JP2014206268A - One-way rotation inhibiting mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a one-way rotation inhibiting mechanism capable of preventing damage without impairing a function to an excessive torque input.SOLUTION: A one-way rotation inhibiting mechanism 17 includes an output shaft 3 and an annular portion 18d rotated relatively to each other, an inclined face 31 formed on an outer peripheral face of the output shaft 3, and a roller 17e rolling on the inclined face 31. The inclined face 31 includes a first part 31a forming a first strut angle, and a second part 31b adjacent to the first part and forming a second strut angle. The second part 31b is formed in adjacent to an engagement direction of the first part 31a so that returning motion of the roller 17e by the second part 31b occurs when an output of a driving source for rotating the annular portion 18d is over a rated torque.

Description

  The present invention relates to a one-way rotation prevention mechanism that transmits only one-way torque from a drive source.

  Conventionally, inner and outer members arranged so as to be relatively rotatable, a plurality of inclined surfaces formed on the outer peripheral surface of the inner member and inclined with respect to the circumferential direction, and inner peripheral surfaces of the inclined surfaces and the outer member There is known a one-way rotation prevention mechanism including a biasing member that biases a rolling element with respect to a space that gradually decreases between the two (see, for example, Patent Document 1).

  In this one-way rotation prevention mechanism, relative rotation in one direction of the inner member and the outer member is prevented by biting each rolling element in each interval gradually decreasing space. Relative rotation in the other direction is allowed because the biting of each rolling element is released. As a result, the one-way rotation prevention mechanism transmits only one-way torque.

  Further, in this one-way rotation prevention mechanism, when a torque greater than a predetermined value is input to the one-way rotation prevention mechanism in a state where the relative rotation between the inner member and the outer member is prevented by the biting of the rolling elements, The fragile part of the member is broken and the transmission of torque is interrupted. This prevents the rolling element from popping out in the direction opposite to the biting direction, and minimizes damage to the one-way rotation prevention mechanism.

JP 2011-190849 A

  However, according to the one-way rotation prevention mechanism of Patent Document 1 described above, when a torque greater than a predetermined value is input, the fragile portion of the outer member breaks, thereby minimizing damage to the one-way rotation prevention mechanism. Suppressed. For this reason, overall damage to the one-way rotation prevention mechanism is avoided, but the function of the one-way rotation prevention mechanism is impaired.

  An object of the present invention is to provide a one-way rotation prevention mechanism capable of preventing damage without impairing the function with respect to an excessive torque input in view of the problems of the prior art.

  The one-way rotation preventing mechanism of the present invention includes an inner member having an outer peripheral surface, an outer member disposed so that an inner peripheral surface can be opposed to the outer peripheral surface, and the outer peripheral surface or the inner peripheral surface. And a plurality of inclined surfaces inclined in the circumferential direction, a plurality of rolling elements rolling on the inclined surface, and the inclined surface and the inner peripheral surface or the outer peripheral surface facing the inclined surface. A plurality of space gradually decreasing spaces formed so that a radial space gradually decreases in the circumferential direction of the inner peripheral surface; and a biasing member that urges the rolling elements in the space gradually decreasing space in the space gradually decreasing space. A torque from a driving source is input to the inner member or the outer member, and relative rotation in one direction of the inner member and the outer member is prevented by the biting of the rolling elements in the space gradually decreasing, Relative rotation in the other direction allows unidirectional rotation The inclined surface includes a contact position between the rolling element and the inclined surface, a contact position between the rolling element and the outer peripheral surface or the inner peripheral surface facing the inclined surface, and the rolling element. A first portion in which the strut angle determined by the rotation center is formed as a first strut angle in which the return motion of the rolling element does not occur, and a second portion in which the strut angle is formed as a second strut angle in which the return motion occurs. And the second part is adjacent to the biting direction of the first part so that when the output of the driving source exceeds a rated torque, the rolling action of the rolling element by the second part occurs. It is formed.

  In the present invention, the inner member and the outer member are relatively rotated (hereinafter referred to as “forward rotation”) so that the inner peripheral surface or the outer peripheral surface facing the inclined surface moves along the direction in which the interval of the gradually decreasing space decreases. .) When trying to do so, in the space gradually decreasing, the inclined surface and the inner peripheral surface or the outer peripheral surface facing the inclined surface bite the rolling elements, so that the inner member and the outer member are fixed to each other, and relative rotation is prevented. Is done.

  On the other hand, when the inner member and the outer member rotate relative to the forward rotation in the opposite direction (hereinafter referred to as “reverse rotation”), the rolling elements are not bitten and the relative rotation is prevented. Absent. Therefore, when the direction of the torque input from the drive source corresponds to forward rotation, the torque is transmitted through the one-way rotation blocking mechanism, and is not transmitted when corresponding to reverse rotation.

  During forward rotation, the position of the rolling element when being bitten in contact with the first portion of the inclined surface in the space gradually decreasing space is such that the larger the torque input from the drive source, the narrower the space in the space gradually decreasing space. That is, the position is moved in the biting direction. In this case, since the first portion has the above-described first strut angle, the rolling element does not return. For this reason, the torque from the drive source is transmitted without any trouble through the one-way rotation prevention mechanism. The returning operation means an operation for returning the rolling element from the biting position to a position where it is not bitten.

  On the other hand, when a disturbance torque is generated and a torque greater than the torque corresponding to the rated torque of the drive source and in the direction corresponding to the forward rotation is applied to the one-way rotation prevention mechanism, the rolling element and the inclined surface The contact position is displaced from the first portion of the inclined surface to the second portion. At this time, since the second portion has the second strut angle at which the rolling element returns, the returning action occurs and the rolling element is returned to the position where it is not bitten.

  As a result, it is possible to avoid the rolling element from being displaced to the end of the inclined surface and applying a large impact force, or the popping out of the rolling element with excessive force caused by the end. Damage to the rotation prevention mechanism can be prevented.

  In this case, torque transmission by the one-way rotation prevention mechanism is temporarily interrupted by the return operation, but thereafter, the rolling element does not perform the return operation due to a decrease or disappearance of disturbance torque or a decrease in torque from the drive source. Since it is bitten by one part, the function of the one-way rotation prevention mechanism is restored without any trouble.

  Therefore, according to the present invention, even when an excessive torque is input to the one-way rotation prevention mechanism, the one-way rotation prevention mechanism can be prevented from being damaged without impairing the function of the one-way rotation prevention mechanism. it can.

