JP6130197B2 - One-way clutch and continuously variable transmission - Google Patents

Description

  The present invention relates to a crank type continuously variable transmission and a one-way clutch used therein.

 For example, Patent Document 1 discloses a crank type continuously variable transmission that converts the rotation of an input shaft connected to an engine into a reciprocating motion of a connecting rod, and converts the reciprocating motion of the connecting rod into a rotational motion of an output shaft by a one-way clutch. Is described.

JP 2012-1048 A

  One-way clutches used in crank type continuously variable transmissions must be responsive to return the rollers from a damping state to a standby state for the next engagement at high frequencies. Absorbing and generating friction on the roller end face by the axial spring, the frictional force attenuates the energy of the roller from the engaged state to the non-engaged state to cope with high frequency response.

  In order to realize the high frequency response as shown in the figure, it is necessary to dampen the roller after the engagement and return to the standby state by the next engagement state, in order to stabilize the high frequency response. Needs to absorb and attenuate energy more quickly.

  The present invention has been made in view of the above problems, and an object of the present invention is to effectively attenuate the energy of the roller during damping (when not engaged) and stabilize high-frequency response and a continuously variable transmission. Is to realize the machine.

In order to solve the above-mentioned problems and achieve the object, a first embodiment according to the present invention includes an outer member (22) and an inner member (23) arranged coaxially on the inner periphery of the outer member (22). A plurality of rollers (25) disposed between an inner peripheral surface (22a) of the outer member (22) and an outer peripheral surface (23a) of the inner member (23), and the plurality of rollers (25). A plurality of elastic members (24) that contact each other and urge in the circumferential direction, and the roller (25) is moved by relative rotation of the outer member (22) and the inner member (23) in a predetermined direction. A one-way clutch (21) for transmitting driving force by engaging between an inner peripheral surface (22a) of the outer member (22) and an outer peripheral surface (23a) of the inner member (23), wherein the inner member Outside (23) The surface (23a) is released when the roller (25) is engaged between the inner peripheral surface (22a) of the outer member (22) and the outer peripheral surface (23a) of the inner member (23). the roller comprises regulating portion of the wedge-shaped to collide with the outer peripheral surface for regulating the movement of the roller (23b) of said inner member (23), the regulating portion of the wedge (23b), said inner member ( than other portions of the outer peripheral surface of 23) (23a) rather small, coefficient of restitution, is composed of a plurality of members having a thickness (23c) relative to the outer peripheral surface of the inner member (23) (23a), said plurality The member (23c) at least partially overlaps the outer peripheral surface of the roller (25) in the axial direction of the roller (25), and the plurality of members (23c) are arranged on the outer periphery of the roller (25). Abuts the surface Is provided at the same distance (R) from the center line (25b) perpendicular to the axial direction of the roller through the axial center (25a) of the roller in the axial direction of the roller. Yes .

Further, according to a second aspect of the present invention, the plurality of members (23c) of the restricting portion are means for blocking outflow of the lubricating oil, and are coated with a low repulsion material having a predetermined thickness Consists of.

According to a third aspect of the present invention, there is provided a continuously variable transmission that includes the one-way clutch according to the first or second aspect and that changes the rotation of the input shaft (11) and transmits the rotation to the output shaft (12). An input side fulcrum (18) whose eccentric amount from the axis (L1) of the input shaft (11) is variable and rotates together with the input shaft (11), and the outer member of the one-way clutch (21) The output side fulcrum (19c) provided in (22) was connected by a connecting rod (19), and the inner member (23) of the one-way clutch (21) was connected to the output shaft (12).

  ADVANTAGE OF THE INVENTION According to this invention, the energy of the roller at the time of damping (at the time of non-engagement) can be attenuate | damped effectively, and the one-way clutch and continuously variable transmission which can stabilize a high frequency responsiveness are realizable.

Specifically, according to the first embodiment of the present invention, the energy absorption effect and attenuation when the roller (25) collides with the restricting portion (23b) by reducing the coefficient of restitution of the restricting portion (23b). The effect can be further enhanced.
Further, when the roller (25) collides with the restricting portion (23b), the roller (25) can be held in a correct posture, and can quickly return to the engagement standby state while reducing the occurrence of one-side contact or local stress. Can do.

