JP5822594B2 - Four-bar linkage type continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission with a four-bar link mechanism that can change speed by adjusting the amount of eccentricity with 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, A plurality of swing links pivotally supported on the output shaft, an input shaft side annular portion rotatably fitted on an eccentric mechanism at one end portion, and the other end portion being a swing link There is known a four-bar linkage mechanism type continuously variable transmission including a connecting rod connected to a swing end portion of the sway (see, for example, Patent Document 1).

  In Patent Document 1, each eccentric mechanism is composed of a cam disk provided eccentrically on the input shaft, and a rotating disk provided eccentrically on the cam 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 cam disk, and the pinion shaft is exposed from the notch hole. The rotating disk is provided with a receiving hole for receiving the input shaft and the cam disk. Internal teeth are formed on the inner peripheral surface of the rotating 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 input shaft side 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. To do. That is, a lever crank mechanism is constituted by the eccentric mechanism, the connecting rod, and the swing link. 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 cam 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

  In the conventional four-bar linkage type continuously variable transmission, the camshaft composed of the cam disk and the input shaft is integrally molded with one member to obtain high rigidity, but let's configure the camshaft with one member. Then, since the structure of a camshaft is complicated, it is necessary to shape | mold by machining. However, the machining process has a problem that mass production is low while precise machining accuracy can be obtained.

  Therefore, the inventor of the present application molded each cam disk and the input shaft separately, and fixed each cam disk to the input shaft, so that the cam disk could be formed by a casting method, and the four-bar link improved in mass productivity. A mechanical type continuously variable transmission was invented.

  By the way, the input shaft of the four-bar linkage mechanism type continuously variable transmission is easily bent because a large load is applied from the connecting rod through the eccentric mechanism. Since the four-bar link mechanism type continuously variable transmission changes the gear ratio by adjusting the amount of eccentricity of the eccentric mechanism, the accuracy of adjusting the gear ratio decreases when the input shaft is bent. In order to solve this problem, it is conceivable to increase the rigidity of the input shaft by increasing the diameter of the input shaft, but there is a limit to fit the transmission in a limited space of the vehicle.

  In view of the above points, the present invention has an object to provide a four-bar linkage mechanism continuously variable transmission that can suppress the deflection of the input shaft while maintaining the diameter of the input shaft without reducing mass productivity. To do.

[1] In order to achieve the above object, the present invention provides a hollow input shaft to which a driving force from a driving source is transmitted, an output shaft arranged parallel to the input shaft, and a shaft eccentric to the input shaft. A plurality of eccentric mechanisms each having a cam disk that is supported and fixed so as to rotate integrally with the input shaft, and a rotating disk that is eccentrically rotated relative to the cam disk; and the output shaft A plurality of oscillating links that are pivotally supported on the output shaft, and provided between the oscillating link and the output shaft, and when the output shaft is to rotate relative to the output shaft to one side, the output shaft The oscillating link is fixed to the other side and the oscillating link is idled with respect to the output shaft when the oscillating link is rotated relative to the other side, and the eccentric mechanism is rotatable at one end. Has an input shaft-side annular portion that is externally fitted to the other end. Comprises a connecting rod connected to the swing end of the swing link, and a pinion shaft inserted into the input shaft, and the input shaft is notched at a location facing the eccentric direction of the cam disk. A hole is formed, the pinion shaft is exposed from the notch hole, and the rotating disk is provided with a receiving hole for receiving the input shaft and the cam disk, and the inner peripheral surface of the rotating disk that forms the receiving hole An inner tooth is formed on the shaft, and the inner tooth meshes with the pinion shaft exposed from the notch hole of the input shaft, and rotates the input shaft and the pinion shaft at the same speed, thereby decentering the eccentric mechanism. The four-position link which controls the transmission ratio by changing the eccentric amount of the eccentric mechanism by changing the rotational speed of the input shaft and the pinion shaft. A mechanism type continuously variable transmission, wherein the eccentric mechanism comprises a plurality of cam disc of the same phase, a plurality of the cam disc of each eccentric mechanism is connected by a connecting member, by the coupling member adjacent the The cam disks of the eccentric mechanism are connected to each other.