  In the present invention, the one-way rotation prevention mechanism includes an input shaft to which a driving force of a driving source is transmitted, an output shaft disposed in parallel with the input shaft, and a driving force transmitted to the input shaft. A plurality of lever crank mechanisms for transmitting to the rotation shaft, the lever crank mechanism being rotatable about the input shaft and having a rotation radius adjustment mechanism and a rotation radius adjustment mechanism supported by the output shaft. In a continuously variable transmission having a swing link, a connecting rod connecting the turning radius adjusting mechanism and the swing link, and converting the rotational motion of the input shaft into the swing motion of the swing link, The swing link is fixed to the output shaft when the swing link is about to rotate to one side around the output shaft, and the swing shaft is fixed to the output shaft when the swing link is about to rotate to the other side. Swing link empty To made the inner member from said output shaft, said outer member may be made of an annular portion constituting the inner peripheral portions of the swing links.

  According to this, even if a disturbance torque is generated due to a sudden impact such as a vehicle on which a continuously variable transmission is mounted climbs on a curb, and even if excessive torque is input to the one-way rotation prevention mechanism, it rotates in one direction. Damage to the one-way rotation blocking mechanism can be prevented without impairing the function of the blocking mechanism. In addition, the function of the one-way rotation prevention mechanism can be quickly recovered by shifting the continuously variable transmission to the low speed side while the above-described rolling element returning operation is caused by excessive torque.

  In the present invention, each inclined surface may be formed such that the strut angle on each inclined surface changes while taking different values until the rolling element returns on each inclined surface. According to this, since the return operation of the rolling element occurs at different timings on each inclined surface, the return operation is performed when an excessive torque exceeding the rated torque is input to the one-way rotation prevention mechanism and the return operation of the rolling element occurs. Can be prevented from concentrating on a specific part of the outer member or the inner member by simultaneously occurring on each inclined surface.

  In the present invention, after the return operation has occurred on one of the inclined surfaces, the return surface has not yet occurred and the inclined surfaces belonging to the group of the inclined surfaces having the largest number arranged in a row. In the case where there are two inclined surfaces located in the middle of the two or two inclined surfaces located in the middle, each inclined surface may be formed so that the returning operation occurs in one of the inclined surfaces.

  According to this, since the returning operation of the rolling elements on each inclined surface occurs in a temporally and spatially dispersed manner, it is possible to more effectively prevent the load from being concentrated on a specific part of the outer member or the inner member. be able to.

Sectional drawing which shows embodiment of the continuously variable transmission provided with the one way clutch which is a one way rotation prevention mechanism which concerns on one Embodiment of this invention. The schematic diagram which shows the turning radius adjustment mechanism, connecting rod, and rocking | fluctuation link of the continuously variable transmission shown in FIG. 1 from an axial direction. The schematic diagram which shows the change of the rotation radius of the rotation radius adjustment mechanism of the continuously variable transmission of FIG. FIG. 2 is a schematic diagram showing a relationship between a change in a rotation radius of a rotation radius adjustment mechanism of the continuously variable transmission of FIG. 1 and a swing angle of a swing motion of a swing link, where (a) shows the maximum rotation radius; ) Shows the swing angle of the swing motion of the swing link when the rotation radius is medium, and (c) shows the swing angle of the swing link when the rotation radius is small. The graph which shows the change of the angular velocity of the rocking | fluctuation link with respect to the change of the rotation radius of the rotation radius adjustment mechanism of the continuously variable transmission of FIG. The graph which shows the rotation state of the output shaft by the six lever crank mechanisms of the continuously variable transmission of FIG. The disassembled perspective view which shows the structure of the one way clutch of the continuously variable transmission of FIG. Sectional drawing of the one-way clutch of FIG. The schematic diagram which shows a part of cross-sectional shape of the one-way clutch of FIG. The graph which shows the time change of the angular velocity about the rocking | fluctuation link of the continuously variable transmission of FIG. The graph which shows the cross-sectional shape of the inclined surface of the one-way clutch shown in FIG. The figure which shows the strut and strut angle in a one way clutch. The graph which shows the change characteristic of the strut angle with respect to the change of the torsion angle about the one-way clutch of FIG. The graph which shows the change characteristic of the input torque with respect to the change of the torsion angle about the one-way clutch of FIG. The graph which shows the cross-sectional shape of the inclined surface of the conventional one-way clutch. The graph which shows the change characteristic of the strut angle with respect to the change of the torsion angle about the conventional one-way clutch. The graph which shows the change characteristic of the input torque with respect to the change of the torsion angle about the conventional one-way clutch. The flowchart which shows a part of process by the control part of the continuously variable transmission of FIG. (A) is a figure which shows a mode when each roller is located in a biting start position, when it assumes that the cyclic | annular part of a rocking | fluctuation link does not produce a shaft wobble with respect to an output shaft. These are figures which show a mode when each roller is located in a biting start position in the actual case where the said shaft runout occurs. It is sectional drawing of another one-way clutch applicable to the continuously variable transmission of FIG. It is a flowchart which shows an example of the procedure which attaches | subjects the order which return operation | movement arises with respect to each inclined surface in the one-way clutch of FIG. (A) shows the change of the strut angle α in the roller of each inclined surface with respect to the torsion angle β in the one-way clutch in which each inclined surface is formed so that the returning operation occurs according to the order given by the procedure of FIG. (B) shows the change in the torque τ transmitted by the one-way clutch with respect to the torsion angle β when the value of the torsion angle β exceeds β1 corresponding to the rated output and the return operation of each roller occurs.

  Hereinafter, an embodiment of a continuously variable transmission provided with a one-way rotation prevention mechanism of the present invention will be described. The continuously variable transmission of the present embodiment is a four-bar linkage mechanism type continuously variable transmission, and outputs with a gear ratio i (i = rotational speed of the input shaft / rotational speed of the output shaft) set to infinity (∞). This is a kind of transmission that can make the rotational speed of the shaft "0", so-called IVT (Infinity Variable Transmission).

  First, with reference to FIG.1 and FIG.2, the structure of the continuously variable transmission of this embodiment is demonstrated.

  The continuously variable transmission 1 according to the present embodiment includes an input shaft 2, an output shaft 3, and six turning radius adjustment mechanisms 4.

  The input shaft 2 is a hollow member, and rotates about the rotation center axis P <b> 1 of the input shaft 2 by receiving a rotational driving force from a driving source such as an internal combustion engine or an electric motor.

  The output shaft 3 is disposed in parallel with the input shaft 2 and transmits rotational power to a drive unit such as a drive wheel of a vehicle via a differential gear, a propeller shaft, and the like (not shown).

