JP6125376B2 - One way clutch - Google Patents

Description

  In the present invention, a plurality of rollers held in a cage disposed between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member are urged in the circumferential direction by an engagement spring, and the inner member and the outer member are moved in one direction. The present invention relates to a one-way clutch that transmits a driving force by biting the roller between the outer peripheral surface and the inner peripheral surface by relative rotation.

  The engagement spring that urges the roller of the one-way clutch in the circumferential direction is composed of a coil spring, and the cage that holds the roller is provided with a protruding portion that restricts the axial displacement of the coil spring, thereby stabilizing the posture of the coil spring. Patent Document 1 below discloses that the roller is prevented from being caught between the inner ring and the outer ring in a tilted state.

Japanese Patent No. 3903157

  By the way, when a leaf spring is used as an engagement spring that urges the roller in the circumferential direction, the structure of Patent Document 1 that requires a coil spring cannot be adopted, so the first end face of the roller is attached to the axial spring. It is conceivable to prevent the tilt by pressing the second end surface of the roller against the side surface of the cage by biasing in the axial direction.

  Such an axial spring can prevent the roller from tilting, but the axial spring alone can completely prevent the roller from tilting due to factors such as variations in the frictional force between the second end surface of the roller and the side surface of the cage. There is a concern that the front end of the roller in the moving direction may bite into the side surface of the cage.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to prevent the front end portion in the moving direction of a roller biased by an axial spring from biting into the side surface of the cage.

In order to achieve the above object, according to the first aspect of the present invention, a plurality of rollers and a cage are arranged between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member, and the plurality of rollers are arranged by the cage. the circumferential and held in sandwiched direction, each said roller is urged in the circumferential direction in engagement spring, the inner member and the outer the peripheral surface of each of said rollers by a relative rotation in one direction of member and said The cage (31) is engaged between peripheral surfaces to transmit a driving force, and the cage (31) has a first cage portion having a first side surface facing a first end surface of each of the rollers, and the first of each of the rollers. and a second cage portion having a second side facing the second end surface which is opposite face of the end face, said biasing the first end surface in an axial spring provided on the first side in the axial direction the A one-way clutch for regulating the orientation of each of the rollers by to abut an end face on the second side, said second side is provided with a recess recessed in a direction away from said first side surface, the recess each said In the process of moving the roller from the daytime point to the engagement point, the front end of the moving direction of the roller is formed at a position where it can be fitted, and when viewed in the axial direction, the load of the axial spring is shifted from the recess. A one-way clutch is proposed which is characterized by acting.

  According to the invention described in claim 2, in addition to the structure of claim 1, the outer ring rotating integrally with the outer member, the inner ring rotating integrally with the inner member, and the space between the outer ring and the inner ring. A one-way clutch characterized in that the outer member is rotatably supported on the outer periphery of the inner member by a bearing having a plurality of rolling elements disposed on the inner ring, and the second side surface is formed on the inner ring. Is done.

According to the invention described in claim 3, in addition to the configuration of claim 1 or claim 2, pre-listening runner member, an output shaft by shifting a rotation of the input shaft connected to a drive source fixed to the outer periphery of the output shaft of the power transmission unit for transmitting, the power transmission unit has an input side fulcrum that rotates together with the input shaft eccentricity from the axis of said input shaft is a variable, pre-Symbol outer A one-way clutch comprising an output side fulcrum provided on a member, and a connecting rod connecting the input side fulcrum and the output side fulcrum is proposed.

The eccentric disk 18 of the embodiment corresponds to the input side fulcrum of the present invention, the pin 19c of the embodiment corresponds to the output side fulcrum of the present invention, and the angular ball bearing 34 of the embodiment corresponds to the bearing of the present invention. The inner ring 36 of the embodiment corresponds to the first cage portion and the first cage portion of the present invention, the ball 37 of the embodiment corresponds to the rolling element of the present invention, and the engine E of the embodiment is This corresponds to the drive source of the present invention.

