JP5982262B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission using a four-bar linkage mechanism.

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

  The lever crank mechanism disclosed in Patent Document 1 includes a rotation radius adjustment mechanism provided on an input shaft, a swing link pivotally supported on an output shaft, and a rotation radius adjustment mechanism at one end thereof. The connecting rod has an input-side annular portion that is externally fitted and the other end portion is connected to the swing end portion of the swing link.

  The turning radius adjusting mechanism includes a disk-shaped rotating disk having a through hole formed eccentrically from the center, a ring gear provided on the inner peripheral surface of the through hole, a first fixed to the input shaft and meshed with the ring gear. One pinion, a carrier to which a driving force from an adjustment driving 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, respectively. The first pinion and the two second pinions are arranged so that a triangle whose apex is the central axis thereof is an equilateral triangle.

  When the rotational speed of the input shaft rotated by the driving source for driving and the carrier rotated by the driving source for adjustment are the same, the eccentric amount of the center point of the rotating disk with respect to the input center axis of the input shaft is maintained and rotated. The radius of the rotation locus of the radius adjusting mechanism is also kept constant. When the rotational speed of the input shaft that is rotated by the driving source for driving and the carrier that is rotated by the driving source for adjustment are different, the eccentric amount of the center point of the rotating disk with respect to the input center axis of the input shaft changes, and the turning radius adjusting mechanism The radius of the rotation trajectory also changes.

  As the radius of the rotation locus of the rotation radius adjusting mechanism changes, the swing width of the swing end of the swing link also changes, and the gear ratio is switched to control the rotational speed of the output shaft relative to the input shaft.

  In such a continuously variable transmission, the distance between the center point of the equilateral triangle whose apex is the center axis of the three pinions and the input center axis of the input shaft, and the center point of the equilateral triangle and the center point of the rotating disk By setting the distance to be equal to each other, the input center axis and the center point of the rotating disk can be overlapped to make the amount of eccentricity zero. When the amount of eccentricity is 0, even when 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.

JP 2012-1048 A

  In the continuously variable transmission of the four-bar linkage mechanism type, when the radius of rotational motion of the rotational radius adjusting mechanism, that is, the amount of eccentricity is not “0”, the driving force is transmitted to the output shaft. Further, when the amount of eccentricity is small, the amount of increase in driving force with respect to the amount of increase in eccentricity becomes large. Therefore, unless the adjustment drive source is controlled with high accuracy, the driving force is transmitted or not transmitted to the output shaft repeatedly.

  In view of the above, the present invention is a continuously variable transmission that can maintain the radius of rotational motion of the rotational radius adjusting mechanism, that is, “0” of the eccentric amount, without controlling the adjusting drive source with high accuracy. The purpose is to provide.

[1] In order to achieve the above object, the present invention provides an input shaft to which a driving force from a travel drive source is transmitted, an output shaft arranged in parallel to the input shaft, and swingable to the output shaft. A plurality of lever crank mechanisms that convert a rotational movement of the input shaft into a swinging movement of the swinging link, and provided between the swinging link and the output shaft. The swing link is fixed to the output shaft when trying to rotate relative to the output shaft on one side, and the swing link relative to the output shaft when trying to rotate relative to the other side. And a one-way rotation preventing mechanism that idles, wherein the lever crank mechanism has an adjustment drive source and a rotation radius that can adjust the radius of the rotary motion on the input shaft side using the drive force of the adjustment drive source. An adjustment mechanism, and the turning radius adjustment mechanism and the swing link are coupled to each other. A continuously variable transmission having a connecting rod, wherein the turning radius adjusting mechanism is configured to be eccentric with respect to the input shaft and to rotate integrally with the input shaft; A rotating part that is rotatable in an eccentric state and a pinion to which the driving force of the adjusting drive source is transmitted, and the rotating part is provided with an inner peripheral part having internal teeth that mesh with the pinion. The radius of rotational motion of the rotational radius adjusting mechanism is “0” because the center of the pinion and the center of the rotating portion are concentrically positioned, and the radius of rotational motion of the rotational radius adjusting mechanism is “0”. The backlash of the portion of the inner peripheral portion where the pinion and the inner teeth of the inner peripheral portion mesh with each other is larger than the backlash of the other portion of the inner peripheral portion. It is characterized by.