  Each of the turning radius adjusting mechanisms 4 is provided so as to rotate about the rotation center axis P1 of the input shaft 2, and includes a cam disk 5 as a cam part, a rotating disk 6 as a rotating part, and a pinion shaft 7. Have.

  The cam disks 5 have a disk shape, and are provided in pairs on the input shaft 2 so as to be eccentric from the rotation center axis P <b> 1 of the input shaft 2 and rotate integrally with the input shaft 2. Each set of cam disks 5 is set so as to have a phase difference of 60 °, and the six sets of cam disks 5 are arranged so as to make a round in the circumferential direction of the input shaft 2.

  The rotating disk 6 has a disk shape in which a receiving hole 6a is provided at a position eccentric from the center thereof, and is rotatably fitted to the cam disk 5 one by one through the receiving hole 6a. doing.

  The center of the receiving hole 6a of the rotating disk 6 is a distance Ra from the rotation center axis P1 of the input shaft 2 to the center P2 of the cam disk 5 (center of the receiving hole 6a) and the center P2 of the cam disk 5 to the rotating disk 6. The distance Rb to the center P3 is the same. The receiving hole 6 a of the rotating disk 6 is provided with an internal tooth 6 b at a position between the pair of cam disks 5.

  The pinion shaft 7 is disposed concentrically with the input shaft 2 in the hollow input shaft 2 and is rotatable relative to the input shaft 2. Further, external teeth 7 a are provided on the outer periphery of the pinion shaft 7. Further, a differential mechanism 8 is connected to the pinion shaft 7.

  By the way, the input shaft 2 is formed with a notch hole 2a between the pair of cam disks 5 at a location facing the eccentric direction of the cam disk 5 so that the inner peripheral surface and the outer peripheral surface communicate with each other. The external teeth 7 a provided on the outer periphery of the pinion shaft 7 are meshed with the internal teeth 6 b provided on the inner periphery of the receiving hole 6 a of the rotating disk 6 through the notch hole 2 a of the input shaft 2.

  The differential mechanism 8 is configured as a planetary gear mechanism, and includes a sun gear 9, a first ring gear 10 connected to the input shaft 2, a second ring gear 11 connected to the pinion shaft 7, the sun gear 9 and the first ring gear 10. And a carrier 13 that pivotally supports a stepped pinion 12 including a small-diameter portion 12b meshing with the second ring gear 11 so as to rotate and revolve. The sun gear 9 of the differential mechanism 8 is connected to a rotating shaft 14a of an adjustment drive source 14 composed of an electric motor for the pinion shaft 7.

  Therefore, when the rotational speed of the adjusting drive source 14 is the same as the rotational speed of the input shaft 2, the sun gear 9 and the first ring gear 10 rotate at the same speed, so that the sun gear 9, the first ring gear 10, the second gear The four elements of the ring gear 11 and the carrier 13 are locked so as not to rotate relative to each other, and the pinion shaft 7 connected to the second ring gear 11 rotates at the same speed as the input shaft 2.

When the rotational speed of the adjusting drive source 14 is made slower than the rotational speed of the input shaft 2, the rotational speed of the sun gear 9 is Ns, the rotational speed of the first ring gear 10 is NR1, and the sun gear 9 and the first ring gear 10
Where j is the gear ratio (number of teeth of the first ring gear 10 / number of teeth of the sun gear 9), the rotation speed of the carrier 13 is (j · NR1 + Ns) / (j + 1). Further, the gear ratio between the sun gear 9 and the second ring gear 11 ((number of teeth of the second ring gear 11 / number of teeth of the sun gear 9) × (number of teeth of the large diameter portion 12a of the stepped pinion 12 / number of teeth of the small diameter portion 12b). ) Is k, the rotation speed of the second ring gear 11 is {j (k + 1) NR1 + (k−j) Ns} / {k (j + 1)}.

  Therefore, when the rotational speed of the adjusting drive source 14 is made slower than the rotational speed of the input shaft 2, the rotational speed of the input shaft 2 to which the cam disk 5 is fixed and the rotational speed of the pinion shaft 7 are the same. In some cases, the rotating disk 6 rotates together with the cam disk 5. On the other hand, when there is a difference between the rotation speed of the input shaft 2 and the rotation speed of the pinion shaft 7, the rotating disk 6 rotates around the center P <b> 2 of the cam disk 5.

  As shown in FIG. 2, the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance Ra from P1 to P2 and the distance Rb from P2 to P3 are the same. Therefore, the center P3 of the rotating disk 6 is positioned on the same line as the rotation center axis P1 of the input shaft 2, and the distance between the rotation center axis P1 of the input shaft 2 and the center P3 of the rotating disk 6, that is, the eccentric amount R1 is set. It can also be set to “0”.

  A connecting rod 15 is rotatably fitted around the periphery of the rotating radius adjusting mechanism 4, specifically, the rotating disk 6 of the rotating radius adjusting mechanism 4.

  The connecting rod 15 has a large-diameter large-diameter annular portion 15a at one end, and a small-diameter annular portion 15b having a smaller diameter than the diameter of the large-diameter annular portion 15a at the other end. The large-diameter annular portion 15a of the connecting rod 15 is externally fitted to the rotary disk 6 via a connecting rod bearing 16 formed of a ball bearing.

  A swing link 18 is pivotally supported on the output shaft 3 via a one-way clutch 17 as a one-way rotation prevention mechanism.

  The one-way clutch 17 fixes the swing link 18 with respect to the output shaft 3 when rotating to the one side around the output shaft 3, and with respect to the output shaft 3 when trying to rotate to the other side. The swing link 18 is idled.

  The rocking link 18 has a rocking end 18a. By inserting a connecting pin 19 into the through hole 18c of the projecting piece 18b with respect to the rocking end 18a, the small-diameter annular portion 15b of the connecting rod 15 is inserted. It is connected with.

  Next, the lever crank mechanism of the continuously variable transmission according to this embodiment will be described with reference to FIGS.

  As shown in FIG. 2, in the continuously variable transmission 1 of the present embodiment, a lever radius adjusting mechanism 4, a connecting rod 15, and a swing link 18 constitute a lever crank mechanism 20 (four-bar linkage mechanism). ing.

  The lever crank mechanism 20 converts the rotational motion of the input shaft 2 into the swing motion of the swing link 18. As shown in FIG. 1, the continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20.

In this lever crank mechanism 20, when the eccentric amount R1 of the turning radius adjusting mechanism 4 is not "0", when the input shaft 2 and the pinion shaft 7 are rotated at the same speed, each connecting rod 15 has a phase of 60 degrees. While changing, the swing link 18 is swung by alternately repeating pushing between the input shaft 2 and the output shaft 3 toward the output shaft 3 and pulling toward the input shaft 2.