According to the configuration of the first aspect, the one-way clutch has a plurality of rollers and a cage disposed between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member, and is held in a state where the plurality of rollers are sandwiched in the circumferential direction by the cage. and, the rollers urges circumferentially engage the spring, for transmitting a driving force to each roller was caught between the outer peripheral surface and the inner peripheral surface by the relative rotation in one direction of the inner member and the outer member .
The cage includes a first cage portion having a first side surface facing the first end surface of each roller, and a second cage portion having a second side surface facing the second end surface that is the opposite surface of the first end surface of each roller. And the posture of each roller is regulated by urging the first end surface in the axial direction with an axial spring provided on the first side surface and bringing the second end surface into contact with the second side surface. The second side surface includes a concave portion that is recessed in a direction away from the first side surface, and the concave portion is formed at a position where the front end portion of the roller in the moving direction can be fitted in the process of moving each roller from the deatum point to the engagement point. When viewed in the axial direction, the load of the axial spring acts at a position deviated from the recess, so even if each roller is tilted in the process of moving from the daytime point to the engagement point, the front end in the movement direction of each roller is a recess. , The second side surface is not caught and the second side surface is prevented from being damaged by the biting of each roller.

  According to the configuration of claim 2, the inner member is formed by a bearing including an outer ring that rotates integrally with the outer member, an inner ring that rotates integrally with the inner member, and a plurality of rolling elements disposed between the outer ring and the inner ring. Since the outer member is supported on the outer periphery of the outer member so as to be relatively rotatable and the second side surface is formed on the inner ring, the second side surface is formed using the inner ring of the bearing for supporting the outer member coaxially with respect to the inner member. This makes it possible to reduce the number of parts.

According to the third aspect, Lee runner member is fixed the rotation of the input shaft connected to a drive source to the outer periphery of the output shaft of the power transmission unit for transmitting the transmission to the output shaft, a power transmission unit has an input side fulcrum of a eccentricity from the axis of the input shaft is variable to rotate with the input shaft, an output side fulcrum provided on the a Sauter member, and the connecting rod for connecting the input side fulcrum and the output side fulcrum Therefore, when the input shaft rotates and the connecting rod reciprocates, the one-way clutch is intermittently engaged and the output shaft rotates intermittently to transmit the driving force. At this time, since the one-way clutch repeatedly engages and disengages at short time intervals, the effect of the invention of claim 1 is more effectively exhibited and the performance of the power transmission unit is improved.

The skeleton figure of the power transmission device for vehicles. FIG. 2 is a detailed view of part 2 of FIG. 1. FIG. 3 is a sectional view taken along line 3-3 in FIG. 2 (OD state). FIG. 3 is a cross-sectional view taken along line 3-3 in FIG. 2 (GN state). The action explanatory view in OD state. The operation explanatory view in the GN state. The disassembled perspective view of a one-way clutch. FIG. 8 is an enlarged view of part 8 in FIG. 2 (cross-sectional view taken along line 8-8 in FIG. 10). 9 is an enlarged view of 9 parts in FIG. FIG. 10 is a sectional view taken along line 10-10 in FIG. 8; FIG. 11 is a sectional view taken along line 11-11 in FIG. 9; FIG. 12 is a sectional view taken along line 12-12 in FIG. 9; FIG. 13 is an enlarged view of part 13 in FIG. 11.

  Hereinafter, embodiments of the present invention will be described with reference to FIGS.

  As shown in FIGS. 1 to 3, the vehicle power transmission device for transmitting the driving force of the engine E to the drive wheels W, W via the left and right axles 10, 10 is a crank type continuously variable transmission T and a differential. Gear D is provided. The continuously variable transmission T of the present embodiment is obtained by superimposing a plurality (four in the embodiment) of power transmission units U having the same structure in the axial direction, and these power transmission units U are parallel. Are provided with a common input shaft 11 and a common output shaft 12, and the rotation of the input shaft 11 is decelerated or increased and transmitted to the output shaft 12.