  According to the present invention, when the radius of the turning radius adjusting mechanism becomes “0”, the backlash of the inner peripheral portion where the pinion and the inner teeth of the inner peripheral portion mesh with each other is caused by the backlash of the other portion of the inner peripheral portion. It is configured to be larger than the rush. For this reason, even when the radius of the turning radius adjusting mechanism becomes “0”, even if the pinion rotates slightly relative to the rotating portion due to the control error of the adjusting drive source, This operating error can be absorbed by a large backlash.

  Therefore, according to the continuously variable transmission of the present invention, it is possible to easily maintain the radius of rotation of the turning radius adjusting mechanism, that is, the eccentricity “0” without controlling the adjusting drive source with high accuracy. it can.

[2] Further, as means for increasing the backlash in the present invention , the internal teeth of the pinion and the inner peripheral portion when the radius of the turning radius adjusting mechanism becomes “0” by reducing the thickness of the inner teeth. It is also possible to make the backlash in the portion of the inner peripheral portion that meshes with that larger than the backlash in the other portion of the inner peripheral portion.

[3] Further, as means for increasing the backlash in the present invention, by partially increasing the radius of the inner peripheral portion, when the radius of the turning radius adjusting mechanism becomes “0”, the pinion and the inner peripheral portion It is also possible to make the backlash in the portion of the inner peripheral portion meshing with the inner teeth larger than the backlash in the other portion of the inner peripheral portion.

Sectional drawing which shows embodiment of the continuously variable transmission of this invention. Explanatory drawing which shows the turning radius adjustment mechanism, connecting rod, and rocking | fluctuation link of this embodiment from an axial direction. Explanatory drawing explaining the change of the rotation radius of the rotation radius adjustment mechanism of this embodiment. It is explanatory drawing which shows the relationship between the change of the rotation radius of the rotation radius adjustment mechanism of this embodiment, and the rocking | swiveling angle | corner (theta) 2 of the rocking | fluctuation motion of a rocking | fluctuation link, (a) is the largest rotation radius, (b) is rotation. (C) shows the rocking angle of the rocking motion of the rocking link when the radius is medium and the rotation radius is small. The graph which shows the change of angular velocity (omega) of a rocking | fluctuation link with respect to the change of the rotation radius of the rotation radius adjustment mechanism of this embodiment. 6 is a graph showing a state in which the output shaft is rotated by six lever crank mechanisms each having a phase difference of 60 degrees in the continuously variable transmission of the present embodiment. Explanatory drawing which shows the backlash of the part which a pinion and the internal tooth of an inner peripheral part mesh | engage when the radius of the rotational motion of the turning radius adjustment mechanism of this embodiment becomes "0".

  Hereinafter, embodiments of a control device for a four-bar linkage type continuously variable transmission according to the present invention will be described. In the four-bar linkage type continuously variable transmission of this embodiment, the speed ratio i (i = rotational speed of the input shaft / rotational speed of the output shaft) is infinite (∞), and the rotational speed of the output shaft is “0”. It is a kind of so-called IVT (Infinity Variable Transmission).

  With reference to FIGS. 1 and 2, the four-bar linkage type continuously variable transmission 1 according to the present embodiment receives a rotational driving force from a driving source for driving such as an engine or an electric motor, which is an internal combustion engine. A hollow input shaft 2 that rotates about an axis P1, and an output shaft 3 that is arranged in parallel to the input shaft 2 and transmits rotational power to driving wheels of a vehicle via a differential gear, a propeller shaft, etc. (not shown); And six turning radius adjusting mechanisms 4 provided on the input shaft 2.