  Since the one-way clutch 17 is provided between the swing link 18 and the output shaft 3, the swing link 18 is pushed or pulled and the swing link 18 is swung. The dynamic link 18 is fixed, and the force of the swinging motion of the swinging link 18 is transmitted to the output shaft 3 to rotate the output shaft 3. In the other case, the swinging link 18 is idled to the output shaft 3. The force of the swing motion of the swing link 18 is not transmitted. Since the six turning radius adjusting mechanisms 4 are arranged by changing the phase by 60 degrees, the output shaft 3 is sequentially rotated by the six turning radius adjusting mechanisms 4.

  Moreover, in the continuously variable transmission 1 of this embodiment, as shown in FIG. 3, the rotation radius of the rotation radius adjustment mechanism 4 can be adjusted by changing the amount of eccentricity R1.

  FIG. 3A shows a state in which the amount of eccentricity R1 is “maximum”, and the rotation center axis P1 of the input shaft 2, the center P2 of the cam disk 5, and the center P3 of the rotation disk 6 are aligned. The pinion shaft 7 and the rotating disk 6 are located. In this case, the gear ratio i is minimized. FIG. 3B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 3A, and FIG. 3C illustrates that the eccentric amount R1 is smaller than that in FIG. Is shown. The gear ratio i is “medium” which is larger than the gear ratio i in FIG. 3A in FIG. 3B, and “large” which is larger than the gear ratio i in FIG. 3B in FIG. Shows the state. FIG. 3D shows a state where the amount of eccentricity R1 is “0”, and the rotation center axis P1 of the input shaft 2 and the center P3 of the rotating disk 6 are located concentrically. In this case, the gear ratio i is infinite (∞).

  FIG. 4 is a schematic diagram showing the relationship between the rotation radius of the rotation radius adjusting mechanism 4 of the present embodiment, that is, the change in the eccentricity R1 and the swing angle of the swing motion of the swing link 18.

  4A shows the case where the eccentric amount R1 is “maximum” in FIG. 3A (when the gear ratio i is the minimum), and FIG. 4B shows the case where the eccentric amount R1 is “ 4 (c) shows the case where the eccentric amount R1 is “small” in FIG. 3 (c) (when the gear ratio i is large). The swing range θ2 of the swing link 18 with respect to the rotational movement of the turning radius adjusting mechanism 4 is shown.

  As is apparent from FIG. 4, as the eccentric amount R1 becomes smaller, the swing range θ2 of the swing link 18 becomes narrower, and when the eccentric amount R1 becomes “0”, the swing link 18 swings. Stops moving.

  FIG. 5 shows a change in the amount of eccentricity R1 of the rotational radius adjusting mechanism 4 with the rotational angle θ of the rotational radius adjusting mechanism 4 of the continuously variable transmission 1 as the horizontal axis and the angular velocity ω of the swing link 18 as the vertical axis. It is a figure which shows the relationship of the change of angular velocity (omega).

  As can be seen from FIG. 5, the angular velocity ω of the swing link 18 increases as the eccentric amount R1 increases (the transmission ratio i decreases).

  FIG. 6 shows the rotation radius adjustment mechanism 4 when the six rotation radius adjustment mechanisms 4 whose phases are different by 60 degrees are rotated (when the input shaft 2 and the pinion shaft 7 are rotated at the same speed). It is a figure which shows angular velocity (omega) of each rocking | fluctuation link 18 with respect to this rotation angle (theta) 1.

  As apparent from FIG. 6, the output shaft 3 is smoothly rotated by the six lever crank mechanisms 20.

  Next, the shape of the one-way clutch 17 provided in the continuously variable transmission 1 of the present embodiment will be described in detail with reference to FIGS. However, in FIG.7 and FIG.8, the below-mentioned spring 17f which comprises an urging | biasing member is abbreviate | omitting illustration. Moreover, in FIG. 8, illustration of the below-mentioned cage 17a is omitted.

  As shown in FIGS. 7 and 8, the one-way clutch 17 serving as a one-way rotation prevention mechanism includes an output shaft 3 that is an inner member, a cage 17a, and an annular portion 18d that is an outer member into which these are inserted. Is provided. The annular portion 18 d constitutes an inner peripheral portion of the swing link 18. The annular portion 18d is arranged so that its inner peripheral surface can rotate relative to the outer peripheral surface of the output shaft 3.

  The cage 17a has a pair of annular portions 17b fixed to the outer peripheral surface of the output shaft 3, and a plurality of column portions 17c provided between the annular portions 17b. Further, a plurality of holding chambers are formed in the cage 17a by a part of the pair of annular portions 17b and the two column portions 17c adjacent to each other. In each holding chamber, a plurality of cams formed on the outer peripheral surface of the output shaft 3 are rollers 17e that are rolling elements that roll in conjunction with the rotation of the annular portion 18d of the swing link 18 that is an outer member. One surface is arranged on the surface 3a.

  A spring 17f that biases the roller 17e toward the other side of the column portion 17c is attached to one of the two adjacent column portions 17c.

  As shown in FIG. 9, an inclined surface 31 that is inclined with respect to the circumferential direction (X direction) of the outer peripheral surface of the output shaft 3 is provided as a part of the cam surface 3 a. Between each inclined surface 31 and the inner peripheral surface of the annular portion 18d facing this, a space gradually decreasing space 21 in which the space in the radial direction gradually decreases in the circumferential direction is formed. The spring 17f and the above-described retainer 17a function as a biasing member that biases the roller 17e in a direction in which the radial interval gradually decreases with respect to each interval gradually decreasing space 21.

  Further, the portion of the cam surface 3 a opposite to the inclined surface 31 is a convex portion 32 that is inclined and rises in the opposite direction to the inclined surface 31. The convex portion 32 prevents the roller 17e from deviating from the side opposite to the inclined surface 31 of the cam surface 3a.

  The one-way clutch 17 configured in this manner is configured so that the inner surface of the inclined surface 31 and the annular portion 18d in the space gradually decreasing space 21 when the swing link 18 is about to rotate to one side about the output shaft 3. By engaging the roller 17e with the surface, the rocking link 18 is fixed to the output shaft 3, and this engagement is released when trying to rotate to the other side. It operates as a one-way rotation prevention mechanism that idles the swing link.

  By the way, a large disturbance torque may be applied to the output shaft 3 when the vehicle rides on the curb. In this case, the disturbance torque and the torque from the drive source are added, and an excessive torque exceeding the rated torque of the drive source may be input to the one-way clutch 17. The state at this time is shown in FIG. 10 for one one-way clutch 17.

