JP2014173666A - One-way rotation prevention mechanism and non-stage transmission using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a one-way rotation prevention mechanism that can efficiently transmit torque, and is hard to be broken even in a case where large torque is transmitted.SOLUTION: In a one-way rotation prevention mechanism 17, an elastic member 17g pressing a roller 17e against one of a pair of annular parts 17b is provided in the other one of the pair of the annular parts 17b forming a holding chamber 17d, and a projection part 17h is provided in the one of the pair of annular parts 17b forming the holding chamber 17d so as to project toward the other one side of the pair of annular parts 17b.

Description

  The present invention relates to a one-way rotation prevention mechanism and a continuously variable transmission using the same.

  2. Description of the Related Art Conventionally, a four-bar linkage mechanism type continuously variable transmission including an input shaft to which driving force from a driving source such as an engine is transmitted, an output shaft arranged in parallel with the input shaft, and a plurality of lever crank mechanisms. It is known (see, for example, Patent Document 1).

  In the continuously variable transmission described in Patent Document 1, a lever crank mechanism includes a rotation radius adjustment mechanism that is rotatable about an input shaft and is capable of adjusting a rotation radius, and a swing link that is pivotally supported by an output shaft. And a connecting rod in which one end is rotatably fitted to the turning radius adjusting mechanism and the other end is connected to the swing end of the swing link.

  The turning radius adjusting mechanism includes a disk-shaped rotating portion having a through hole formed eccentrically from the center, a ring gear provided on the inner peripheral surface of the through hole, and a first pinion fixed to the input shaft and meshing with the ring gear. And a carrier to which the driving force from the adjusting drive source is transmitted, and two second pinions that are pivotally supported by the carrier so as to rotate and revolve, and mesh with the ring gear. The first pinion and the two second pinions are arranged so that a triangle whose vertex is the center thereof is an equilateral triangle.

  In this turning radius adjusting mechanism, when the rotational speed of the input shaft rotated by the traveling drive source and the carrier rotated by the adjusting drive source are the same, the eccentric amount of the center of the rotating portion with respect to the rotational center axis of the input shaft is The turning radius of the turning radius adjusting mechanism is also kept constant. On the other hand, when the rotational speeds of the input shaft and the carrier are different, the amount of eccentricity of the center of the rotating portion with respect to the rotational center axis of the input shaft changes, and the rotational radius of the rotational radius adjusting mechanism also changes.

  Therefore, the turning radius adjusting mechanism changes the swing width of the swing end portion of the swing link, and thus the gear ratio, by changing the rotation radius, thereby controlling the rotational speed of the output shaft relative to the rotational speed of the input shaft. .

  In this continuously variable transmission, the distance between the center of the equilateral triangle whose apex is the center of the three pinions and the rotation center axis of the input shaft is the distance between the center of the equilateral triangle and the center of the rotating part. If they are set equal, the rotational center axis of the input shaft and the center of the rotating part can be overlapped to make the amount of eccentricity “0”. When the amount of eccentricity is “0”, even if the input shaft is rotating, the swing width of the swing end of the swing link is “0”, and the output shaft is not rotated.

  In the lever crank mechanism of the continuously variable transmission, a cam portion is constituted by the carrier and the second pinion, and the driving force from the adjustment drive source is transmitted to the cam portion.

  Further, the cam portion is set so that the phase is different for each lever crank mechanism, and the plurality of cam portions make a round in the circumferential direction of the input shaft. Therefore, each connecting link sequentially transmits torque to the output shaft and rotates the output shaft by the connecting rod whose one end is externally fitted to each turning radius adjusting mechanism.

  As shown in FIG. 12, this continuously variable transmission includes an output shaft 3 that is an inner member, a cage C, and an annular portion of a swing link that is an outer member into which the shaft is inserted. (Not shown).

  The cage C includes 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 pair of annular portions 17b. In the cage C, a plurality of holding chambers 17d are formed by two adjacent column portions 17c and a part of the pair of annular portions 17b.