  Next, the structure of the continuously variable transmission T will be described with reference to FIGS.

  First, the structure of one power transmission unit U will be described as a representative. The input shaft 11 connected to the engine E and rotates passes through the hollow rotating shaft 14a of the speed change actuator 14 such as an electric motor so as to be relatively rotatable. The rotor 14b of the speed change actuator 14 is fixed to the rotating shaft 14a, and the stator 14c is fixed to the casing. The rotation shaft 14 a of the speed change actuator 14 can rotate at the same speed as the input shaft 11 and can rotate relative to the input shaft 11 at a different speed.

  A first pinion 15 is fixed to the input shaft 11 passing through the rotation shaft 14 a of the speed change actuator 14, and a crank-shaped carrier 16 is connected to the rotation shaft 14 a of the speed change actuator 14 so as to straddle the first pinion 15. The Two second pinions 17, 17 having the same diameter as the first pinion 15 are supported via pinion pins 16 a, 16 a at positions forming an equilateral triangle in cooperation with the first pinion 15, respectively. The first pinion 15 and the second pinions 17, 17 mesh with a ring gear 18 a formed eccentrically inside a disc-shaped eccentric disk 18. A ring portion 19 b provided at one end of the rod portion 19 a of the connecting rod 19 is fitted to the outer peripheral surface of the eccentric disk 18 via a ball bearing 20 so as to be relatively rotatable.

  A one-way clutch 21 provided on the outer periphery of the output shaft 12 is arranged inside the outer member 22 with a ring-shaped outer member 22 pivotally supported by a rod portion 19a of a connecting rod 19 via a pin 19c. 12, and an inner member 23 fixed to 12 and rollers 25 arranged in a wedge-shaped space formed between the outer member 22 and the inner member 23 and urged by engagement springs 24. The specific structure of the one-way clutch 21 will be described in detail later.

  As is clear from FIG. 2, the four power transmission units U... Share the crank-shaped carrier 16, but the phase of the eccentric disk 18 supported by the carrier 16 via the second pinions 17 and 17 is the same. Each power transmission unit U differs by 90 °. For example, in FIG. 2, the eccentric disk 18 of the leftmost power transmission unit U is displaced upward in the figure with respect to the input shaft 11, and the eccentric disk 18 of the third power transmission unit U from the left is relative to the input shaft 11. The eccentric discs 18 and 18 of the second and fourth power transmission units U and U from the left are located in the middle in the vertical direction.

  Next, the structure of the one-way clutch 21 will be described with reference to FIGS. 3 to 6, the one-way clutch 21 is schematically shown, and the actual structure is shown in FIGS.

  The one-way clutch 21 according to the present embodiment basically includes twelve rollers 25 between a circular inner peripheral surface 22a of an annular outer member 22 and an outer peripheral surface 23a bent in a wave shape of a cylindrical inner member 23. The connecting rod 19 is connected to the projecting portions 22b, 22b provided on the outer periphery of the outer member 22 via the pins 19c and the clips 40, 40, and the output shaft 12 is connected to the inner peripheral portion of the inner member 23. Are coupled so that they cannot rotate relative to each other.

  The one-way clutch 21 includes a cage 31 for supporting the engagement springs 24 that urge the rollers 25 in the circumferential direction. The cage 31 includes a pair of inner rings 36 and 36 of angular ball bearings 34 and 34, which will be described later, and twelve spring support rods 33 that are arranged at equal intervals in the circumferential direction and connect the pair of inner rings 36 and 36 to each other. The pair of inner rings 36 are arranged on both sides in the axial direction of the twelve rollers 25. The twelve spring support rods 33 are arranged between the twelve rollers 25. When the inner peripheral portions of the inner rings 36 are pressed into the outer peripheral surface 23 a of the inner member 23, the cage 31 is coupled to the inner member 23 so as not to be relatively rotatable.