Moreover, according to the 2nd form which concerns on this invention, a roller (25) uses a some member (23c) of a control part (23b) as a means to interrupt | block the outflow of lubricating oil, A control part (23b) The pressure generated by the squeeze effect when colliding with the roller can be increased, and the energy of the roller (25) can be absorbed more effectively. Further, since the viscosity of the lubricating oil is increased particularly at low temperatures, the energy absorption effect and damping effect are further enhanced.

Further, according to the third aspect of the present invention, the one-way clutch of the present invention is applied to a crank type continuously variable transmission, thereby realizing the responsiveness of returning the roller from the damping state to the engagement standby state at a high frequency. can do.

The block diagram of the powertrain of the motor vehicle by which the continuously variable transmission of this embodiment is mounted. The figure which shows the structure of the continuously variable transmission of this embodiment. The figure which shows operation | movement of the TOP state of the continuously variable transmission of this embodiment. The figure which shows the operation | movement of the LOW state of the continuously variable transmission of this embodiment. The disassembled perspective view of the one-way clutch mounted in the continuously variable transmission of this embodiment. The figure which shows the state change of the one-way clutch of this embodiment. The figure which shows the state change of 1 cycle until a roller is released from an engagement state, and becomes an engagement state again in the one-way clutch of this embodiment. The schematic diagram which shows the structure of the outer peripheral surface (stopper part) of the inner member in the one-way clutch of this embodiment. The schematic diagram explaining the structure and function of the outer peripheral surface (stopper part) of the inner member in the one-way clutch of this embodiment. The schematic diagram explaining the function of the outer peripheral surface (stopper part) of the inner member in the one-way clutch of this embodiment.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. The embodiment described below is an example as means for realizing the present invention, and the present invention can be applied to a modified or modified embodiment described below without departing from the spirit of the present invention. In the following, an example in which the one-way clutch and the crank type continuously variable transmission according to the present invention is applied to a power train of an automobile will be described, but it is needless to say that it can be applied to other uses other than the automobile.

  <Powertrain Configuration> First, the configuration of the powertrain of an automobile on which the continuously variable transmission of this embodiment is mounted will be described with reference to FIG.

  As shown in FIG. 1, the driving force of the engine 1 is input from an output shaft 2 to a crank type continuously variable transmission (hereinafter abbreviated as a continuously variable transmission) 3, and the continuously variable transmission 3 passes through a differential gear 4. Are transmitted to the left and right axles 5 to drive the drive wheels 6.

  <Structure of continuously variable transmission> Next, the structure of the continuously variable transmission according to this embodiment will be described with reference to FIGS.

  As shown in FIG. 2, the continuously variable transmission 3 of the present embodiment has a plurality of (four in the embodiment) power transmission mechanisms U having the same structure as an input shaft 11 coaxial with the output shaft 2 of the engine 1. On the other hand, they are arranged in the axial direction. Each power transmission mechanism U includes a common input shaft 11 and a common output shaft 12 arranged in parallel, and the rotation of the input shaft 11 is decelerated or increased and transmitted to the output shaft 12.

  Hereinafter, one structure of the plurality of power transmission mechanisms U will be described with reference to FIGS. 3 and 4.

  An input shaft 11 that is connected to the engine 1 and rotates passes through a hollow rotary shaft 14a of a 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 having the same diameter as the first pinion 15 are supported via pinion pins 16a at positions forming an equilateral triangle in cooperation with the first pinion 15, and these first pinions 15 The ring gear 18 a formed eccentrically inside the disc-shaped eccentric disk 18 meshes with the second pinion 17. 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.

