JP2012026558A - One-way clutch device and pulley device having the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a one-way clutch device, compact in the radial direction, and capable of restraining functional reduction by abrasion.SOLUTION: This one-way clutch device includes a first clutch member 19, a second clutch member 20, a rolling element 21 rollably arranged between the first clutch member 19 and the second clutch member 20, and a retainer 40 provided with a pocket part 41 for rollably holding the rolling element 21. An inclined face 24 contacting with the rolling element 21 is formed on at least one end surface among opposed end surfaces of the first clutch member 19 and the second clutch member 20, and a step surface 26 is formed between the inclined faces on the end surfaces. An engaging projection part 42 engaging in the circumferential direction with the step surface 26 is arranged in the retainer 40.

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, the rotation from the crankshaft is caused by 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 clutch spring 109 is tightly adhered to the inner peripheral surface of the pulley member 104. As a result, the frictional force on the pulley member 104 is increased, and the carrier 107 is rotated integrally. The carrier 107 is composed of a torsion coil spring 10.
Since the thrust washer 108 and the flange portion 106 are frictionally coupled by the urging force of 5, 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. 6, 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 of the rotating body and the inner rotating body, and the other rotating body of the outer rotating body and the inner rotating body. And a second clutch member that is coupled to be axially movable relative to the first clutch member in the axial direction, and the second clutch member is axially moved toward the first clutch member. An urging means for urging the rolling element, a rolling element disposed between the first clutch member and the second clutch member so as to be capable of rolling, and a plurality of circumferentially disposed rolling elements, and the first clutch. Arranged between the member and the second clutch member, the rolling A cage that is provided with a plurality of pocket portions in a circumferential direction to hold the roller, and when the second clutch member is separated from the first clutch member, the second clutch member and the one clutch A slanting surface with which the rolling element contacts at least one of the opposing end surfaces of the first clutch member and the second clutch member. Are formed in a circumferential direction, and a step surface is formed between the inclined surfaces of the end surfaces of the first clutch member and the second clutch member facing each other. An engaging protrusion that engages with the surface in the circumferential direction is provided so as to protrude in the axial direction from the cage toward the step surface.

  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. Rotating relative to each other, the rolling element rolls on the inclined surface, and the second clutch member is separated 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.

  Further, when the outer diameter of the rolling element is increased to increase the torque capacity, the member that pushes the rolling element from the circumferential direction needs to be increased in accordance with the outer diameter of the rolling element. Since the rolling element is engaged with the step surface in the circumferential direction, the shape of the engaging protrusion of the cage that can be easily molded may be adjusted, and the step surface shape that requires a large amount of work is greatly changed. There is no need. As a result, there is an advantage that forging of one of the rotating bodies of the first clutch member and the second clutch member having the stepped surface is facilitated, and damage to the forging die is reduced.

  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 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 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 by forging and cutting from a metal material such as bearing steel, and rotates integrally with the inner peripheral surface of the pulley member 13. It is fixed as possible. As shown in FIGS. 2 and 3, a plurality of inclined surfaces 24 are formed at equal intervals in the circumferential direction on the end surface of the first clutch member 19 facing the second clutch member 20. The inclined surface 24 is formed in the tangential direction e at each point on the circumference. Moreover, since the inclined surface 24 is formed so as to be inclined with respect to the tangential direction e, the inclined surface 24 is closest to the second clutch member 19 on one side of the tangential direction e, and is inclined in the tangential direction e. On the other side, the inclined surface 24 is furthest away from the second clutch member 19. A plane 25 perpendicular to the rotation axis of the first clutch member 19 is formed between the inclined surfaces 24. On the other side of the tangential direction e, the inclined surface 24 is greatly recessed with respect to the plane 25, and a step surface 26 perpendicular to the tangential direction e is formed between the inclined surface 24 and the plane 25. Further, as shown in FIG. 1, the opposite end surface of the first clutch member 19 is a flat surface without unevenness, 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 by forging and cutting from a metal material such as bearing steel, and a disk portion 27 arranged along the radial direction; The disk portion 27 is formed in a substantially L-shaped cross section from a cylindrical portion 28 extending from the radially outer end portion of the disk portion 27 toward the opposite side to the first clutch member 19 in the axial direction.

  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 end surface of the disc portion 27 facing the first clutch member 19 is formed as a flat surface without 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 made of cylindrical rollers, and are arranged one by one on each inclined surface 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 it is comprised so that it may roll in the tangential direction of each point on the circumference by relative rotation of both. Yes.