  In each holding chamber 17d, one columnar roller 17e, which is a rolling element that rolls in conjunction with the rotation of the annular portion of the swing link that is the outer member, is disposed one by one.

Two springs 17f ₁ and 17f ₂ , which are first elastic members that urge the roller 17e toward the other of the pillars 17c, are provided on one of the two adjacent pillars 17c forming the holding chamber 17d. One is attached.

  Further, one of the pair of annular portions 17b forming the holding chamber 17d is urged so as to press the end face of the roller 17e toward the other of the pair of annular portions 17b to stabilize the posture of the roller 17e. In order to attenuate the energy at the time of vibration of 17e, the spring 17g which is a 2nd elastic member is attached.

  In such a one-way clutch composed of an inner member, an outer member, a cage, a rolling element, a first elastic member, and a second elastic member, the swing link is centered on the output shaft 3. When the roller 17e is engaged at a predetermined contact point 3b of the cam surface 3a formed on the outer peripheral surface of the output shaft 3, the swing link is fixed to the output shaft 3. When trying to rotate to the other side, the meshing between the roller 17e and the cam surface 3a is released, and the swing link is idled with respect to the output shaft.

  In this continuously variable transmission, the plurality of lever crank mechanisms rotate the output shaft 3 by each of the swing links transmitting torque in turn, so that when the torque is large, the output shaft 3 is twisted. May occur. At this time, since the annular portion 17b is fixed to the output shaft 3 and the column portion 17c is fixed to the annular portion 17b, the holding chamber 17d follows the twist of the output shaft 3 as shown in FIG. Deform.

JP 2012-1048 A

  However, since the roller 17e is urged by the spring 17g and is abutted against one of the pair of annular portions 17b, the roller 17e does not follow the twist of the output shaft 3 and has a posture parallel to the rotation center axis of the output shaft 3. There is to keep. That is, the roller 17e may be inclined with respect to the output shaft 3.

  In such a case, in the portion where the twist is small (for example, on the line A-A in FIG. 12), as shown in FIG. 13A, the roller 17 e is similar to the case where the output shaft 3 is not twisted. The torque can be transmitted by contacting the cam surface 3a at a predetermined contact point 3b on the outer peripheral surface of the output shaft 3.

  However, in a portion with a large twist (for example, on the line B-B in FIG. 12), the roller 17 e has a cam surface 3 a at a predetermined contact point 3 b on the outer peripheral surface of the output shaft 3 as shown in FIG. There is a possibility that torque cannot be transmitted.

  Further, when the cam surface 3a and the roller 17e are not in contact at the contact point 3b, the member constituting the one-way clutch because the edge of the roller 17e comes into contact with the annular portion 17b and the cage is worn. May be damaged.

  SUMMARY OF THE INVENTION In view of the foregoing, it is an object of the present invention to provide a one-way rotation prevention mechanism that can transmit torque without waste and is not easily damaged even when large torque is transmitted, and a continuously variable transmission using the same. And

  The one-way rotation preventing mechanism of the present invention includes an inner member, a pair of annular portions fitted around the inner member, and a holding chamber defined by a plurality of column portions provided between the pair of annular portions. A cylindrical outer member into which the inner member and the cage are inserted, a rolling element that is arranged in the holding chamber and rolls in conjunction with the rotation of the outer member or the inner member, and is arranged in the holding chamber. A first elastic member that biases the rolling element so as to be pressed against one of the two pillars forming the chamber, and meshes with the rolling element on the outer peripheral surface of the inner member and / or the inner peripheral surface of the outer member. In the one-way rotation prevention mechanism in which the cam surface is formed, one of the pair of annular portions is attached with a second elastic member that biases the rolling element so as to press against the other of the pair of annular portions, A protrusion protruding toward one side of the pair of annular portions on the other of the pair of annular portions Wherein the but has been formed.