  The engagement spring 24 is formed by bending a single elastic plate with an S-shaped cross section, one end of which is fixed to the spring support rod 33 of the cage 31 by welding or the like, and the other end is in contact with the roller 25 to be elastic. A deformable biasing portion 24a is formed.

  One angular ball bearing 34 is disposed between the two adjacent one-way clutches 21 and 21, and the outer ball members 22 and 22 and the inner member 23 can be rotated relative to each other while maintaining the concentric state. Connected to. The angular ball bearing 34 has a plurality of balls 37 arranged between two outer rings 35, 35 and one inner ring 36. The two outer rings 35, 35 are formed by two axially adjacent outer members 22, 22. The inner ring 36 is formed as a separate member and is press-fitted into the outer peripheral surface 23 a of the inner member 23. That is, one angular ball bearing 34 supports the two outer rings 35, 35 with a common ball 37, so that the two outer members 22, 22 of the two adjacent one-way clutches 21, 21 are supported in a relatively rotatable manner. Is done.

  The two angular ball bearings 34, 34 (see FIG. 8) located at both ends in the axial direction of the four one-way clutches 21 arranged side by side have only one inner ring 36 and one outer ring 35. Abut.

  Accordingly, a pair of angular ball bearings 34 and 34 are disposed on both axial sides of each one-way clutch 21, and the first side surface 36 a formed on the inner ring 36 of one angular ball bearing 34 and the other angular ball bearing 34. The second side surfaces 36b formed on the inner ring 36 face each other. A flat first end face 25a and a second end face 25b are formed at both axial ends of the roller 25, and an axial spring comprising an annular leaf spring between the first side face 36a of the inner ring 36 and the first end face 25a of the roller 25. 38 is arranged. The twelve protrusions 38a projecting from the inner periphery of the axial spring 38 elastically abut on the first end surfaces 25a of the twelve rollers 25, thereby the second end surfaces 25b of the twelve rollers 25. Is pressed against the second side surface 36b of the other inner ring 36, whereby the posture of the rollers 25 is stabilized.

  On the second side surface 36b of the other angular ball bearing 34, twelve concave portions 36c... That are recessed in the direction away from the first side surface 36a of the one angular ball bearing 34 are formed.

  As shown in FIG. 12, the circumferential range of the concave portion 36c of the second side surface 36b is from the position a of the moving direction front end portion 25c of the roller 25 at the daytime point to the moving direction front end portion of the roller 25 at the engagement point. It extends beyond the position b of 25c, and the radial range is set so as to cover the vicinity of the moving direction front end portion 25c of the roller 25 at the daytime point. When viewed in the axial direction of the roller 25, the protrusion 38 a of the axial spring 38 that presses the first end surface 25 a of the roller 25 does not overlap the recess 36 c facing the second end surface 25 b of the roller 25, and the damping point side ( It is shifted to the left in the figure.

  An annular ring spring 39 is disposed in an annular groove 22c formed in the inner peripheral surface 22a of the outer member 22, and this ring spring 39 abuts on the peripheral surface of the roller 25, so as to contact the outer peripheral surface 23a of the inner member 23. Energize towards.

  Next, the operation of the embodiment of the present invention having the above configuration will be described.

  First, the operation of one power transmission unit U of the continuously variable transmission T will be described. When the rotation shaft 14 a of the speed change actuator 14 is rotated relative to the input shaft 11, the carrier 16 rotates about the axis L <b> 1 of the input shaft 11. At this time, the center O of the carrier 16, that is, the center of the equilateral triangle formed by the first pinion 15 and the two second pinions 17, 17 rotates around the axis L 1 of the input shaft 11.