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

  The power transmission mechanism U shares the crank-shaped carrier 16, but the phase of the eccentric disk 18 supported by the carrier 16 via the second pinion 17 differs by 90 ° in each power transmission mechanism U. For example, in FIG. 2, the eccentric disk 18 of the leftmost power transmission mechanism U is displaced upward in the figure with respect to the input shaft 11, and the eccentric disk 18 of the third power transmission mechanism U from the left is relative to the input shaft 11. The eccentric disk 18 of the second and fourth power transmission mechanisms U from the left is located in the middle in the vertical direction.

  <Structure of the one-way clutch> Next, the structure of the one-way clutch will be described with reference to FIG.

  The one-way clutch 21 includes twelve rollers 25 disposed 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 protruding connecting portion 22b provided on the outer periphery of the member 22 via the connecting pin 19c and the clip 40, and the output shaft 12 is coupled to the inner peripheral portion of the inner member 23 so as not to be relatively rotatable. .

  The one-way clutch 21 includes a cage 31 for supporting an engagement spring 24 that biases the roller 25. The cage 31 includes a pair of annular members 32 made of an annular plate member and twelve spring support rods that are arranged at equal intervals in the circumferential direction and connect the pair of annular members 32 to each other. 32 is disposed on both axial sides of the twelve rollers 25, and twelve spring support rods 33 are disposed between the twelve rollers 25. The inner peripheral portion of the annular member 32 is formed in a corrugated shape, and the cage 31 is coupled to the inner member 23 so as not to be relatively rotatable by engaging with the corrugated outer peripheral surface 23 a of the inner member 23. The engagement spring 24 is formed by bending a single elastic plate member into an S-shaped cross section, and one end thereof is fixed to the spring support rod 33 of the cage 31 by welding or the like.

  Between the outer member 22 and the inner member 23, a pair of ball bearings 34 located on both sides in the axial direction of the roller 25 are disposed, and the outer member 22 and the inner member 23 maintain a concentric state by the ball bearings 34. It is connected so that relative rotation is possible. The ball bearing 34 has a plurality of balls 37 disposed between an outer ring 35 and an inner ring 36, the outer ring 35 is formed integrally with the axial end of the outer member 22, and the inner ring 36 is configured as a separate member to form an inner member. 23 is fixed to the outer periphery. There are two types of ball bearings 34, one is a single row, and the other two ball bearings 34 located at both axial ends of the four one-way clutch 21 are a single row, and the other three balls Since the bearings 34 are shared by the two adjacent one-way clutches 21, they become double rows.

  An axial spring 38 is disposed between one ball bearing 34 and one annular member 32 of the cage 31, and a plurality of pressing portions 38 a protruding from the inner periphery of the axial spring 38 are provided on the inner periphery of the annular member 32. Passing between the recesses 32a of the roller 25, abuts against the end face of the roller 25 and is pressed by its elasticity. An annular ring spring 39 is disposed in an annular groove 22 c formed on the inner peripheral surface of the outer member 22. The ring spring 39 abuts on the peripheral surface of the roller 25 and faces the outer peripheral surface 23 a of the inner member 23. Energize.

  <Description of Operation> Next, the power transmission action of the continuously variable transmission according to this embodiment will be described with reference to FIGS.

  First, the operation of one power transmission mechanism U of the continuously variable transmission 3 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 an equilateral triangle formed by the first pinion 15 and the two second pinions 17 rotates around the axis L 1 of the input shaft 11.

  FIG. 3 shows a state in which the center O of the carrier 16 is opposite to the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). At this time, the eccentric amount of the eccentric disk 18 with respect to the input shaft 11 is At the maximum, the ratio of the continuously variable transmission 3 is in the TOP state. FIG. 4 shows a state where 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 amount of the eccentric disk 18 with respect to the input shaft 11 is As a result, the ratio of the continuously variable transmission 3 becomes LOW.

  In the TOP state shown in FIG. 3, when the input shaft 11 is rotated by the engine 1 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, In a state where the one pinion 15, the two second pinions 17 and the eccentric disk 18 are integrated, the pinion 15 rotates eccentrically around the input shaft 11 (see arrow A). While rotating from the state shown in FIG. 3 (A) to the state shown in FIG. 3 (C), 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 the connecting pin 19c on the small-diameter annular rod portion 19a in the counterclockwise direction (see arrow B1). 3A and 3C show both ends of the rotation of the outer member 22 in the arrow B1 direction.