When each cam disk is fixed by the input shaft, when the input shaft is bent, the interval between the cam disks is widened. According to the four-bar linkage mechanism type continuously variable transmission of the present invention, the cam disks of the adjacent eccentric mechanisms are connected to each other, so that the interval between the cam disks can be prevented from widening. Therefore, the input shaft is difficult to bend, and the cam disk and the input shaft are formed as a single member as in the prior art, and the input shaft is maintained without increasing the diameter of the input shaft without decreasing the mass productivity. Deflection can be suppressed.
Further, in the four-bar linkage type continuously variable transmission of the present invention, each eccentric mechanism includes a plurality of cam disks having the same phase, and the plurality of cam disks of the eccentric mechanism are connected by a connecting member, and using this connecting member, The cam disks of adjacent eccentric mechanisms are connected to each other. According to this, it is not necessary to separately provide a new member for connecting the cam disks of the adjacent eccentric mechanisms, and the number of parts can be reduced and the cost can be reduced.

  [2] In the present invention, cam disks can be arranged on the input shaft so that the phases of adjacent cam disks are closest to each other. If comprised in this way, the area | region where adjacent cam disks overlap will increase, and it will become easy to connect adjacent cam disks with a volt | bolt etc.

  Further, when the cam disks of the adjacent eccentric mechanisms are fixed with bolts, holes for inserting the bolts can be formed at the same position in all the cam disks. Therefore, there is no need to change the position of the hole for the bolt of the cam disk in accordance with the position of the cam disk on the input shaft, and the manufacture of the four-bar linkage mechanism type continuously variable transmission can be simplified.

[3] In the present invention, it constitutes a consolidated member with a long bolt, a plurality of cam disks eccentric mechanism located on the most axial end side of the input shaft of the plurality of eccentric, shorter short bolts than the long bolts It can be constituted so that it may be connected also by.

Sectional drawing which shows embodiment of the four-bar linkage mechanism type continuously variable transmission of this invention. The perspective view which decomposes | disassembles and shows the input shaft, pinion shaft, and eccentric mechanism of this embodiment. Sectional drawing which shows typically the input shaft and cam disk of this embodiment. 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. 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.

  Embodiments of a four-bar linkage type 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 to 4, a continuously variable transmission 1 according to the present embodiment receives an input central axis P1 (by receiving rotational power from a drive source for a vehicle such as an engine or an electric motor, which is an internal combustion engine not shown). (See FIG. 4) A hollow input shaft 2 that rotates around the center of the input shaft 2 and the input shaft 2 are arranged in parallel, and the rotational power is transmitted to the drive wheels (not shown) of the vehicle via a differential gear, a propeller shaft, etc., not shown. An output shaft 3 to be operated, and six eccentric mechanisms 4 provided on the input shaft 2.

  Each eccentric mechanism 4 includes a cam disk 5 and a rotating disk 6 that are separate from the input shaft 2. The cam disks 5 are disk-shaped, and are fixed to the input shaft 2 in pairs by spline coupling so as to be eccentric from the input center axis P1 and rotate integrally with the input shaft 2. One set of cam disks 5 of each eccentric mechanism 4 is arranged so that the phases thereof are sequentially changed by 60 degrees so that the six sets of cam disks 5 make a round in the circumferential direction of the input shaft 2.

  The input shaft 2 is provided with a plurality of spline teeth 2c (see FIG. 2) for fixing the cam disks 5 in correspondence with the cam disks 5. All the spline teeth 2c are formed in the same phase, and the number of teeth is set to a multiple of the number of the eccentric mechanisms 4 (that is, a multiple of 6). Thereby, the shape of each cam disk 5 including the spline teeth of the cam disk 5 coupled with the spline teeth 2c of the input shaft 2 can be formed identically. Fixing and positioning are easy.

  As shown in FIGS. 2 and 3, each set of cam disks 5 has two sets of adjacent cam disks 5 fixed by a long bolt 5a. That is, each set of the cam disks 5 other than the two sets of cam disks 5 positioned at both ends in the axial direction is fixed by the two long bolts 5a. Two sets of cam disks positioned at both ends in the axial direction are fixed by one long bolt 5a and one short bolt 5b, respectively. With this configuration, there is no need to separately provide bolts for connecting the cam disks 5 of the adjacent eccentric mechanisms 4, and the number of parts can be reduced to reduce costs. In the present embodiment, the input shaft 2 and the six sets of cam disks 5 constitute a camshaft.

