JP2013019429A - Four-bar linkage type continuous variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the come-off of a bearing for an eccentric mechanism of a four-bar linkage type continuously variable transmission.SOLUTION: The continuously variable transmission 1 comprises a plurality of the eccentric mechanisms 4 each having a fixed disk 5 and an oscillating disk 6. A receiving hole 6a for receiving an input shaft 2 and the fixed disk 5 is fixed at the oscillating disk 6. The receiving disk 6a is formed of a small-diameter hole 6c positioned in the axial center and a large-diameter hole 6d which is formed so as to axially surround the small-diameter hole 6c, and a step 6e formed between the small-diameter hole 6c and the large-diameter hole 6d. The bearing 21 for the eccentric mechanism is arranged between the fixed disk 5 and a large-diameter hole 6d. The bearing 21 comprises a retainer 23 for holding a plurality of rolling bodies 22 and an outer ring 24. A hanging part 24a hanging between the step 6a and the fixed disk 5 is formed at the outer ring 24.

Description

  The present invention relates to a four-bar link type continuously variable transmission that can be changed by adjusting an amount of eccentricity by an eccentric mechanism provided on an input shaft.

  Conventionally, a hollow input shaft to which driving force from a drive source such as an engine provided in a vehicle is transmitted, an output shaft arranged in parallel with the input shaft, and a plurality of eccentric mechanisms provided on the input shaft, There are a plurality of swing links pivotally supported on the output shaft, a large-diameter annular portion that is rotatably fitted to the eccentric mechanism at one end, and the other end of the swing link There is known a four-bar link type continuously variable transmission including a connecting rod connected to a swing end (see, for example, Patent Document 1).

  In Patent Document 1, each eccentric mechanism is composed of a fixed disk provided eccentrically on the input shaft, and a swinging disk provided eccentrically on the fixed disk and rotatably provided. A one-way clutch is provided between the swing link and the output shaft. The one-way clutch fixes the swing link to the output shaft when the swing link is about to rotate relative to the output shaft, and To idle the swing link.

  A pinion shaft is inserted into the input shaft, and a notch hole is formed at a location facing the eccentric direction of the fixed disk, and the pinion shaft is exposed from the notch hole. The swing disk is provided with a receiving hole for receiving the input shaft and the fixed disk. Inner teeth are formed on the inner peripheral surface of the swing disk that forms the receiving hole.

  The inner teeth mesh with the pinion shaft exposed from the notch hole of the input shaft. When the input shaft and the pinion shaft are rotated at the same speed, the eccentric amount of the eccentric mechanism is maintained. When the rotational speeds of the input shaft and the pinion shaft are made different, the eccentric amount of the eccentric mechanism is changed, and the transmission gear ratio is changed.

  When the eccentric mechanism is rotated by rotating the input shaft, the large-diameter annular portion of the connecting rod rotates and the swing end of the swing link connected to the other end of the connecting rod swings. . Since the swing link is provided on the output shaft via the one-way clutch, the rotational drive force (torque) is transmitted to the output shaft only when rotating to one side.

  The eccentric direction of the fixed disk of each eccentric mechanism is set so as to make a round around the input shaft with different phases. Therefore, the swinging link sequentially transmits the torque to the output shaft by the connecting rod fitted to each eccentric mechanism, so that the output shaft can be smoothly rotated.

JP-T-2005-502543

  An eccentric mechanism bearing is disposed between the fixed disk and the oscillating disk. In order to prevent the eccentric mechanism bearing from falling off, it is conceivable to attach a stopper to the fixed disk or the swing disk. However, the process of attaching a stopper increases and is troublesome. In addition, the number of components of the transmission increases, and the manufacturing cost, weight, and space also increase, which contributes to the deterioration of efficiency.

  In view of the above, the present invention is a four-bar link type continuously variable transmission that can prevent the eccentric mechanism bearing disposed between the fixed disk and the oscillating disk from dropping without increasing the number of manufacturing steps and the number of parts. The purpose is to provide a machine.