  When the outer member 22 rotates in the direction of the arrow B1 in this way, the roller 25 is caught in 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 is performed via the inner member 23. Since it is transmitted to the output shaft 12, 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 rotates eccentrically in the counterclockwise direction (see arrow A). While rotating from the state shown in FIG. 3C through the state shown in FIG. 3D to the state shown in FIG. 3A, 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 the connecting pin 19c on the rod portion 19a in the clockwise direction (see arrow B2). 3C and 3A show both ends of rotation of the outer member 22 in the direction of arrow B2.

  When the outer member 22 rotates in the direction of the arrow B2 in this way, the roller 25 is pushed out from the wedge-shaped space between the outer member 22 and the inner member 23 while compressing the engagement spring 24, so that the outer member 22 becomes the inner member. The output shaft 12 does not rotate by slipping with respect to the member 23.

  As described above, when the outer member 22 reciprocates, the output shaft 12 rotates counterclockwise (see arrow C) only when the outer member 22 rotates counterclockwise (see arrow B1). The shaft 12 rotates intermittently.

  FIG. 4 shows the operation when the continuously variable transmission 3 is operated in the LOW state. At this time, since the position of the input shaft 11 coincides with the center of the eccentric disk 18, the amount of eccentricity of the eccentric disk 18 with respect to the input shaft 11 becomes zero (the state where this amount of eccentricity becomes zero is a geared neutral (GN)). Called state). When the input shaft 11 is rotated by the engine 1 in this GN state 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, In a state where the two second pinions 17 and the eccentric disk 18 are integrated, the input pin 11 rotates 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.

  Therefore, if the speed change actuator 14 is driven and the position of the carrier 16 is set between the TOP state of FIG. 3 and the LOW state of FIG. 4, operation at an arbitrary ratio between the zero ratio and the predetermined ratio becomes possible.

  In the continuously variable transmission 3, the phases of the eccentric disks 18 of the four power transmission mechanisms U juxtaposed are shifted by 90 ° from each other, so that the four power transmission mechanisms U alternately transmit the driving force. In other words, any one of the four one-way clutches 21 is always in an engaged state, so that the output shaft 12 can be continuously rotated.

  <Operation of One-Way Clutch> Next, referring to FIG. 6, the state change of the one-way clutch 21 will be described.

  FIG. 6A shows a DP (Datum Point) state of the one-way clutch 21, that is, a state immediately before the one-way clutch 21 is engaged. In the DP state, the urging portion 24 a of the engagement spring 24 abuts on the outer peripheral surface of the roller 25, and the roller 25 is urged in a direction to be engaged between the inner peripheral surface 22 a of the outer member 22 and the outer peripheral surface 23 a of the inner member 23. At this time, the one-way clutch 21 is not yet engaged, and the roller 25 is in contact with the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23 without being engaged.

  When the outer member 22 rotates relative to the inner member 23 in the direction of arrow A from this DP state, the roller 25 is subjected to the arrow A by the biasing force received from the engagement spring 24 and the frictional force received from the outer member 22 and the inner member 23. The one-way clutch 21 is engaged as shown in FIG. 6B by moving in the direction and engaging in a wedge-shaped space between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23.

  When the outer member 22 rotates relative to the inner member 23 in the arrow B direction from the engaged state of the one-way clutch 21 shown in FIG. 6B, the roller 25 is caused by the frictional force received from the outer member 22 and the inner member 23. By moving in the direction of the arrow B against the biasing force received from the engagement spring 24 and detaching from the wedge-shaped space between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23, FIG. As shown, the one-way clutch 21 is disengaged. This state is called a damping state, and the roller 25 rotates in the direction of arrow B while compressing the urging portion 24a of the engagement spring 24. The roller 25 moves from the inner peripheral surface 22a of the outer member 22 or the outer peripheral surface 23a of the inner member 23. Get away. Thereafter, the roller 25 is urged by the engagement spring 24 and quickly returns to the DP state shown in FIG.