  Each turning radius adjusting mechanism 4 includes a cam disk 5 as a cam part and a rotating disk 6 as a rotating part. 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 input center axis P1 and rotate integrally with the input shaft 2. Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the input shaft 2 with six sets of cam disks 5 with a phase difference of 60 degrees. In addition, a disc-shaped rotating disk 6 having a receiving hole 6a for receiving the cam disk 5 is rotatably fitted to each set of cam disks 5 in an eccentric state.

  In the rotating disk 6, the center point of the cam disk 5 is P2, the center point of the rotating disk 6 is P3, the distance Ra between the input center axis P1 and the center point P2, and the distance Rb between the center point P2 and the center point P3 are the same. So that it is eccentric with respect to the cam disk 5.

  The receiving hole 6 a of the rotating disk 6 is provided with internal teeth 6 b that are positioned between the pair of cam disks 5. In the present embodiment, the receiving hole 6a corresponds to the inner peripheral portion of the present invention. The input shaft 2 is formed with a notch hole 2 a that is positioned between a pair of cam disks 5 and that communicates the inner peripheral surface and the outer peripheral surface at a location facing the eccentric direction of the cam disk 5.

  In the hollow input shaft 2, a pinion shaft 7 that is disposed concentrically with the input shaft 2 and has external teeth 7 a at locations corresponding to the rotary disk 6 is disposed so as to be rotatable relative to the input shaft 2. . The external teeth 7 a of the pinion shaft 7 mesh with the internal teeth 6 b of the rotating disk 6 through the cutout holes 2 a of the input shaft 2. The pinion shaft 7 of this embodiment corresponds to the pinion of the present invention.

  A differential mechanism 8 is connected to the pinion shaft 7. The differential mechanism 8 is configured by 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, a sun gear 9 and A carrier 13 is provided that supports a stepped pinion 12 including a large-diameter portion 12a that meshes with the first ring gear 10 and a small-diameter portion 12b that meshes with the second ring gear 11 so as to rotate and revolve freely.

  The sun gear 9 is connected to a rotating shaft 14a of an adjustment drive source 14 composed of an electric motor for the pinion shaft 7. If the rotational speed of the adjustment 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, and the sun gear 9, the first ring gear 10, and the second ring The four elements of the 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 is. The number of rotations of the carrier 13 is (j · NR1 + Ns) / (j + 1) where j is the number of teeth of the first ring gear 10 / the number of teeth of the sun gear 9. 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 / tooth of the small diameter portion 12b) If the number)) is k, the rotation speed of the second ring gear 11 is {j (k + 1) NR1 + (k−j) Ns} / {k (j + 1)}.

  When 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, the rotating disk 6 rotates together with the cam disk 5. When there is a difference between the rotational speed of the input shaft 2 and the rotational speed of the pinion shaft 7, the rotating disk 6 rotates the periphery of the cam disk 5 around the center point 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 and the distance Rb are the same, and therefore the center point P3 of the rotating disk 6 is the same as the input center axis P1. The distance between the input center axis P1 and the center point P3, that is, the amount of eccentricity R1 can be set to “0” so as to be positioned on the axis.

  A connecting rod 15 having a large-diameter large-diameter annular portion 15a at one end and a small-diameter annular portion 15b having a smaller diameter than the large-diameter annular portion 15a at the other end is provided at the periphery of the rotating disk 6. A large-diameter annular portion 15a is rotatably fitted via a connecting rod bearing 16 made of a ball bearing. The output shaft 3 is provided with six swing links 18 corresponding to the connecting rod 15 via a one-way clutch 17 as a one-way rotation prevention mechanism.