  3 and 5 show a state in which the center O of the carrier 16 is on the opposite side of the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). The amount of eccentricity is maximized, and the gear ratio of the continuously variable transmission T is in a minimum OD (overdrive) state. 4 and 6 show a state in which the center O of the carrier 16 is on the same side as the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). At this time, the eccentric disk 18 with respect to the input shaft 11 The amount of eccentricity becomes zero, and the transmission ratio of the continuously variable transmission T becomes an infinite GN (geared neutral) state.

  In the OD state shown in FIG. 5, when the input shaft 11 is rotated by the engine E and the rotation shaft 14 a of the speed change actuator 14 is rotated at the same speed as the input shaft 11, the input shaft 11, the rotation shaft 14 a, the carrier 16, With the one pinion 15, the two second pinions 17 and 17, and the eccentric disk 18 being integrated, the pinion 15 rotates eccentrically around the input shaft 11 (see arrow A). While rotating from FIG. 5A through FIG. 5B to the state of FIG. 5C, the ring portion 19b is supported on the outer periphery of the eccentric disk 18 via the ball bearing 20 so as to be relatively rotatable. The connecting rod 19 rotates the outer member 22 pivotally supported by a pin 19c at the tip of the rod portion 19a in the counterclockwise direction (see arrow B). 5A and 5C show both ends of rotation of the outer member 22 in the arrow B direction.

  When the outer member 22 rotates in the arrow B direction in this way, the rollers 25... Bite into the wedge-shaped space between the outer member 22 and the inner member 23 of the one-way clutch 21, and the rotation of the outer member 22 passes through the inner member 23. Therefore, the output shaft 12 rotates counterclockwise (see arrow C).

  When the input shaft 11 and the first pinion 15 further rotate, the eccentric disk 18 in which the ring gear 18a is engaged with the first pinion 15 and the second pinion 17, 17 rotates eccentrically in the counterclockwise direction (see arrow A). While rotating from the state shown in FIG. 5C to the state shown in FIG. 5A, the ring portion 19b is supported on the outer periphery of the eccentric disk 18 via the ball bearing 20 so as to be relatively rotatable. The connecting rod 19 rotates the outer member 22 pivotally supported by a pin 19c at the tip of the rod portion 19a in the clockwise direction (see arrow B ′). FIG. 5C and FIG. 5A show both ends of the rotation of the outer member 22 in the arrow B ′ direction.

  When the outer member 22 rotates in the direction of the arrow B ′ in this way, the rollers 25 are pushed out from the wedge-shaped space between the outer member 22 and the inner member 23 while compressing the engagement springs 24, thereby the outer member. 22 slips with respect to the inner member 23 and the output shaft 12 does not rotate.

  As described above, when the outer member 22 reciprocates, the output shaft 12 rotates counterclockwise (see arrow C) only when the rotation direction of the outer member 22 is counterclockwise (see arrow B). The shaft 12 rotates intermittently.

  FIG. 6 shows the operation when the continuously variable transmission T is operated in the GN state. At this time, since the position of the input shaft 11 coincides with the center of the eccentric disk 18, the eccentric amount of the eccentric disk 18 with respect to the input shaft 11 becomes zero. In this state, when the input shaft 11 is rotated by the engine E and the rotating shaft 14a of the speed change actuator 14 is rotated at the same speed as the input shaft 11, the input shaft 11, the rotating shaft 14a, the carrier 16, the first pinion 15, 2 In a state where the second pinions 17 and 17 and the eccentric disk 18 are integrated, the input pin 11 is rotated eccentrically in the counterclockwise direction (see arrow A). However, since the eccentric amount of the eccentric disk 18 is zero, the stroke of the reciprocating motion of the connecting rod 19 is also zero, and the output shaft 12 does not rotate.

  Accordingly, if the speed change actuator 14 is driven and the position of the carrier 16 is set between the OD state of FIG. 3 and the GN state of FIG. 4, operation at an arbitrary speed ratio between the infinite speed ratio and the minimum speed ratio is performed. Is possible.