  When the roller 25 is pushed out of the wedge-shaped space between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23 in the process of shifting from the engaged state to the damping state, the roller 25 is attached in the axial direction by the axial spring 38. Since the end face of the urged roller 25 is pressed against the annular member 32 of the cage 31, the behavior of the roller 25 can be stabilized by the frictional force. Further, when the roller 25 is pushed out from the wedge-shaped space between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23, the roller 25 is applied to the inner peripheral surface of the outer member 22 positioned radially outward by centrifugal force. Although it is pressed, it can be suppressed by the elastic force of the ring spring 39 inward in the radial direction.

  <Energy Absorption / Attenuation Structure of Roller> Next, a structure for absorbing and attenuating the energy of the roller in the damping state in the continuously variable transmission of this embodiment will be described.

  FIG. 7 shows a change in state of one cycle until the roller is released from the engaged state and re-engaged in the one-way clutch of the present embodiment.

  The energy generated when the roller 25 is released from the engaged state is absorbed by the engagement spring 24 and is attenuated by the frictional force generated by pressing the roller end surface by the axial spring 38.

  However, the one-way clutch used in the crank type continuously variable transmission as in this embodiment, as shown in FIG. 7, has a high frequency (about 100 Hz) that quickly returns the roller 25 from the damping state to the engagement standby state (DP state). Responsiveness is required. That is, in order to achieve high-frequency response with the one-way clutch of the present embodiment, the damping state is quickly terminated after being released from the engaged state, and the standby state (DP state) is prepared in preparation for the next engagement. In order to stabilize this high frequency response, it is necessary to absorb and attenuate the energy of the roller 25 more quickly.

  Therefore, in this embodiment, as shown in FIG. 8, a wedge shape formed to cause the roller 25 to collide with the outer peripheral surface 23 a of the inner member 23 in order to restrict the movement of the roller 25 released from the engaged state. The repulsion coefficient e of the stopper portion 23b is configured to be smaller than other portions. The restitution coefficient e is defined as V = −eV0, where V0 is a speed when the roller 25 collides with the stopper portion 23b, and −V is a speed when the roller 25 repels after the collision.

  Specifically, as shown in FIG. 9A, a portion of the stopper portion 23b where the roller 25 collides is coated with a low-rebound material 23c having a predetermined thickness to reduce the restitution coefficient. Thus, by reducing the coefficient of restitution of the stopper portion 23b with the coating material 23c, the energy absorption effect and the damping effect when the roller 25 collides with the stopper portion 23b can be further enhanced.

  Further, as shown in FIG. 10A, when the roller 25 collides with the stopper portion 23b and the lubricating oil is discharged, the pressure P1 is generated due to the outflow resistance (squeeze effect) of the lubricating oil. The higher the pressure generated by the squeeze effect, the more energy of the roller 25 can be absorbed. As shown in FIG. 10B, the pressure P2 (> P1) due to the squeeze effect is further increased by providing the stopper portion 23b with means for blocking outflow of the lubricating oil. In addition, since the viscosity of the lubricating oil increases at low temperatures, the energy absorption effect and damping effect are further enhanced. The outflow resistance can be expressed by a well-known three-dimensional Reynolds equation.

  Therefore, in the present embodiment, as shown in FIG. 9B, by using the coating material 23c as a means for blocking outflow of the lubricating oil, the roller 25 is generated due to a squeeze effect when it collides with the stopper portion 23b. The pressure P is increased and the energy of the roller 25 is absorbed. Specifically, the coating material 23c is provided at two positions corresponding to both ends in the axial direction of the roller 25 in the stopper portion 23b, so that the outflow resistance of the lubricating oil when the roller 25 collides with the stopper portion 23b. The pressure due to the squeeze effect can be increased.

  Further, the coating material 23c is provided at the same distance R from the axial center 25b of the roller 25, and the gap portion of the coating material 23c is provided so as to at least partially overlap the outer peripheral surface of the roller 25. Thus, when the roller 25 collides with the stopper portion 23b, the roller 25 can maintain the correct posture without being inclined, and can quickly return to the engagement standby state (DP state) while reducing the occurrence of one-side contact and local stress. Can do.