  [1] In order to achieve the above object, the present invention provides a hollow input shaft to which a driving force from a vehicle drive source is transmitted, an output shaft arranged in parallel with the input shaft, and a bias to the input shaft. A plurality of eccentric mechanisms having a fixed disk provided in the center, a swing disk provided eccentrically with respect to the fixed disk, and a plurality of swing links pivotally supported by the output shaft; The swing link is fixed to the output shaft and is relatively rotated to the other side when attempting to rotate relative to the output shaft on one side. A one-way rotation prevention mechanism that idles the swinging link with respect to the output shaft when attempting to, a large-diameter annular portion that is rotatably fitted to the eccentric mechanism at one end, and the other Connected to the end of the swing link connected to the swing end of the swing link A rod and a pinion shaft inserted into the input shaft, and the input shaft is formed with a notch at a location facing the eccentric direction of the fixed disk, and the pinion shaft is exposed from the notch. The swing disk is provided with a receiving hole for receiving the input shaft and the fixed disk, and an inner tooth is formed on the inner peripheral surface of the swing disk forming the receiving hole. By engaging with the pinion shaft exposed from the notch hole of the input shaft and rotating the input shaft and the pinion shaft at the same speed, the eccentric amount of the eccentric mechanism is maintained, and the input shaft and the pinion shaft A continuously variable transmission for controlling a gear ratio by changing an eccentric amount of the eccentric mechanism by varying a rotational speed, wherein the receiving hole is located at an axial center and the inner teeth The small-diameter hole formed and the large-diameter hole larger in diameter than the small-diameter hole arranged so as to sandwich the small-diameter hole in the axial direction, and a step between the small-diameter hole and the large-diameter hole And a bearing for an eccentric mechanism is disposed between the outer peripheral surface of the fixed disk and the inner peripheral surface of the large-diameter hole. The eccentric mechanism bearing includes a plurality of rolling elements, The outer ring or the inner ring is provided with a projecting portion that projects between the stepped portion and the fixed disk.

  According to the present invention, since the overhanging portion is sandwiched between the step portion and the fixed disk, it is possible to prevent the eccentric mechanism bearing from falling off. In addition, because the overhang is provided on the outer ring or inner ring as a component of the eccentric mechanism bearing, there is no need to provide a separate stopper or the like for the eccentric mechanism bearing, and a four-bar link type continuously variable The transmission can be easily manufactured.

  [2] Here, when providing an overhang portion on the outer ring of the eccentric mechanism bearing, the side wall extending radially inward from the peripheral edge of the eccentric mechanism bearing on the side where the outer ring overhang portion is not provided is provided on the fixed disk. If it extends to the outer peripheral surface, it becomes difficult for the lubricating oil scattered in the transmission to enter the eccentric mechanism bearing. In this case, if the side wall extending radially inward from the peripheral edge of the outer ring opposite to the side where the protruding portion is provided is configured so that the inner edge thereof is spaced from the outer peripheral surface of the fixed disk, the protruding portion Lubricating oil can be appropriately taken in from the peripheral side opposite to the above, and the eccentric mechanism bearing can be lubricated and cooled satisfactorily.

Sectional drawing which shows embodiment of the four-bar link type continuously variable transmission of this invention. Explanatory drawing which shows the eccentric mechanism of this embodiment, a connecting rod, and a rocking | fluctuation link from an axial direction. Explanatory drawing explaining the change of the eccentric amount of the eccentric mechanism of this embodiment. It is explanatory drawing which shows the relationship between the change of the eccentric amount of the eccentric mechanism of this embodiment, and the range of the rocking | fluctuation motion of a rocking | fluctuation link, (a) is the maximum amount of eccentricity, (b) is the amount of eccentricity, (C) shows the swing range of the swing link when the amount of eccentricity is small. The graph which shows the change of the angular velocity of a rocking | fluctuation link with respect to the change of the eccentric amount of the eccentric mechanism of this embodiment. In the continuously variable transmission of this embodiment, the graph which shows the state in which an output shaft is rotated by six four-bar linkage mechanisms which respectively made the phase different 60 degree | times. Sectional drawing which shows the bearing for eccentric mechanisms of this embodiment. Sectional drawing which expands and shows the bearing for eccentric mechanisms of this embodiment. The schematic diagram which shows the space | interval of the rolling element of the bearing for eccentric mechanisms of this embodiment.

  Embodiments of a four-bar link continuously variable transmission according to the present invention will be described below. The continuously variable transmission according to the present embodiment is a transmission capable of setting the speed ratio i (i = rotational speed of the input shaft / rotational speed of the output shaft) to infinity (∞) and the rotational speed of the output shaft to “0”. It is a kind of so-called Infinity Variable Transmission (IVT).