  In the continuously variable transmission T, the phases of the eccentric disks 18 of the four power transmission units U arranged in parallel are shifted by 90 ° from each other, so that the four power transmission units U are alternately driven. By transmitting, that is, any one of the four one-way clutches 21 is always in an engaged state, the output shaft 12 can be continuously rotated.

  Next, the tilt preventing action of the roller 25 of the one-way clutch 21 will be described.

  The right column in FIG. 11 is a position (engage point) where the roller 25 is engaged with a wedge-shaped space formed between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23 to transmit the driving force. The middle column in FIG. 11 shows a state in which the roller 25 is at a standby position (daytime point) immediately before the roller 25 bites into the wedge-shaped space, and the left column in FIG. It shows a state in which it is at a position (damping point) where the engagement point is pushed back to the maximum in the reverse direction beyond the daytime point at the moment of disengagement. Further, the upper part of FIG. 11 shows a normal state where the roller 25 is not inclined, and the lower part of FIG. 11 shows an abnormal state where the roller 25 is inclined.

  As shown in the upper part of FIG. 11, the roller 25 of the one-way clutch 21 has a first protrusion 36 a of an axial spring 38 disposed between the roller 35 of the one-way clutch 21 and the first side surface 36 a of the inner ring 36 of one angular ball bearing 34. Since the first end face 25a is pressed in the axial direction, the second end face 25b is pressed against the second side face 36b of the inner ring 36 of the other angular ball bearing 34 to prevent the tilting.

  However, as shown in the lower part of FIG. 11, when the roller 25 moves from the daytime point toward the engagement point when the one-way clutch 21 is engaged, the second end surface 25b is caught by the second side surface 36b and the roller 25 is inclined. In some cases, the inner member 22 may be caught between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23. Even in such a case, since the concave portion 36c is formed on the second side surface 36b of the inner ring 36, the front end portion 25c in the moving direction of the second end surface 25b of the inclined roller 25 is fitted into the concave portion 36c. Thus, the second end surface 25b of the inner ring 36 is unlikely to bite into the second side surface 36b of the inner ring 36, and damage to the second side surface 36b of the inner ring 36 can be prevented.

  In order to ensure the rigidity of the inner ring 36 of the angular ball bearing 34, it is desirable to reduce the depth of the recess 36c within a range in which the front end 25c in the moving direction of the roller 25 does not contact the bottom of the recess 36c. As shown in FIG. 13 (A), the depth D of the recess 36c is such that D> S when the allowable maximum inclination angle of the roller 25 is θ and the stroke of the inclined roller 25 projecting into the recess 36c is S. × sin θ is set.

  In the embodiment described above, the recess 36c extends from the position of the front end 25c in the moving direction of the roller 25 at the daytime point (see the chain line) toward the engagement point. FIG. 13B shows a second embodiment. As shown in the form, the starting point of the recess 36c may be shifted to the damping point side by a distance ΔS. As a result, the stroke S ′ at which the roller 25 inclined at the engagement point protrudes into the recess 36c is increased by the distance ΔS, and the minimum depth D ′ of the recess 36c is increased accordingly.

  Further, when viewed in the axial direction of the roller 25, the protrusion 38a of the axial spring 38 that presses the first end surface 25a of the roller 25 does not overlap the recess 36c facing the second end surface 25b of the roller 25, and is on the damping point side. Due to the deviation (see FIG. 12), it is possible to avoid a situation in which the inclination of the roller 25 is increased by the elastic force of the protrusion 38a of the axial spring 38 and the moving direction front end 25c falls into the recess 36c. it can.

  Further, since the existing angular ball bearings 34 are used as a part of the cage 31, the structure of the cage 31 can be simplified and the number of parts can be reduced.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, the use of the one-way clutch of the present invention is not limited to the continuously variable transmission T of the embodiment. However, since the one-way clutch 21 of the continuously variable transmission T according to the embodiment repeats engagement and disengagement at short time intervals, the effect is more effectively exhibited by applying the present invention to the one-way clutch 21. .