  10A and 10B, the horizontal axis represents time, and the vertical axis represents angular velocity. The graph curve 22 shows the time change of the angular velocity of the swing link 18, and the graph curve 23 shows the time change of the angular velocity of the output shaft 3. In FIG. 10, the torsion angle (twist angle) corresponding to the twist generated in the output shaft 3 corresponding to the magnitude of the torque transmitted to the output shaft 3 is shown by the area of the hatched portion 24.

During normal traveling, the torsion angle is small as shown in FIG. 10A, but when a large disturbance torque is applied to the output shaft 3, the output indicated by the graph curve 23 is shown in FIG. 10B. Since the angular velocity of the shaft 3 decreases, the torsion angle indicated by the area of the shaded portion 24 becomes extremely large.

  Then, an excessive torque is applied to the one-way clutch 17 and the roller 17e is displaced to the end of the inclined surface 31 (see FIG. 9) to give a large impact force, or the roller 17e is excessively applied to the end of the inclined surface 31. There is a risk of pop-out being replayed with extra power. Therefore, in the present embodiment, in order to avoid such a situation and prevent the one-way clutch 17 from being damaged, the following configuration is adopted for the inclined surface 31.

  FIG. 11 shows the cross-sectional shape of the inclined surface 31 in the space gradually decreasing space 21 with the horizontal axis as the position X along the outer periphery of the output shaft 3 and the vertical axis as the position Y in the direction perpendicular to the outer periphery (radial direction). .

  As shown in FIG. 11, the inclined surface 31 has a first strut angle that does not cause a return operation in the direction opposite to the biting direction (the increasing direction of X) of the roller 17 e bitten by the space gradually decreasing space 21. A first portion 31a having a second strut angle adjacent to the first portion 31a on the biting direction side with X1 as a boundary and causing the return operation; and biting of the second portion 31b And a third portion 31c that adjoins the direction side with X2 as a boundary and prevents the roller 17e from moving in the biting direction.

  Here, the returning operation means that the roller 17e bitten by the space gradually decreasing space 21 is bitten in the direction opposite to the biting direction by the inclined surface 31 and the inner peripheral surface of the annular portion 18d opposed to the inclined surface 31. It means an operation to return to a position that is not. The strut angle will be described later with reference to FIG.

  The second portion 31b is formed adjacent to the biting direction side of the first portion 31a so that when the output of the drive source exceeds the rated torque, the returning operation of the roller 17e occurs by the second portion 31b. The biting position of the roller 17e on the inclined surface 31 is displaced in the biting direction (increase direction of X) as the torque input from the drive source to the one-way clutch 17 increases.

  FIG. 12 shows the strut angle described above. As shown in FIG. 12, when considered in a cross section along the circumferential direction of the inner peripheral surface 18e of the annular portion 18d, the contact C1 where the first portion 31a of the inclined surface 31 and the roller 17e contact each other, and the inner periphery of the annular portion 18d A strut is defined as a straight line L connecting the surface 18e and the contact C2 where the roller 17e contacts. A strut angle is defined as an angle α formed by a straight line connecting the center point O of the roller 17e and the contact C1 or C2 and a straight line L indicating the strut.

  In order to stably transmit the torque without causing the returning operation of the roller 17e, the relationship between the frictional force F applied to the roller 17e and the force P causing the returning operation needs to satisfy F ≧ P. Further, if the coefficient of static friction between the first portion 31a and the roller 17e is μ, the force that the roller 17e receives from the first portion 31a in the vertical direction is N, and the force that the roller 17e receives in the strut direction is Q, F = μN = ΜQ cos α, P = Q sin α, so that tan α ≦ μ is required to satisfy F ≧ P.

  For example, when the Hertz surface pressure by the force Q is 4000 [MPa] or less, since 0.08 ≦ μ ≦ 0.10, α ≦ 4.5 [°] does not cause a return operation. Is a necessary condition. The return operation occurs when α> 4.5 [°]. Therefore, in this case, the first strut angle at which the return operation described above does not occur is 4.5 [°] or less, and the second strut angle at which the return operation occurs is a value exceeding 4.5 [°].

In FIG. 12, in addition to the roller 17e that contacts the first portion 31a and the inner peripheral surface 18e at the contacts C1 and C2, respectively, the roller 17e that contacts the first portion 31a and the inner peripheral surface 18e at the contacts C1 ′ and C2 ′ respectively. It is shown. Since the former has a larger value of the strut angle α than the latter, the return operation is more likely to occur than the latter.

  FIG. 13 shows the characteristics of the change in the strut angle α with respect to the change in the torsion angle β indicated by the area of the shaded portion 24 in FIG. 10 for the one-way clutch 17. In FIG. 13, α1 is the maximum value of the strut angle α that satisfies the requirement for preventing the roller 17e from returning, for example, the above-mentioned 4.5 [°].

  β1 is the value of the torsion angle β when the drive source outputs the rated torque. β2 is the value of the torsion angle β when the one-way clutch 17 is damaged when disturbance torque is applied and excessive torque is input to the one-way clutch 17 and the roller 17e reaches the third portion 31c. is there.

  When the torsion angle β is equal to or less than β1, the strut angle α is slightly smaller than α1 and is constant. A range in which the torsion angle β is equal to or less than β1 corresponds to the first portion 31 a of the inclined surface 31. In FIG. 11, the curve of the first portion 31 a portion swells slightly upward so that the strut angle α is constant.

  In this case, the contact position with the inclined surface 31 of the roller 17e bitten in the space gradually decreasing space 21 exists on the first portion 31a. The position gradually decreases as the torque input from the drive source increases. The space 21 is displaced in the direction in which the interval becomes narrow, that is, in the biting direction. When the drive source outputs the rated torque, the torsion angle β is β1, and the roller 17e is located at the portion of the inclined surface 31 that transitions from the first portion 31a to the second portion 31b.

  When the torsion angle β is equal to or less than β1, the returning operation of the roller 17e does not occur, so that the torque from the driving source is transmitted through the one-way clutch 17 without any trouble. The transition from the first portion 31a to the second portion 31b on the inclined surface 31 is performed such that the strut angle α continuously changes. For this reason, even when the roller 17e is displaced from the first portion 31a to the position on the second portion 31b due to excessive torque input, no impact is generated.

  When the torsion angle β exceeds β1 and is less than β2, the roller 17e contacts the second portion 31b (see FIG. 11) of the inclined surface 31. In this case, the strut angle α exceeds α1 and increases as the torsion angle β increases. For this reason, the returning operation of the roller 17e occurs in the range of the torsion angle β. Therefore, the roller 17e does not reach the third portion 31c (see FIG. 11) of the inclined surface 31.