  The one-way clutch 17 as a one-way rotation prevention mechanism is provided between the swing link 18 and the output shaft 3, and swings on the output shaft 3 when attempting to rotate relative to the output shaft 3 on one side. The link 18 is fixed, and the swing link 18 is idled with respect to the output shaft 3 when attempting to rotate relative to the other side. The swing link 18 is swingable with respect to the output shaft 3 when the one-way clutch 17 is idle with respect to the output shaft 3.

  The swing link 18 is formed in an annular shape, and a swing end portion 18 a connected to the small diameter annular portion 15 b of the connecting rod 15 is provided above the swing link 18. The swing end portion 18a is provided with a pair of projecting pieces 18b projecting so as to sandwich the small-diameter annular portion 15b in the axial direction. The pair of projecting pieces 18b are formed with through holes 18c corresponding to the inner diameter of the small-diameter annular portion 15b. A connecting pin 19 is inserted into the through hole 18c and the small diameter annular portion 15b. Thereby, the connecting rod 15 and the swing link 18 are connected.

  FIG. 3 shows the positional relationship between the pinion shaft 7 and the rotating disk 6 in a state where the eccentricity R1 of the turning radius adjusting mechanism 4 is changed. FIG. 3A shows a state in which the amount of eccentricity R1 is “maximum”, so that the input center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotating disk 6 are aligned. The pinion shaft 7 and the rotating disk 6 are located. At this time, 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. Become. FIG. 3D shows a state where the amount of eccentricity R1 is “0”, and the input center axis P1 and the center point P3 of the rotary disk 6 are located concentrically. The gear ratio i at this time is infinite (∞). The continuously variable transmission 1 of the present embodiment can adjust the radius of rotational motion on the input shaft 2 side by changing the amount of eccentricity R1 by the rotational radius adjusting mechanism 4.

  As shown in FIG. 2, the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 of the present embodiment constitute a lever crank mechanism 20 (four-bar linkage mechanism). Then, the lever crank mechanism 20 converts the rotational motion of the input shaft 2 into the swing motion of the swing link 18. The continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20. When the input shaft 2 is rotated and the pinion shaft 7 is rotated at the same speed as the input shaft 2 when the eccentric amount R1 is not “0”, each connecting rod 15 changes its phase by 60 degrees, and the eccentric amount R1. On the basis of this, it is repeatedly swung between the input shaft 2 and the output shaft 3 by alternately pushing to the output shaft 3 side or pulling to the input shaft 2 side.

  Since the small-diameter annular portion 15b of the connecting rod 15 is connected to the swing link 18 provided on the output shaft 3 via the one-way clutch 17, the swing link 18 is pushed and pulled by the connecting rod 15 to swing. Then, the output shaft 3 rotates only when the swing link 18 rotates in either the pushing direction side or the pulling direction side, and the output shaft 3 rotates when the swing link 18 rotates in the other direction. Thus, the force of the swing motion of the swing link 18 is not transmitted to the swing link 18, and the swing link 18 is idled. Since each turning radius adjusting mechanism 4 is arranged with a phase changed every 60 degrees, the output shaft 3 is rotated in turn by each turning radius adjusting mechanism 4.

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). It shows a swing range theta ₂ of the swinging link 18 for rotational movement of the rotational radius adjusting mechanism 4. As apparent from FIG. 4, as the eccentricity R1 becomes smaller, the swing range theta ₂ of the swinging link 18 is narrowed. When the eccentric amount R1 is “0”, the swing link 18 does not swing. Further, in the present embodiment, among the swing range theta ₂ of the oscillating end portion 18a of the swing link 18, the inner dead center position closest to the input shaft 2, and the outer dead center farthest position from the input shaft 2 To do.

  FIG. 5 shows the angular velocity ω accompanying the change in the eccentric amount 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. The relationship of changes is shown. 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 of the turning radius adjusting mechanism 4 when the six turning radius adjusting mechanisms 4 having different phases by 60 degrees are rotated (when the input shaft 2 and the pinion shaft 7 are rotated at the same speed). The angular velocity ω of each swing link 18 with respect to the angle θ1 is shown. As can be seen from FIG. 6, the output shaft 3 is smoothly rotated by the six lever crank mechanisms 20.