  The axial spring of the present invention is not limited to the leaf spring of the embodiment, and may be any type of spring.

  The bearing of the present invention is not limited to the angular ball bearing 34 of the embodiment, and may be any type of bearing.

  In the embodiment, a part of the outer member 22 of the one-way clutch 21 is used as the outer ring 35 of the angular ball bearing 34. However, the outer ring 35 may be configured as a separate member and fixed to the outer member 22.

  In the embodiment, the inner ring 36 of the angular ball bearing 34 is formed as a separate member from the inner member 23 of the one-way clutch 21, but a part of the inner member 23 may be used as the inner ring 36.

11 Input shaft 12 Output shaft 18 Eccentric disc (input side fulcrum)
19 Connecting rod 19c Pin (Output side fulcrum )
22 outer member 22a inner peripheral surface 23 inner member 23a outer peripheral surface 24 engagement spring 25 roller 25a first end surface 25b second end surface 25c moving direction front end 31 cage 34 angular ball bearing (bearing)
35 Outer ring 36 Inner ring (first and second cage parts)
36a First side surface 36b Second side surface 36c Concave portion 37 Ball (rolling element)
38 Axial Spring E Engine (drive source)
U Power transmission unit

Claims (3)

A plurality of rollers (25) and a cage (31) are disposed between the outer peripheral surface (23a) of the inner member (23) and the inner peripheral surface (22a) of the outer member (22), and the plurality of rollers (25) and the cage (31) are arranged by the cage (31). The rollers (25) are held in a state of being sandwiched in the circumferential direction, and each of the rollers (25) is urged in the circumferential direction by an engagement spring (24), and one of the inner member (23) and the outer member (22) is urged. Each of the rollers (25) is engaged between the outer peripheral surface (23a) and the inner peripheral surface (22a) by relative rotation in a direction to transmit a driving force;
The cage (31) includes a first cage portion (36) having a first side surface (36a) facing the first end surface (25a) of each roller (25), and the first cage portion (36). An axial spring provided on the first side surface (36a), the second cage portion (36) having a second side surface (36b) facing the second end surface (25b) opposite to the end surface (25a). 38), the posture of each roller (25) is regulated by urging the first end surface (25a) in the axial direction and bringing the second end surface (25b) into contact with the second side surface (36b). A one-way clutch,
The second side surface (36b) includes a recess (36c) that is recessed away from the first side surface (36a), and the recess (36c) moves each roller (25) from a daytime point to an engagement point. In the process, the front end (25c) in the moving direction of the roller (25) is formed at a position where it can be fitted, and the load of the axial spring (38) is shifted from the recess (36c) when viewed in the axial direction. One-way clutch characterized by acting on.   The outer ring (35) that rotates integrally with the outer member (22), the inner ring (36) that rotates integrally with the inner member (23), and the outer ring (35) and the inner ring (36). The outer member (22) is supported on the outer periphery of the inner member (23) by a bearing (34) having a plurality of rolling elements (37) so as to be relatively rotatable, and the second side surface (36b) is supported by the inner ring ( 36. The one-way clutch according to claim 1, which is formed in 36). Before hearing runner member (23), said output shaft (12 of the driving source a power transmission unit for transmitting to the connected input shaft (E) and shifting the rotation of (11) with an output shaft (12) (U) )
The power transmission unit (U), the a a eccentricity from the axis of the input shaft (11) is variable input side fulcrum that rotates together with the input shaft (11) (18), before Symbol outer member (22) 3. An output side fulcrum (19c) provided on the input side fulcrum (19c) and a connecting rod (19) connecting the input side fulcrum (18) and the output side fulcrum (19c). One-way clutch described in.

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