  According to the one-way rotation preventing mechanism of the present invention, the first elastic member for biasing the rolling element and the second elastic member are provided in the holding chamber, and a convex portion is provided, and the end surface of the rolling element contacts the convex portion. Thus, even when a large torque is applied to the inner member and the twist is generated, the posture of the rolling element follows the twist of the inner member, and torque can be transmitted without waste. In addition, since vibration generated in the rolling elements can be suppressed, the retainer is not easily worn or damaged.

  In the one-way rotation preventing mechanism of the present invention, the convex portion preferably has a semi-cylindrical shape whose central axis is orthogonal to the axes of the pair of annular portions. If the convex portion is formed in this way, the end face of the rolling element and the convex portion come into line contact with each other, and the friction increases, so that the damping characteristic for suppressing the vibration of the rolling element becomes high.

  In the one-way rotation preventing mechanism of the present invention, the apex of the convex portion is preferably on a plane defined by the shafts of the pair of annular portions and the point that contacts when the cam surface and the rolling element mesh with each other. . If the apex of the convex part is configured to coincide with such a position, it is easy to keep the axis of the rolling element properly.

  In addition, the one-way rotation prevention mechanism of the present invention is capable of rotating around the input shaft and adjusting the rotation radius, the input shaft transmitting the driving force of the driving source, the output shaft arranged in parallel with the input shaft, A rotating radius adjusting mechanism, a swing link pivotally supported by the output shaft, and a connecting rod connecting the rotating radius adjusting mechanism and the swing link, and the rotational motion of the input shaft is controlled by the swing link swinging. The one-way rotation prevention mechanism fixes the swing link to the output shaft when the swing link is about to rotate about one side of the output shaft. The present invention can be applied to a continuously variable transmission that idles a rocking link with respect to an output shaft when attempting to rotate to the other side.

Sectional drawing which shows embodiment of the continuously variable transmission provided with the one way clutch which is the one way rotation prevention mechanism 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 shown in FIG. The disassembled perspective view which shows the structure of the one way clutch of the continuously variable transmission shown in FIG. The schematic diagram which shows the attitude | position of the roller at the time of no load of the one-way clutch of the continuously variable transmission shown in FIG. It is a schematic diagram which shows a part of cross-sectional shape of the one-way clutch shown in FIG. 9, (a) is sectional drawing which follows an AA line, (b) is sectional drawing which follows a BB line. The schematic diagram which shows the attitude | position of the roller at the time of high load of the one way clutch of the continuously variable transmission shown in FIG. It is a schematic diagram which shows a part of cross-sectional shape of the one-way clutch shown in FIG. 10, (a) is sectional drawing which follows an AA line, (b) is sectional drawing which follows a BB line. The schematic diagram which shows the attitude | position of the roller at the time of high load of the conventional one-way clutch. It is a schematic diagram which shows a part of cross-sectional shape of the one-way clutch shown in FIG. 12, (a) is sectional drawing which follows an AA line, (b) is sectional drawing which follows a BB line.

  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 gear ratio between the sun gear 9 and the first ring gear 10 ( When j is the number of teeth of the first ring gear 10 / the 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 swing link 18 is provided with a swing end portion 18a, and the swing end portion 18a is provided with a pair of projecting pieces 18b formed so as to sandwich the small-diameter annular portion 15b in the axial direction. Yes. The pair of projecting pieces 18b are formed with through holes 18c corresponding to the inner diameter of the small-diameter annular portion 15b. The connecting rod 15 and the swing link 18 are connected by inserting the connecting pin 19 into the through hole 18c and the small-diameter annular portion 15b. Further, the swing link 18 is provided with an annular portion 18d.

  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, the springs 17f ₁ and 17f _{2 that} are the first elastic members and the spring 17g that is the second elastic member are not shown. 8 and 10, only one cam surface 3a and roller 17e are shown, and the other cam surfaces and rollers are not shown.