  Further, each set of cam disks 5 has a disk-shaped rotating disk 6 provided with a receiving hole 6a for receiving the cam disk 5 and is rotatable with respect to the cam disk 5 via an eccentric mechanism bearing 4a. It is fitted. 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. 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.

  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 arranged concentrically with the input shaft 2 and has external teeth 7 a at positions corresponding to the internal teeth 6 b of the rotary disk 6 is rotatable relative to the input shaft 2. Has been placed. 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.

  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 14 a of an actuator 14 that is an electric motor for the pinion shaft 7. When the rotational speed of the actuator 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, the second ring gear 11, and the like. The four elements of 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 actuator 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 the 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 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. 4, 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.

  On the periphery of the rotary disk 6, an input shaft side annular portion 15a having a large diameter is provided at one end, and an output shaft side annular portion 15b having a smaller diameter than the diameter of the input shaft side annular portion 15a is provided at the other end. An input shaft side annular portion 15a of the connecting rod 15 is rotatably fitted through a roller bearing 16 for the connecting rod. 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 output shaft side 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 output shaft side annular portion 15b in the axial direction. A through hole 18c corresponding to the inner diameter of the output shaft side annular portion 15b is formed in the pair of projecting pieces 18b. A connecting pin 19 is inserted into the through hole 18c and the output shaft side annular portion 15b. Thereby, the connecting rod 15 and the swing link 18 are connected.

  FIG. 5 shows the positional relationship between the pinion shaft 7 and the rotating disk 6 in a state where the eccentric amount R1 of the eccentric mechanism 4 is changed. FIG. 5A 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. 5B shows a state where the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 5A, and FIG. 5C shows 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. 5A in FIG. 5B, and “large” which is larger than the gear ratio i in FIG. 5B in FIG. Become. FIG. 5D 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 (∞).

  As shown in FIG. 4, the eccentric mechanism 4, the connecting rod 15, and the swing link 18 of the present embodiment constitute a lever crank mechanism 20. 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 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 output shaft side 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. When swinging, the output shaft 3 rotates only when the swing link 18 rotates in either the pushing direction side or the pulling direction side, and when the swing link 18 rotates in the other direction, output is performed. The force of the oscillating motion of the oscillating link 18 is not transmitted to the shaft 3, and the oscillating link 18 rotates idle. 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.

  6A shows the case where the eccentric amount R1 is “maximum” in FIG. 5A (when the gear ratio i is the minimum), and FIG. 6B shows the case where the eccentric amount R1 is “ FIG. 6C shows the case where the eccentric amount R1 is “small” in FIG. 5C (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 apparent from FIG. 6, as the amount of eccentricity R1 becomes smaller, the swing range θ2 of the swing link 18 becomes narrower. 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. 7 shows the relationship between changes in the angular velocity ω accompanying changes in the amount of eccentricity 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 apparent from FIG. 7, 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. 8 shows each swing link with respect to the rotation angle θ1 of the eccentric mechanism 4 when the six eccentric mechanisms 4 having phases different by 60 degrees are rotated at the same speed of the input shaft 2 and the pinion shaft 7. An angular velocity ω of 18 is shown. FIG. 8 shows that the output shaft 3 is smoothly rotated by the six lever crank mechanisms 20.

  According to the four-bar linkage type continuously variable transmission of the present embodiment, the cam disks 5 of the eccentric mechanisms 4 are fixed to the input shaft 2, so that each cam disk 5 can be aligned with the input shaft 2. it can. In addition, since each cam disk 5 is connected by the input shaft 2, when changing the phase angle of each cam disk 5, it is not necessary to change the mold for forming the cam disk 5, and a set of adjacent ones. It is only necessary to change the drilling positions of the holes for the bolts 5a and 5b between the cam disks 5. For this reason, the phase angle can be changed relatively easily. Therefore, the cam disk 5 and the input shaft 2 can be manufactured with high accuracy, and the degree of freedom in layout of the four-bar linkage mechanism continuously variable transmission 1 can be increased.