  FIG. 14 shows a change characteristic of the torque τ input to the one-way clutch 17 with respect to the change of the torsion angle β indicated by the shaded portion 24 in FIG. In FIG. 14, β1 and β2 are the value of the torsion angle β when the drive source outputs the rated torque and the value of the torsion angle β at which the one-way clutch 17 is damaged, as in the case of FIG. τ1 is a value of torque τ that damages the one-way clutch 17.

  As shown in FIG. 14, when the torsion angle β is equal to or less than β1, the torque τ increases almost in proportion to the torsion angle β. When the torsion angle β exceeds β1 and is less than β2, the torque τ increases at a larger increase rate with respect to the change of the torsion angle β. However, as described above, since the returning operation of the roller 17e occurs before the torsion angle β reaches β2, the torsion angle β does not reach β2. Therefore, the torque τ does not exceed the large value τ1 that damages the one-way clutch 17.

  FIGS. 15 to 17 are comparative examples of the one-way clutch 17 of the present embodiment shown in FIGS. 11, 13, and 14 with respect to changes in the sectional shape of the inclined surface and the torsion angle β for the conventional one-way clutch. The change characteristic of the strut angle α and the change characteristic of the input torque τ with respect to the change of the torsion angle β are shown.

  As shown in FIGS. 15 and 16, in the inclined surface of the space gradually decreasing space of the conventional one-way clutch, the strut angle α is equal to or less than the maximum value α1 in the range of values that satisfy the requirements for preventing the return operation. A portion 32a and a portion 32b that adjoins the portion 32a in the biting direction (positive X direction) side with X3 as a boundary and prevents the movement of the roller 17e.

  In FIG. 16 and FIG. 17, β3 is a value of the torsion angle β at which excessive torque is input to the one-way clutch and the roller 17e reaches the portion 32b that prevents the movement, and the one-way clutch is damaged. Τ1 in FIG. 17 is a value of the input torque τ that causes the one-way clutch to be damaged.

  In this case, when there is no excessive torque input, the return operation does not occur because the strut angle α is equal to or less than the maximum value α1 that satisfies the requirement for preventing the return operation. When an excessive torque is input, the torsion angle β reaches β3 without causing a return operation, and the movement of the roller 17e is prevented by the inclined portion 32b. As a result, the torque τ immediately exceeds τ1, and the one-way clutch is damaged.

  FIG. 18 is a flowchart illustrating a part of the process performed by the control unit that controls the continuously variable transmission 1. This process is repeated at predetermined intervals. When the process is started, the control unit first determines whether or not the magnitude of acceleration (vehicle speed difference) a calculated from the vehicle speed is equal to or greater than a predetermined value ΔV (step S1). If it is determined that the value is not equal to or greater than the predetermined value ΔV, there is no situation in which the returning operation of the roller 17e occurs, so the processing of FIG.

  If it is determined that the value is equal to or greater than the predetermined value ΔV, it is determined whether or not a predetermined rapid deceleration has occurred in the rotation of the output shaft 3 (step S2). If it is determined that the rapid deceleration has not occurred, there is no situation in which the return operation of the roller 17e occurs, so the processing of FIG.

  If it is determined that sudden deceleration has occurred, an excessive torque is input to the one-way clutch 17 and the returning operation of the roller 17e by the second portion 31b of the inclined surface 31 occurs. Control is performed to reduce the eccentric amount R1 of the adjusting mechanism 4 to increase the gear ratio i of the continuously variable transmission 1 and shift to the low speed side. Then, the process of FIG. 18 is complete | finished.

  By appropriately performing the control to shift to the low speed side, the input of excessive torque is eliminated, so that the roller 17e is engaged with the first portion 31a of the inclined surface 31 where the return operation does not occur. . As a result, the one-way clutch 17 returns to a state where torque can be transmitted from the drive source without any problem.

  As described above, according to the present embodiment, torque τ1 that causes damage to the one-way clutch 17 even in a situation where a large disturbance torque is applied to the output shaft 3 as in the case of riding on a curb. Since the return operation of the roller 17e occurs before is input to the one-way clutch 17, it is possible to avoid the one-way clutch 17 from being damaged. Further, the function of the one-way clutch 17 can be immediately recovered by shifting the continuously variable transmission 1 to the low speed side while the return operation is occurring.

  However, if all the inclined surfaces 31 have the same position and shape with respect to the output shaft 3 that is the inner member, there is a possibility that the returning operation will occur simultaneously for all the rollers 17e. At the same time, when the return operation occurs, the transmission torque in the one-way clutch 17 decreases rapidly, and the behavior of the vehicle is greatly disturbed.

  Further, since the one-way clutch 17 is used in combination with the lever crank mechanism 20, the annular portion of the swing link 18 is mainly caused by the inertia force generated by the swing of the swing link 18 of the lever crank mechanism 20. 18 d causes shaft runout in a predetermined direction with respect to the output shaft 3.

  As a result, when the return operation occurs, the timing at which the return operation occurs differs between the roller 17e located on one side in the axial runout direction and the roller 17e located on the opposite side. The load tends to concentrate.

  FIG. 19 shows this in a simplified manner. That is, in FIG. 19A, the inclined surfaces 31 all have the same position and shape with respect to the output shaft 3, and the annular portion 18 d of the swing link 18 does not cause shaft runout with respect to the output shaft 3. The state when each roller 17e is located in the biting start position when it is assumed is shown.

  In this case, since all the inclined surfaces 31 have the same shape and are equidistant from the annular portion 18d, the engagement of all the rollers 17e is started simultaneously from the design position, and the returning operation is simultaneously performed. Arise. For this reason, the transmission torque in the one-way clutch 17 is rapidly reduced, and the behavior of the vehicle is greatly disturbed.

  On the other hand, in FIG. 19B, the inclined surfaces 31 all have the same position and shape with respect to the output shaft 3, and each roller 17e is in the biting start position in the actual case where the shaft portion is shaken in the annular portion 18d. The situation when it is located is shown.

  In this case, the roller 17e of the inclined surface 31 on the arrow Y1 side whose distance from the annular portion 18d is increased due to the axial deflection of the annular portion 18d is bitten from the position that has run up the inclined surface 31 from the designed position. Is started. That is, as the roller 17e of the inclined surface 31 whose distance from the annular portion 18d is farther, the returning operation occurs with a smaller torsion angle τ.