  1 and 2, the continuously variable transmission 1 of the present embodiment receives an input central axis P1 by receiving rotational power from a vehicle drive source such as an internal combustion engine (not shown) or an electric motor. A hollow input shaft 2 that rotates about the center, and an output shaft 3 that is arranged in parallel to the input shaft 2 and that transmits rotational power to drive wheels (not shown) of the vehicle via a differential gear, a propeller shaft, etc. (not shown) And six eccentric mechanisms 4 provided on the input shaft 2.

  Each eccentric mechanism 4 includes a fixed disk 5 and a swing disk 6. The fixed 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. One set of fixed disks 5 of each eccentric mechanism 4 is arranged so that the phases thereof are different from each other by 60 degrees so that the six sets of fixed disks 5 make a round in the circumferential direction of the input shaft 2. Further, a disc-shaped rocking disc 6 having a receiving hole 6a for receiving the fixed disc 5 is eccentrically fitted to each set of fixed discs 5 so as to be rotatable.

  The oscillating disk 6 has a center point of the fixed disk 5 as P2, a center point of the oscillating disk 6 as P3, a distance Ra between the input center axis P1 and the center point P2, and a distance Rb between the center point P2 and the center point P3. Are eccentric with respect to the fixed disk 5 so as to be the same.

  The receiving hole 6 a of the swing disk 6 is provided with an internal tooth 6 b positioned between the pair of fixed disks 5. The input shaft 2 is formed between a pair of fixed disks 5 and is formed with a notch hole 2 a that communicates the inner peripheral surface and the outer peripheral surface at a location facing the eccentric direction of the fixed disk 5.

  The input shaft 2 is pivotally supported by the transmission case 1a via an input shaft bearing 2b. The input shaft bearing 2b is press-fitted into a hole provided in the transmission case 1a. The input shaft 2 is press-fitted into the input shaft bearing 2b. The input shaft bearing 2b or the input shaft 2 may be fitted to the transmission case 1a or the input shaft bearing 2b so as to have a very small gap. The adjustment accuracy of the gear ratio of the step transmission 1 is improved.

  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 swing disk 6 is disposed so as to be rotatable relative to the input shaft 2. Yes. The external teeth 7 a of the pinion shaft 7 mesh with the internal teeth 6 b of the swing disk 6 through the cutout holes 2 a of the input shaft 2.

  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 rotation shaft 14a of a drive source 14 composed of an electric motor for the pinion shaft 7. When the rotational speed of the 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 gear 11 are rotated. In addition, the four elements of the carrier 13 are in a locked state where relative rotation is impossible, 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 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 (first The number of rotations of the carrier 13 is (j · Nr1 + Ns) / (j + 1) where j is the number of teeth of one 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) (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 fixed disk 5 is fixed and the rotational speed of the pinion shaft 7 are the same, the oscillating disk 6 rotates together with the fixed 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 oscillating disk 6 rotates the periphery of the fixed disk 5 around the center point P <b> 2 of the fixed disk 5.

  As shown in FIG. 2, the oscillating disk 6 is eccentric with respect to the fixed disk 5 so that the distance Ra and the distance Rb are the same, so that the center point P3 of the oscillating disk 6 is set to the input center axis P1. The distance between the input center axis P1 and the center point P3, that is, the eccentric amount R1 can be set to “0”.

  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 swing disk 6. The large-diameter annular portion 15a is rotatably fitted via a roller bearing 16. 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 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 oscillating disk 6 in a state where the eccentric amount R1 of the eccentric mechanism 4 is changed. FIG. 3A shows a state in which the eccentricity R1 is set to “maximum”, and the input center axis P1, the center point P2 of the fixed disk 5, and the center point P3 of the swing disk 6 are aligned. In addition, the pinion shaft 7 and the swing 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 oscillating disk 6 are located concentrically. The gear ratio i at this time is infinite (∞).

  As shown in FIG. 2, the eccentric mechanism 4, the connecting rod 15, and the swing link 18 of the present embodiment constitute a four-bar linkage mechanism 20. The continuously variable transmission 1 of this embodiment includes a total of six four-bar linkage 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 the phase amount R1 while changing the phase by 60 degrees. On the basis of the above, the pushing to the output shaft 3 side and the pulling to the input shaft 2 side are repeated alternately between the input shaft 2 and the output shaft 3.