  By the way, in general, the input shaft of the four-bar linkage mechanism type continuously variable transmission is easily bent because a large load is applied from the connecting rod through the eccentric mechanism. Since the four-bar link mechanism type continuously variable transmission changes the gear ratio by adjusting the amount of eccentricity of the eccentric mechanism, the accuracy of adjusting the gear ratio decreases when the input shaft is bent.

  According to the four-bar linkage mechanism continuously variable transmission 1 of the present embodiment, adjacent cam disks 5 are connected to each other with different phases. When the input shaft 2 bends, each pair of cam disks 5 tends to open, but since the adjacent pair of cam disks 5 of the present embodiment are connected to each other, each pair of cam disks 5 Opening between the disks 5 is prevented. Therefore, the input shaft 2 becomes difficult to bend, and the deflection of the input shaft 2 can be suppressed while maintaining the diameter without making the input shaft 2 large.

  Each set of cam disks 5 is arranged on the input shaft 2 so that the phase difference between the adjacent sets of cam disks 5 is reduced. For this reason, the overlapping region between adjacent sets of cam disks 5 increases, and it becomes easy to make a hole for inserting a long bolt 5a for connecting adjacent sets of cam disks 5. Further, since the phase difference between the adjacent cam disks 5 is constant, the shape of the cam disks 5 and the positions of the holes for the bolts 5a and 5b can be configured in the same way. Easy to manufacture.

  In this 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 from the swing link 18 to the output shaft 3 is not limited. 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.

  In the present embodiment, the transmission is used for a vehicle such as an automobile. However, the four-bar link mechanism type continuously variable transmission of the present invention is not limited to this, and is used for, for example, a ship. There may be.

DESCRIPTION OF SYMBOLS 1 ... Four-bar linkage type continuously variable transmission, 2 ... Input shaft, 2a ... Notch hole, 2b ... Bearing for input shaft, 2c ... Spline tooth, 3 ... Output shaft, 4 ... Eccentric mechanism, 4a ... Bearing for eccentric mechanism 5 ... cam disc, 5a ... long bolt, 5b ... short bolt, 6 ... rotating disc, 6a ... receiving hole, 6b ... internal tooth, 7 ... pinion shaft, 7a ... external tooth, 15 ... connecting rod, 15a ... input shaft Side annular portion, 17 ... one-way clutch (one-way rotation prevention mechanism), 18 ... swing link, 18a ... swing end, 20 ... lever crank mechanism.

Claims (3)

A hollow input shaft to which the driving force from the driving source is transmitted;
An output shaft arranged parallel to the input shaft;
A plurality of cam disks that are eccentrically supported by the input shaft and fixedly provided so as to rotate integrally with the input shaft, and a rotating disk that is provided eccentrically and rotatable with respect to the cam disk. An eccentric mechanism;
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 an input shaft side annular portion rotatably fitted to the eccentric mechanism at one end, and the other end coupled 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 cam disk, and the pinion shaft is exposed from the notch hole,
The rotating disk is provided with a receiving hole for receiving the input shaft and the cam disk,
Inner teeth are formed on the inner peripheral surface of the rotating 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 four-bar linkage continuously variable transmission that controls the transmission ratio,
Each of the eccentric mechanisms includes a plurality of cam disks having the same phase,
The plurality of cam disks of each eccentric mechanism are connected by a connecting member,
A four-bar linkage type continuously variable transmission characterized in that adjacent cam disks of the eccentric mechanism are connected by the connecting member . A four-bar linkage type continuously variable transmission according to claim 1,
A four-bar linkage mechanism type continuously variable transmission, wherein the cam disks are arranged on an input shaft so that the phases of adjacent cam disks of the eccentric mechanisms are closest to each other. The four-bar linkage type continuously variable transmission according to claim 1 or 2,
The connecting member is composed of a long bolt,
Among the plurality of eccentric mechanisms, the plurality of cam disks of the eccentric mechanism located closest to the shaft end of the input shaft are connected by a short bolt shorter than the long bolt. Continuously variable transmission.