  As shown in FIG. 7, the continuously variable transmission 1 according to the present embodiment is an output shaft 3 that is an inner member, a cage 17a, and a swing that is an outer member into which they are inserted as a one-way rotation prevention mechanism. A one-way clutch 17 having an annular portion 18d of the link 18 is provided.

  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. In the cage 17a, a plurality of holding chambers 17d are formed by a part of the pair of annular portions 17b and the two column portions 17c adjacent to each other.

  As shown in FIGS. 8 and 10, each holding chamber 17d has one roller 17e that is a rolling element that rolls in conjunction with the rotation of the annular portion 18d of the swing link 18 that is the outer member. Has been placed.

Two springs 17f ₁ and 17f _{2 that} are _first elastic members that urge the roller 17e toward the other of the column portions 17c are attached to one of the two adjacent column portions 17c.

  One end of the pair of annular portions 17b is biased so as to press the end face of the roller 17e toward the other of the pair of annular portions 17b to stabilize the posture of the roller 17e, and the energy is attenuated when the roller 17e vibrates. Therefore, a spring 17g as a second elastic member is attached.

  On the other side of the pair of annular portions 17b, a convex portion 17h that protrudes toward one of the pair of annular portions 17b is formed. The shape of the convex portion 17h is a semi-cylindrical shape whose central axis is orthogonal to the axis of the annular portion 17b. Further, the apex of the convex portion 17h is a point (contact point 3b) that contacts when the cam surface 3a formed on the outer peripheral surface of the output shaft 3 and the roller 17e that is a rolling element mesh with each other, and the annular portion 17b. It lies on a plane defined by the axis.

  In the continuously variable transmission 1 of the present embodiment, a one-way clutch 17 as a one-way rotation prevention mechanism is formed by these members.

  The one-way clutch 17 configured as described above has a predetermined contact point of the cam surface 3a formed on the outer peripheral surface of the output shaft 3 when the swinging link is about to rotate to one side about the output shaft 3. When the roller 17e meshes with the output shaft 3 in 3b, the rocking link is fixed to the output shaft 3 and the engagement between the roller 17e and the cam surface 3a is released when trying to rotate to the other side. On the other hand, it operates as a one-way rotation prevention mechanism that idles the swing link.

  By the way, in the continuously variable transmission 1 of the present embodiment, the six lever crank mechanisms 20 have their swing links 18 sequentially transmit torque to rotate the output shaft 3.

  When the transmitted torque is small, the output shaft 3 is not twisted, and the holding chamber 17d formed by the annular portion 17b fixed to the output shaft 3 and the column portion 17c fixed to the annular portion 17b. Does not deform following the twist of the output shaft 3. At this time, the posture of the roller 17e is parallel to the output shaft 3 as shown in FIG.

  For this reason, when the torque transmitted to the output shaft 3 is small, the roller 17e also has a B line in FIG. 8 as shown in FIG. Even on the -B line, the torque meshed with the cam surface 3a and transmitted from the swing link 18 can be transmitted to the output shaft 3 without waste.

  On the other hand, when the torque transmitted to the output shaft 3 is large, the output shaft 3 is twisted and formed by an annular portion 17b fixed to the output shaft 3 and a column portion 17c fixed to the annular portion 17b. The holding chamber 17d may be deformed following the twist of the output shaft 3. At this time, as shown in FIG. 10, the posture of the roller 17 e is tilted and parallel to follow the twist of the output shaft 3.

  This includes a spring 17g, which is a second elastic member that is urged so as to be pressed from one of the pair of annular portions 17b to the other, and a convex portion 17h formed on the other annular portion 17b against which the roller 17e abuts. Therefore, the roller 17e is held.

  For this reason, the roller 17e has a large transmission torque, even on the line AA in FIG. 10 as shown in FIG. 11A, as shown in FIG. Even on the line, it can mesh with the cam surface 3a and transmit the torque transmitted from the swing link 18 to the output shaft 3 without waste.