  Here, in the continuously variable transmission 1 of the four-bar linkage mechanism type, the driving force is transmitted to the output shaft 3 when the radius of the rotational motion of the rotational radius adjusting mechanism 4, that is, the eccentricity R 1 is not “0”. When the eccentric amount R1 is small, the amount of increase in the driving force of the output shaft 3 with respect to the amount of increase in the eccentric amount R1 is large. Therefore, unless the adjustment drive source 14 is controlled with high accuracy, the driving force is transmitted or not transmitted to the output shaft 3 repeatedly.

  Therefore, in the continuously variable transmission 1 of the present embodiment, as shown in FIG. 7, when the radius of the rotational motion of the rotational radius adjusting mechanism 4, that is, the eccentric amount R1 becomes “0”, the pinion shaft 7 and the inner peripheral portion The thickness of the inner teeth 6b of the portion X is set so that the backlash of the portion X of the receiving hole 6a that meshes with the inner teeth 6b of the receiving hole 6a is larger than the backlash of the other portion of the receiving hole 6a. It is configured to be thinner than the thickness of the other portion of the internal teeth 6b.

  According to the continuously variable transmission 1 of the present embodiment, the internal teeth of the pinion shaft 7 and the receiving hole 6a as the inner peripheral portion when the radius of the rotational motion of the rotational radius adjusting mechanism 4, that is, the eccentric amount R1 becomes “0”. The backlash of the part of the receiving hole 6a which meshes with 6b is comprised so that it may become larger than the backlash of the other part of the receiving hole 6a. For this reason, when the eccentric amount R1 of the turning radius adjusting mechanism 4 becomes “0”, the pinion shaft 7 is operated by rotating a little relative to the rotating disk 6 due to the control error of the adjusting drive source 14. Even if an error occurs, this operation error can be absorbed by play (gap) caused by a large backlash.

  Therefore, according to the continuously variable transmission 1 of the present embodiment, the radius of the rotational motion of the turning radius adjusting mechanism 4, that is, the eccentricity “0” can be easily achieved without controlling the adjusting drive source 14 with high accuracy. Can be maintained.

  Note that the magnitude of the output torque to the output shaft 3 with respect to the torque fluctuation due to the control error of the adjusting drive source 14 decreases in inverse proportion to the magnitude of the backlash in the portion X in FIG. “0”. Therefore, it is preferable to set the magnitude of the backlash of the portion X in FIG. 7 so that the output torque to the output shaft 3 with respect to the torque fluctuation due to the control error becomes “0”, but the present invention is not limited to this. It is sufficient that the output torque to the output shaft 3 against the torque fluctuation due to the control error can be suppressed by setting the backlash of the part X in FIG.

  Further, in the present embodiment, by reducing the thickness of the inner teeth 6b, the pinion shaft 7 and the inner peripheral portion when the radius of the rotational motion of the rotational radius adjusting mechanism 4, that is, the eccentric amount R1 becomes “0”. In the present invention, the backlash of the portion X of the receiving hole 6a with which the inner teeth 6b of the receiving hole 6a are engaged is larger than the backlash of the other portion of the receiving hole 6a. The configuration of the peripheral portion is not limited to this. For example, the radius of the receiving hole 6a in the portion X of FIG. 7 is made larger than the radius of the portion of the other receiving hole 6a to widen the space between the inner teeth 6b and the outer teeth 7a, thereby increasing the backlash. Also good.

  In the present embodiment, the one-way clutch 17 is used as the one-way rotation prevention mechanism. However, the one-way rotation prevention mechanism of the present invention is not limited to this, and torque is applied from the swing link 18 to the output shaft 3. May be configured by a two-way clutch (two-way clutch) configured to be able to switch the rotation direction of the swing link 18 capable of transmitting the rotation with respect to the output shaft 3.