  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 eccentric mechanism 4 is arranged with a phase changed every 60 degrees, the output shaft 3 is rotated in turn by each eccentric 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). The swing range θ2 of the swing link 18 with respect to the rotational movement of the eccentric mechanism 4 is shown. As is clear from FIG. 4, as the amount of eccentricity R1 decreases, the swing range θ2 of the swing link 18 decreases. When the eccentric amount R1 is “0”, the swing link 18 does not swing. In the present embodiment, the position closest to the input shaft 2 in the swing range θ2 of the swing end 18a of the swing link 18 is the internal dead center, and the position farthest from the input shaft 2 is the external dead center. .

  FIG. 5 shows the relationship of the change in the angular velocity ω accompanying the change in the eccentric amount R1 of the eccentric mechanism 4 with the rotational angle θ1 of the eccentric mechanism 4 of the continuously variable transmission 1 as the horizontal axis and the angular velocity ω of the swing link 11 as the vertical axis. Indicates. As is clear from FIG. 5, it can be seen that the angular velocity ω of the swing link 11 increases as the eccentric amount R1 increases (the transmission ratio i decreases).

  FIG. 6 shows the rotation angle θ1 of the eccentric mechanism 4 when the six eccentric mechanisms 4 having phases different 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 is shown. From FIG. 6, it can be seen that the output shaft 3 is smoothly rotated by the six four-bar linkage mechanisms 20.

  Referring to FIG. 7, the receiving hole 6a of the oscillating disk 6 is located at the center in the axial direction so as to sandwich the small-diameter small-diameter hole 6c and the small-diameter hole 6c from the axial direction, and has a larger diameter than the small-diameter hole 6c. And a pair of large-diameter holes 6d. A step portion 6e is formed between the small diameter hole 6c and the large diameter hole 6d due to the difference in diameter. On the large diameter hole 6d side of the stepped portion 6e, a cutout portion 6f cut out in the axial direction is provided. The inner teeth 6b are provided on the inner peripheral surface of the small diameter hole 6c.

  A roller bearing 21 for an eccentric mechanism is provided between the outer peripheral surface of the fixed disk 5 and the inner peripheral surface of the large-diameter hole 6d. As shown in FIG. 8, the roller bearing 21 includes a plurality of rolling elements 22 formed of cylindrical “rollers”, a cage 23 that holds the plurality of rolling elements 22 at intervals, an outer ring 24, Consists of.

  On the periphery of the outer ring 24 on the side of the stepped portion 6e, an overhanging portion 24a is provided that projects inwardly in the radial direction so as to be positioned between the notch 6f of the stepped portion 6e and the fixed disk 5. The overhanging portion 24a is sandwiched between the fixed disk 5 and the cutout hole 6f, thereby preventing the roller bearing 21 from falling off. Accordingly, it is not necessary to separately provide a stopper or the like for removing the roller bearing 21 for the eccentric mechanism, and it is possible to prevent an increase in the number of manufacturing steps and the number of parts of the four-bar link type continuously variable transmission 1.

  Further, a side wall 24 b that is bent so as to be spaced from the outer peripheral surface of the fixed disk 5 is provided on the periphery of the outer ring 24 on the side opposite to the stepped portion 6 e. Thus, since the inner peripheral edge of the side wall 24b is spaced from the outer peripheral surface of the fixed disk 5, the roller bearing 21 can take in the lubricating oil scattered in the transmission case. Further, the lubricating oil taken into the interior passes between the stepped portion 6e and the fixed disk 5 and is supplied to the small diameter hole 6c. Thereby, the continuously variable transmission 1 can be appropriately lubricated and cooled.

  FIG. 9 schematically shows a radial cross section of the roller bearing 21. As is apparent from FIG. 9, the rolling elements 22 of the roller bearing 21 are arranged at different intervals in the circumferential direction, whereby the rotational center of gravity of the roller bearing 21 is shifted from the center. In a four-bar link continuously variable transmission, in general, the fixed disk and the oscillating disk rotate at the same speed unless the transmission ratio is changed. There is a feature that fine wear (fretting) is likely to occur. By shifting the rotational center of gravity of the roller bearing 21 as described above, the cage 23 can be rotated relative to the outer ring 24 by the moment of inertia, and fretting of the roller bearing 21 can be prevented.