  As shown in FIG. 5, between the first clutch member 19 and the second clutch member 20, a cage 40 made of a plate-like metal material by a press or the like is disposed. A pocket portion 41 that holds the moving body 21 so as to be able to roll is provided. The pocket part 41 has the same number as the rolling element 21 in the circumferential direction. The pocket portion 41 is a rectangular window penetrating in the axial direction of the cage 40, and only one side of the rectangular shape is formed by a side surface 42 a of the engagement protrusion 42 that is bent at a right angle toward the first clutch member 19 side. It is formed. A side surface 42 b of the engaging protrusion 42 opposite to the rolling element 21 is engaged with the step surface 26 in the rotation direction of the first clutch member 19.

  In order to increase the torque transmission force of the one-way clutch device 11, it is necessary to increase the contact area between the inclined surface 24 and the rolling element 21 and increase the contact area between the rolling element 21 and the end surface of the second clutch member 20. In order to increase the contact area, either an increase in the outer diameter of the rolling element 21 or an increase in the length of the rolling element 21 can be considered. Increasing the length of the rolling element 21 is a pulley. Increasing the outer diameter of the device 10 and increasing the outer diameter of the rolling element 21 will increase the axial length of the pulley device 10. The pulley apparatus 10 used for the alternator has a limit on the outer diameter and an allowance in the axial length.

  When the rolling element 21 is directly engaged with the step surface 26, if the outer diameter of the rolling element 21 is increased in order to increase the torque transmission force, the step surface 26 needs to be enlarged accordingly. When the step surface 26 becomes large, a portion corresponding to the step surface 26 of the forging die for forging the first clutch member 19 becomes deep, and the forging die is easily damaged. By using the cage 40 provided with the engagement protrusion 42, it is not necessary to enlarge the step surface 26, and the portion corresponding to the step surface 26 of the forging die for forging the first clutch member 19 is shallow. It is possible to minimize damage to the forging die.

  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 inclined surface 25 in the direction of the arrow c toward the direction in which the gap S between the inclined surface 25 and the disk 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 inclined surface 25 formed on the first clutch member 19 and the rolling element 21 rolling on the inclined 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 urging force of the torsion coil spring 22, and the coupling with the pulley member 13 is released. 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 this embodiment, unlike the conventional one-way clutch device (see FIG. 6), it is not necessary to secure a storage 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 process the inclined surface 24 (inclined 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.

The present invention can be appropriately changed without being limited to the above embodiment.
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.

  For example, 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.

The inclined surface 24, the flat surface 25, and the step surface 26 are formed on the first clutch member 19, but the end surface on the second clutch member 20 side of the first clutch member 19 is made a flat surface without any irregularities, An inclined surface, a flat surface, and a step surface may be formed on the end surface of the clutch member 20 on the first clutch member 19 side.
Furthermore, an inclined surface, a flat surface, and a step surface may be formed on opposite end surfaces of the first clutch member 19 and the second clutch member 20.

  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), 24: inclined surface, 26: stepped surface, 27A: contact surface, 28: cylindrical portion, 30A: contacted surface, 33: tip surface (coupling surface; Coupling means), 34: stepped surface (coupling surface; coupling means), 40: retainer, 42: engaging protrusion

Claims (6)

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 rotating body coupled to the other rotating body of the outer circumferential rotating body and the inner circumferential rotating body so as to be integrally rotatable and relatively movable in the axial direction, and opposed to the first clutch member in the axial direction. A clutch member;
Biasing means for biasing the second clutch member in the axial direction toward the first clutch member;
A rolling element disposed between the first clutch member and the second clutch member so as to be capable of rolling, and a plurality of rolling elements disposed in a circumferential direction;
A cage that is disposed between the first clutch member and the second clutch member, and that has a plurality of pocket portions in the circumferential direction for holding the rolling elements in a rollable manner;
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 plurality of inclined surfaces in contact with the rolling elements are formed in at least one of the opposing end surfaces of the first clutch member and the second clutch member in the circumferential direction;
A step surface is formed between the inclined surfaces of the end surfaces where the inclined surfaces are formed among the opposing end surfaces of the first clutch member and the second clutch member,
An one-way clutch device characterized in that an engaging protrusion that engages with the step surface in the circumferential direction is provided so as to protrude in the axial direction from the retainer to the step surface side.   The one-way clutch device according to claim 1, 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 1, wherein the rolling element is constituted by a ball that rolls on the cam surface in a circumferential direction. 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; The one-way clutch device according to any one of claims 1 to 3, 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 4. A pulley member around which a belt is wound;
A pulley boss disposed on the inner peripheral side of the pulley member and having the same axial center as the pulley member; The one-way clutch device according to any one of 5;
A pulley apparatus comprising:

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