  Further, the roller 17e of the inclined surface 31 on the arrow Y2 side whose distance from the annular portion 18d becomes closer due to the axial deflection of the annular portion 18d is started to be bitten from a position below the designed surface. The That is, as the roller 17e on the inclined surface 31 is closer to the annular portion 18d, the returning operation occurs with a larger torsion angle τ.

  Therefore, the load on the annular portion 18d when the return operation occurs tends to concentrate on the arrow Y2 side of the annular portion 18d. Therefore, a one-way clutch that can eliminate this load concentration is shown below.

  FIG. 20 shows another example of the one-way clutch applicable to the continuously variable transmission 1. The one-way clutch 33 includes an inclined surface 34 that causes the return operation of each roller 17e to occur at different timings in place of the inclined surface 31 in the one-way clutch 17 described above. The inclined surface 34 includes a first portion 31a, a second portion 31b, and a third portion 31c having the same function as in the case of the inclined surface 31 described above.

  In the one-way clutch 33, the inclined surfaces 34 are configured such that the returning operation of the rollers 17e on the inclined surfaces 34 occurs in the order indicated by the numbers displayed in the vicinity of the inclined surfaces 34 in FIG. That is, in each inclined surface 34, return operation | movement arises at a different timing according to the ordered order.

  FIG. 21 shows an example of a procedure for assigning each inclined surface 34 the order in which the returning operation as shown in FIG. 20 is caused. That is, first, in step S1, “1” is set to “n”, and this is the order of the arbitrary inclined surface 34. Next, in step S2, the inclined surface 34 that should be given the next order is selected.

  At the time of this selection, the group of the inclined surfaces 34 that are not yet ordered and have the largest number in a row, or the inclined surfaces 34 belonging to one of the groups when there are a plurality of groups. An inclined surface 34 located in the middle is selected. When there are two inclined surfaces 34 located in the middle, one of the inclined surfaces 34 is selected. Or when the inclined surface 34 which is not ordered does not form the said group and is only a single thing, one of the inclined surfaces 34 is selected.

  At this time, when there are a plurality of selection candidates, for example, the last selected inclined surface 34 and further the inclined surface 34 as far as possible from the previous selected inclined surface 34 are selected. In short, the order of the inclined surfaces 34 is selected so as to be distributed and sequentially arranged without any deviation in time and position.

  Next, in step S3, 1 is added (incremented) to n. In step S4, the order of the selected inclined surfaces 34 is set to “n”. Next, in step S <b> 5, it is determined whether “n” has reached the number of inclined surfaces 34. If it is determined that it has not reached, the process returns to step S2. If it is determined that it has been reached, the ordering is terminated. Thereby, ordering as shown in FIG. 20 can be performed.

  Producing the returning operation according to this ordering determines the inclination of the portion of the inclined surface 34 that transitions from the first portion 31a to the second portion 31b and the distance from the rotation center of the output shaft 3 to the inclined surface 34. This can be realized by changing each inclined surface 34. That is, the inclined surface 34 is formed by utilizing the fact that the return operation occurs at an earlier timing, that is, at a smaller torsion angle τ, as the inclination is larger and the distance is larger. In other words, the inclined surface 34 is formed so that the strut angle α (see FIG. 12) at each inclined surface 34 is different at each timing. Note that the strut angle α is not limited to each one of the inclined surfaces 34 at each timing, but may be different for each of the plurality.

  However, as described above, the timing at which the return operation occurs also changes due to the above-described shaft runout, so that it is necessary to form each inclined surface 34 in consideration of this.

  FIG. 22A shows a change in the strut angle α at each inclined surface 34 with respect to the torsion angle β in the one-way clutch 33 in which the inclined surfaces 34 are formed according to the order in which the returning operations occur in this way. According to the graph curve Gn (n = 1, 2,..., 14) in FIG. 22 (a), the inclined surfaces whose order is “n” (n = 1, 2,..., 14), respectively. The change of the strut angle α in 34 rollers 17e is shown.

  As shown in FIG. 22A, the strut angle α at each inclined surface 34 at each timing is different. That is, the strut angle α in each inclined surface 34 changes while taking different values until the rolling element 17e returns to the inclined surface 34. When the value of the torsion angle β is equal to or less than β1 corresponding to the rated output, the rollers 17e are engaged with each inclined surface 34 at the strut angle α corresponding to each inclined surface 34. In this case, the value of the strut angle α corresponding to each inclined surface 34 is a value equal to or smaller than the maximum strut angle α1 that satisfies the above-described requirement not to cause the return operation.

  When the value of the torsion angle β exceeds β1, as the torsion angle β increases, the strut angle α increases as the biting position on each inclined surface 34 changes. When the strut angle α on each inclined surface 34 substantially exceeds a certain value α2 larger than α1 described above, the returning operation of the roller 17e on the inclined surface 34 occurs.

  The returning operation that occurs in each inclined surface 34 occurs in the order given to each inclined surface 34. That is, each time the torsion angle β increases and sequentially reaches the values b1,..., B14, the return operation occurs on the inclined surfaces 34 of the order 1,.

  FIG. 22B shows changes in the torque τ transmitted in the one-way clutch 33 when the value of the torsion angle β exceeds β1 corresponding to the rated output and the returning operation of each roller 17e occurs.

  In the graph curve Ln (n = 1) in FIG. 22B, it is assumed that all the inclined surfaces 34 are configured by the inclined surfaces 34 whose order is “n” (n = 1). The change in torque τ transmitted in the one-way clutch 33 is shown. However, this change is shown on the assumption that even if the torsion angle β increases, the return operation does not occur and the clutch 17 does not break.

  Similarly, other graph curves Ln (n = 2,..., 14) are inclined surfaces in which all the inclined surfaces 34 are in the order of “n” (n = 2,..., 14). Assuming that it is constituted by 34, a change in torque τ transmitted in the one-way clutch 33 is shown.

  As shown by the graph curve L, the torque τ value transmitted in the one-way clutch 33 is represented by the graph curve L14 and the graph curve L14 in the range where the returning operation of the roller 17e does not occur. It is an intermediate value between the values of torque τ shown.

  When the returning operation of the roller 17e occurs, each time the torsion angle β exceeds β1 corresponding to the rated output and reaches b1,. A return operation occurs on the inclined surface 34. For this reason, the torque τ transmitted in the one-way clutch 33 decreases as shown by the graph curve L because the torque transmitted by one roller 17e decreases every time the return operation occurs.

  When the value of the torsion angle β reaches b14, a return operation occurs on the last inclined surface 34 in the order 14, and the transmitted torque τ becomes zero.