  As a coating material, for example, NBR (nitrile rubber) or ACM (acrylic rubber) having high oil resistance can be used.

  Moreover, as for the bonding method of the coating material 23c, there are (1) a method of directly bonding by metal plating and (2) a method of applying and bonding an adhesive. A method of applying and bonding the adhesive is suitable.

  The coating material 23c may be provided not only at two locations on both ends of the roller 25 in the axial direction but also at three locations including the axial center position.

  As described above, by applying the one-way clutch of the present embodiment to the crank type continuously variable transmission, it is possible to realize the responsiveness of returning the roller from the damping state to the engagement standby state (DP state) at a high frequency. .

  Note that the one-way clutch 21 of the present embodiment can be applied to any application other than the continuously variable transmission 3.

  Further, the continuously variable transmission 3 of the present embodiment includes four sets of power transmission mechanisms U, but the number may be more or less.

  In the present embodiment, the inner member 23 of the one-way clutch 21 is configured as a separate member from the output shaft 12, but the inner member 23 may be used as it is as the output shaft 12.

  In the present embodiment, the cage 31 is fixed to the inner member 23, but may be fixed to the outer member 22.

  Further, the number of the rollers 25 and the engagement springs 24 of the one-way clutch 21 is not limited to the above-described embodiment.

11 Input shaft 12 Output shaft 18 Eccentric disc (input side fulcrum)
19 Connecting rod 19c Connecting pin (Output side fulcrum)
21 One-way clutch 22 Outer member 22a Inner peripheral surface 23 Inner member 23a Outer peripheral surface 23b Stopper portion 23c Coating material 25 Roller

Claims (3)

An outer member (22), an inner member (23) coaxially disposed on the inner periphery of the outer member (22), an inner peripheral surface (22a) of the outer member (22), and the inner member (23). A plurality of rollers (25) disposed between the outer peripheral surfaces (23a), and a plurality of elastic members (24) that respectively abut against the plurality of rollers (25) and bias in the circumferential direction, By the relative rotation of the outer member (22) and the inner member (23) in a predetermined direction, the roller (25) is moved to the inner peripheral surface (22a) of the outer member (22) and the outer peripheral surface of the inner member (23). A one-way clutch (21) engaged between (23a) and transmitting a driving force,
The outer peripheral surface (23a) of the inner member (23) is related to the roller (25) between the inner peripheral surface (22a) of the outer member (22) and the outer peripheral surface (23a) of the inner member (23). A wedge-shaped restricting portion (23b) for restricting the movement of the roller by colliding the roller with the outer peripheral surface of the inner member (23) when released from the combined state;
The restricting portion of the wedge (23b), the restitution coefficient than other portions of the outer circumferential surface of the inner member (23) (23a) are rather small, the thickness to the outer peripheral surface (23a) of said inner member (23) A plurality of members (23c) having
The plurality of members (23c) at least partially overlap the outer peripheral surface of the roller (25) in the axial direction of the roller (25),
The portion where the plurality of members (23c) abut on the outer peripheral surface of the roller (25) passes through the center (25a) in the axial direction of the roller in the axial direction of the roller and is orthogonal to the axial direction of the roller. The one-way clutch is provided at the same distance (R) from the center line (25b) . The plurality of members (23c) of the restricting portion are means for blocking outflow of lubricating oil, and are made of a coating material coated with a low repulsion material having a predetermined thickness. One-way clutch. A continuously variable transmission that includes the one-way clutch (21) according to claim 1 or 2 and that shifts the rotation of the input shaft (11) and transmits it to the output shaft (12),
An input side fulcrum (18) that is variable in eccentricity from the axis (L1) of the input shaft (11) and rotates together with the input shaft (11), and the outer member (22) of the one-way clutch (21) An output side fulcrum (19c) provided on the connecting member (19) is connected by a connecting rod (19), and the inner member (23) of the one-way clutch (21) is connected to the output shaft (12). transmission.

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