  In this embodiment, the roller bearing 21 that does not include the inner ring is described as the eccentric mechanism bearing. However, the eccentric mechanism bearing of the present invention may include the inner ring. In this case, an overhang portion may be provided on the inner ring. At this time, the outer ring of the eccentric mechanism bearing may be omitted.

  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, 1a ... Transmission case, 2 ... Input shaft, 2a ... Notch hole, 2b ... Input shaft bearing, 3 ... Output shaft, 4 ... Eccentric mechanism, 5 ... Fixed disk, 6 ... Swing disk 6a ... receiving hole, 6b ... internal tooth, 6c ... small diameter hole, 6d ... large diameter hole, 6e ... stepped portion, 6f ... notch, 7 ... pinion shaft, 7a ... external teeth, 8 ... differential mechanism (planetary gear) 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 ... drive source (motor), 14a ... rotating shaft, 15 ... connecting rod, 15a ... large diameter annular portion, 15b ... small diameter annular portion, 15c ... lubricating oil hole, 16 ... roller bearing for connecting rod, 17 ... one-way clutch (one-way rotation prevention mechanism) , 18 ... Swing link, 18a Oscillating end, 18b ... projecting piece, 18c ... through hole, 19 ... connecting pin, 20 ... four-bar linkage mechanism, 21 ... roller bearing for eccentric mechanism, 22 ... rolling element, 23 ... retainer, 24 ... outer ring, 24a ... Overhang, 24b ... Side wall, P1 ... Input center axis, P2 ... Center point of fixed disk, P3 ... Center point of rocking disk, Ra ... Distance between P1 and P2, Rb ... Distance between P2 and P3, R1 ... Eccentricity (distance between P1 and P3), .theta.1 ... rotational angle of the eccentric mechanism, .theta.2 ... oscillation range, .omega .... angular velocity of the oscillating link.

Claims (2)

A hollow input shaft to which a driving force from a driving source of the vehicle is transmitted;
An output shaft arranged parallel to the input shaft;
A plurality of eccentric mechanisms including a fixed disk provided eccentrically with respect to the input shaft, and a swinging disk provided eccentrically with respect to the fixed disk and rotatably provided;
A plurality of swing links pivotally supported by the output shaft;
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
A connecting rod having a large-diameter annular portion that is rotatably fitted to the eccentric mechanism at one end, and the other end connected to the swing end of the swing link;
A pinion shaft inserted into the input shaft,
In the input shaft, a notch hole is formed at a location facing the eccentric direction of the fixed disk, and the pinion shaft is exposed from the notch hole,
The swing disk is provided with a receiving hole for receiving the input shaft and the fixed disk,
Inner teeth are formed on the inner peripheral surface of the rocking disk that forms the receiving hole,
The inner teeth mesh with the pinion shaft exposed from the notch hole of the input shaft,
The eccentric amount of the eccentric mechanism is maintained by rotating the input shaft and the pinion shaft at the same speed, and the eccentric amount of the eccentric mechanism is changed by changing the rotational speeds of the input shaft and the pinion shaft. A continuously variable transmission that controls the gear ratio,
The receiving hole is composed of a small-diameter hole located in the center in the axial direction and formed with the internal teeth, and a large-diameter hole having a larger diameter than the small-diameter hole arranged so as to sandwich the small-diameter hole in the axial direction. And
A step is formed between the small diameter hole and the large diameter hole,
Between the outer peripheral surface of the fixed disk and the inner peripheral surface of the large-diameter hole, an eccentric mechanism bearing is disposed,
The eccentric mechanism bearing includes a plurality of rolling elements, a cage that holds the plurality of rolling elements, and an outer ring or an inner ring,
A four-bar link type continuously variable transmission characterized in that the outer ring or the inner ring is provided with an overhanging part that projects between the step part and the fixed disk. The four-bar link continuously variable transmission according to claim 1,
The eccentric mechanism bearing includes the outer ring,
The overhang portion is provided on the outer ring,
A side wall extending inward in the radial direction is provided on the peripheral edge of the outer ring opposite to the side on which the protruding portion is provided,
The four-bar ring continuously variable transmission characterized in that the side wall is configured such that the inner peripheral edge thereof is spaced from the outer peripheral surface of the fixed disk.

Images