you may provide a holder | retainer.

  DESCRIPTION OF SYMBOLS 10: Pulley apparatus, 11: One-way clutch apparatus, 12: Pulley boss | hub (inner peripheral side rotary body), 13: Pulley member (outer peripheral side rotary body), 19: 1st clutch member, 20: 2nd clutch member, 21 : Rolling element, 22: torsion coil spring (biasing means), 25: cam surface, 27A: contact surface, 28: cylindrical portion, 30A: contacted surface, 33: tip surface (coupling surface; coupling means), 34 : Step surface (coupling surface; coupling means), 41: Sprag

Claims (8)

A one-way clutch device disposed between an outer circumferential rotating body and an inner circumferential rotating body disposed in the same axial center on the radially inner side of the outer circumferential rotating body,
A first clutch member coupled to one rotating body of the outer circumferential side rotating body and the inner circumferential side rotating body so as to be integrally rotatable;
A second clutch member coupled to the other rotating body so as to be integrally rotatable and relatively movable in the axial direction, and facing the first clutch member in the axial direction;
Biasing means for biasing the second clutch member in the axial direction toward the first clutch member;
An operating means for moving the second clutch member away from the first clutch member in the axial direction by relative rotation in one direction between the first clutch member and the second clutch member;
A coupling means for coupling the second clutch member and the one rotating body in the axial direction when the second clutch member is separated from the first clutch member;
A one-way clutch device characterized by comprising: The operating means is
A rolling element disposed so as to be capable of rolling between the first clutch member and the second clutch member;
A cam surface that moves the rolling element toward the second clutch member by the relative rotation in the one direction between the first clutch member and the second clutch member;
The one-way clutch apparatus of Claim 1 provided with.   The one-way clutch device according to claim 2, wherein the rolling element is constituted by a cylindrical roller that rolls on the cam surface in a circumferential direction.   The one-way clutch device according to claim 2, wherein the rolling element is configured by a ball that rolls on the cam surface in a circumferential direction.   2. The one-way clutch device according to claim 1, wherein the actuating means includes a sprag disposed between the first clutch member and the second clutch member so as to be capable of changing a posture. The coupling means includes
A contact surface provided on the second clutch member; and a contact surface formed on the one rotating body so as to face the contact surface in the axial direction; 6. The one-way clutch device according to claim 1, wherein the second clutch member and the one rotating body are frictionally coupled by axial contact with the contacted surface.   The biasing means is interposed between the second clutch member and the other rotating body, and is frictionally coupled between the second clutch member and the other rotating body by being in pressure contact with both. The one-way clutch device according to any one of claims 1 to 6. A pulley member around which a belt is wound;
A pulley boss disposed on the inner peripheral side of the pulley member and in the same axial center as the pulley member;
The one-way clutch device according to any one of claims 1 to 7, wherein the pulley member is used as an outer peripheral rotating body, and the pulley boss is provided as an inner peripheral rotating body.
A pulley apparatus comprising:

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