DESCRIPTION OF SYMBOLS 1 Continuously variable transmission 2 Input shaft 2a Notch hole 3 Output shaft 4 Turning radius adjustment mechanism 5 Cam disk (cam part)
6 Rotating disc (rotating part)
6a Receiving hole (inner circumference)
6b Inner teeth 7 Pinion shaft (pinion)
7a External teeth 8 Differential mechanism (planetary gear 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 Adjustment drive source (motor)
14a Rotating shaft 15 Connecting rod 15a Large-diameter annular portion 15b Small-diameter annular portion 15c Lubricating oil hole 16 Connecting rod bearing 17 One-way clutch (one-way rotation prevention mechanism)
18 swing link 18a swing end 18b protrusion 18c through hole 19 connecting pin 20 lever crank mechanism (four-bar link mechanism)
21 Oil passage pipe 21a Discharge hole 22 Boundary plane 30 Transmission case 40 Control device 42 Brake detection unit 44 Shift position detection unit 46 Accelerator pedal opening detection unit 48 Vehicle speed detection unit P1 Input center axis P2 Cam disc center point P3 Rotating disc Center point Ra P1 and P2 distance Rb P2 and P3 distance R1 Eccentricity (P1 and P3 distance)
rotation angle theta ₂ swing range of θ1 rotational radius adjusting mechanism.

Claims (3)

An input shaft to which driving force from the driving source for traveling is transmitted;
An output shaft disposed parallel to the input shaft;
A plurality of lever crank mechanisms that have a swing link that is pivotally supported by the output shaft, and that converts a rotational motion of the input shaft into a swing motion of the swing link;
The swing link is provided between the swing link and the output shaft, and the swing link is fixed to the output shaft when attempting to rotate relative to the output shaft and relative rotation to the other side. A one-way rotation prevention mechanism that idles the swing link with respect to the output shaft when
The lever crank mechanism includes an adjustment drive source, a rotation radius adjustment mechanism capable of adjusting a radius of rotational motion on the input shaft side using a drive force of the adjustment drive source, the rotation radius adjustment mechanism, and the swinging mechanism. A continuously variable transmission provided with a connecting rod for connecting a dynamic link,
The turning radius adjusting mechanism includes:
A cam portion that rotates integrally with the input shaft in a state of being eccentric with respect to the input shaft;
A rotating part rotatable in an eccentric state with respect to the cam part;
A pinion to which the driving force of the adjustment driving source is transmitted,
The rotating portion is provided with an inner peripheral portion having inner teeth that mesh with the pinion,
The radius of the rotational motion of the rotational radius adjusting mechanism is “0” because the center of the pinion and the center of the rotating part are located concentrically,
When the radius of the rotational motion of the rotational radius adjusting mechanism becomes “0”, backlash of the inner peripheral portion where the pinion and the inner teeth of the inner peripheral portion mesh with each other is caused by another portion of the inner peripheral portion. A continuously variable transmission that is configured to be larger than the backlash. The continuously variable transmission according to claim 1, wherein
By reducing the thickness of the inner teeth, when the radius of the turning radius adjusting mechanism becomes “0”, the backlash of the inner peripheral portion where the pinion and the inner teeth of the inner peripheral portion mesh with each other is reduced. The continuously variable transmission is configured to be larger than the backlash of the other part of the inner peripheral portion.   The continuously variable transmission according to claim 1, wherein
  By partially increasing the radius of the inner peripheral portion, when the radius of the turning radius adjustment mechanism becomes “0”, the portion of the inner peripheral portion where the pinion and the inner teeth of the inner peripheral portion are engaged with each other. A continuously variable transmission, wherein the backlash is configured to be larger than the backlash of the other part of the inner periphery.

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