  Further, since the roller 17e is held by the spring 17g, which is the second elastic member, and the convex portion 17h, the vibration is greatly attenuated. Therefore, the end of the roller 17e, in particular, the edge of the end face is unlikely to come into contact with the annular portion 17b or the column portion 17c, and the retainer 17a is unlikely to be damaged such as wear.

  Furthermore, since the convex portion 17h has a semi-cylindrical shape, the roller 17e is in line contact. That is, since the contact area with the roller 17e is large, the friction between the roller 17e and the convex portion 17h is large, and the vibration of the roller 17e is attenuated in a short time.

  Although the illustrated embodiment has been described above, the present invention is not limited to such a form.

  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 cam surface 3a 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.

In the above embodiment, the springs 17f ₁ , 17f ₂ , and 17g are used as the elastic members, but elastic members other than the springs may be used.

  Moreover, in the said embodiment, although the convex part 17h was formed in the semi-cylinder shape whose center axis is orthogonal to the output shaft 3, you may form a convex part in a hemispherical shape.

  Furthermore, in the said embodiment, the holder | retainer 17a which has the some holding | maintenance chamber 17d 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, 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 portion, 16 ... connecting rod bearing , 17 ... one-way clutch (one-way rotation prevention mechanism), 17a ... cage, 17b ... annular part, 17c ... pillar part, 17d ... holding chamber, 17e ... roller (rolling element), 17f ₁ , 17f ₂ ... spring ( First elastic member), 17 g ... Spring (second elastic member), 17h ... convex portion, 18 ... swinging link, 18a ... swinging end, 18b ... projecting piece, 18c ... through hole, 18d ... annular portion (outer member), 19 ... connecting pin , 20 ... lever crank mechanism, i ... gear ratio, P1 ... rotation axis of the input shaft 2, P2 ... center of the cam disk 5, P3 ... center of the rotation disk 6, Ra ... distance between P1 and P2, Rb ... P2 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;
A cage having a pair of annular portions that are externally fitted to the inner member and a holding chamber defined by a plurality of column portions provided between the pair of annular portions;
A cylindrical outer member into which the inner member and the cage are inserted;
A rolling element disposed in the holding chamber and rolling in conjunction with rotation of the outer member or the inner member;
A first elastic member disposed in the holding chamber and biasing the rolling element so as to press against one of the two pillars forming the holding chamber;
A one-way rotation prevention mechanism in which a cam surface meshing with the rolling element is formed on an outer peripheral surface of the inner member and / or an inner peripheral surface of the outer member;
A second elastic member that urges the rolling element to be pressed against the other of the pair of annular portions is attached to one of the pair of annular portions,
The one-way rotation preventing mechanism, wherein a convex portion projecting toward one side of the pair of annular portions is formed on the other of the pair of annular portions. The unidirectional rotation prevention mechanism according to claim 1,
The unidirectional rotation blocking mechanism, wherein the convex portion has a semi-cylindrical shape whose central axis is orthogonal to the axis of the pair of annular portions. The one-way rotation prevention mechanism according to claim 1 or 2,
The one-way rotation prevention mechanism characterized in that the apex of the convex portion is on a plane defined by the axis of the pair of annular portions and a point that contacts when the cam surface and the rolling element mesh with each other. . One-way rotation prevention mechanism according to any one of claims 1 to 3,
An input shaft to which the driving force of the driving source is transmitted;
An output shaft disposed parallel to the input shaft;
A turning radius adjusting mechanism that is rotatable about the input shaft and capable of adjusting a turning radius, a swing link that is pivotally supported by the output shaft, and a connection that connects the turning radius adjusting mechanism and the swing link. A plurality of lever crank mechanisms that convert a rotational motion of the input shaft into a swing motion of the swing link,
The one-way rotation prevention mechanism is configured to fix the swing link with respect to the output shaft and to rotate to the other side when the swing link is about to rotate to one side around the output shaft. A continuously variable transmission characterized in that the swing link is idled with respect to the output shaft.