  Thus, according to the one-way clutch 33, since the inclined surface 34 is formed so that the strut angle α on each inclined surface 34 is different at each timing, the returning operation of the roller 17e on each inclined surface 34 is It occurs at different timings for the roller 17e. For this reason, the transmitted torque τ is not abrupt but becomes zero over a certain period of time. Therefore, it is possible to prevent the behavior of the vehicle from being greatly disturbed or the load from being concentrated on a specific part of the annular portion 18d.

  Further, since each inclined surface 34 is formed so that the returning operation on each inclined surface 34 occurs in a temporally and spatially dispersed manner, it is extremely effective that the load concentrates on a specific part of the annular portion 18d. Can be prevented.

In addition, this invention is not limited to the said embodiment. For example, although the case where the one-way rotation prevention mechanism of the present invention is used as the one-way clutch 17 of the continuously variable transmission 1 has been described in the above embodiment, it may be used for devices other than the continuously variable transmission.

  Moreover, in the said embodiment, the inclined surface 31 was formed in the outer peripheral surface of the output shaft 3 which is an inner member. However, you may form in the internal peripheral surface of the cyclic | annular part 18d of the rocking | fluctuation link 18 which is an outer side member. Further, it may be formed on both the outer peripheral surface of the output shaft 3 and the inner peripheral surface of the annular portion 18d of the swing link 18.

  In the above-described embodiment, the inner member and the output shaft 3 are an integral member, and the outer member and the annular portion 18d of the swing link 18 are an integral member. However, the inner member and the output shaft 3 may be separate members, and the outer member and the annular portion 18d of the swing link 18 may be separate members.

  Moreover, in the said embodiment, although the spring 17f was used as an urging member, you may use urging members other than a spring.

  Furthermore, in the said embodiment, the holder | retainer 17a which has several holding | maintenance chambers is comprised by the annular | circular shaped pair of annular part 17b and the pillar part 17c provided between them. However, the holding chamber is not limited to such a configuration. For example, a concave portion may be formed on the outer peripheral surface of the inner member, and the inner member and the cage may be integrated with the concave portion as a holding chamber.

DESCRIPTION OF SYMBOLS 1 ... Continuously variable transmission, 2 ... Input shaft, 2a ... Notch hole, 3 ... Output shaft (inner member), 3a ... Cam surface, 3b ... Contact point, 4 ... Turning radius adjustment mechanism, 5 ... Cam disk, 6 ... Rotating disc, 6a ... receiving hole, 6b ... internal teeth, 7 ... pinion shaft, 7a ... external teeth, 8 ... differential mechanism, 8a ... differential mechanism case, 9 ... sun gear, 10 ... first ring gear, 11 ... second Ring gear, 12 ... Stepped pinion, 12a ... Large diameter portion, 12b ... Small diameter portion, 13 ... Carrier, 14 ... Adjusting drive source, 14a ... Rotating shaft, 15 ... Connecting rod, 15a ... Large diameter annular portion, 15b ... Small diameter Annular part, 16 ... connecting rod bearing, 17 ... one-way clutch (one-way rotation prevention mechanism), 17a ... retainer, 17b ... annular part, 17c ... column part, 17e ... roller (rolling element), 17f ... spring (biasing) Member), 18 ... swing link, 18 ... rocking end part, 18b ... projecting piece, 18c ... through hole, 18d ... annular part (outer member), 19 ... connecting pin, 20 ... lever crank mechanism, 21 ... space gradually decreasing space, 31, 34 ... inclined surface, 31a ... 1st part, 31b ... 2nd part, 31b ... 3rd part, i ... Gear ratio, P1 ... Rotation center axis of input shaft 2, P2 ... Center of cam disk 5, P3 ... Center of rotation disk 6, Ra ... P1 and P2 distance, Rb... P2 and P3 distance, R1... P1 and P3 distance (eccentricity), .theta.1... Rotation angle of the turning radius adjusting mechanism 4, .theta.2.

Claims (4)

An inner member having an outer peripheral surface;
An outer member disposed such that an inner circumferential surface can rotate relative to the outer circumferential surface;
A plurality of inclined surfaces formed on the outer peripheral surface or the inner peripheral surface and inclined in the circumferential direction;
A plurality of rolling elements that roll on the inclined surface;
A plurality of space gradually decreasing spaces formed such that a radial space gradually decreases in the circumferential direction of the inner peripheral surface between the inclined surface and the inner peripheral surface or the outer peripheral surface facing the inclined surface;
An urging member that urges the rolling elements in a direction in which the interval gradually decreases in the space gradually decreasing;
Torque from a driving source is input to the inner member or the outer member,
A relative rotation in one direction of the inner member and the outer member is prevented by the biting of the rolling elements in the space gradually decreasing space, and a relative rotation in the other direction is allowed;
The inclined surface is a strut determined by a contact position between the rolling element and the inclined surface, a contact position between the rolling element and the outer peripheral surface or the inner peripheral surface facing the inclined surface, and a rotation center of the rolling element. A corner including a first portion formed as a first strut angle at which the rolling element does not return, and a second portion formed as a second strut angle at which the strut angle causes the return motion;
The second portion is formed adjacent to the biting direction of the first portion so that when the output of the drive source exceeds a rated torque, the rolling motion of the second portion is returned by the second portion. One-way rotation prevention mechanism characterized by this. The unidirectional rotation prevention mechanism according to claim 1,
An input shaft to which the driving force of the driving source is transmitted, an output shaft disposed in parallel with the input shaft, and a plurality of lever crank mechanisms for transmitting the driving force transmitted to the input shaft to the output shaft; The lever crank mechanism is rotatable about the input shaft and is capable of adjusting a rotation radius; a swing link supported on the output shaft; and the rotation radius adjustment mechanism; A continuously variable transmission having a connecting rod for connecting to the swing link and converting the rotational motion of the input shaft to the swing motion of the swing link, wherein the swing link is centered on the output shaft; In order to fix the swing link with respect to the output shaft when trying to rotate to one side, and to idle the swing link with respect to the output shaft when trying to rotate to the other side, The member is the output From made, said outer member in one direction rotation preventing mechanism, characterized by comprising an annular portion constituting the inner peripheral portions of the swing links.   3. Each inclined surface is formed so that the strut angle in each inclined surface changes with a different value until the rolling element returns in each inclined surface. One-way rotation prevention mechanism.   Positioned in the middle of the inclined surfaces belonging to the group of the inclined surfaces having the largest number that are continuously arranged after the returning operation has occurred on one of the inclined surfaces. 4. The inclined surface according to claim 3, wherein each of the inclined surfaces is formed so that the return operation occurs in one of the inclined surfaces when there are two inclined surfaces positioned in the middle or in the middle. 5. One-way rotation prevention mechanism.