WO2013008624A1

WO2013008624A1 - Continuously variable transmission

Info

Publication number: WO2013008624A1
Application number: PCT/JP2012/066381
Authority: WO
Inventors: 優史西村; 和樹市川
Original assignee: 本田技研工業株式会社
Priority date: 2011-07-13
Filing date: 2012-06-27
Publication date: 2013-01-17
Also published as: CN103649594B; CN103649594A; JPWO2013008624A1; JP5703379B2

Abstract

In the continuously variable transmission, when an eccentric disc (19) is rotated relative to an eccentric cam (18) using a gear change shaft (15) that fits coaxially into the inside of an input shaft (12), the eccentricity (ε) of the eccentric disc (19) with respect to the input shaft (12) changes and as a result of the reciprocation stroke of the connecting rod (33) changing, the intermittent rotation angle of the output shaft changes and the gear ratio is changed. Since the center of gravity (G) of the eccentric disc (19) has been made to coincide with the center of eccentric rotation (O1), even if the eccentric disc (19) is eccentrically rotated with respect to the eccentric cam (18) in order to change the gear ratio, the distance (d) from the axis line (L) of the input shaft (12) to the center of gravity (G) of the eccentric disc (19) does not change. Therefore, even if the gear ratio is changed, the second moment of inertia of the eccentric disc (19) with respect to the axial line (L) of the input shaft (12) does not change and vibrations that accompany changes in gear ratio can be kept to a minimum.

Description

Continuously variable transmission

The present invention eccentrically rotates one end of the connecting rod by the input shaft, intermittently rotates the output shaft connected to the other end of the connecting rod via the one-way clutch, and changes the eccentric amount of the one end of the connecting rod. It is related with the continuously variable transmission which changes a gear ratio by making it.

Such a continuously variable transmission is known from Patent Document 1 below. In this continuously variable transmission, a disk-shaped eccentric cam is fixed to the input shaft in an eccentric state, and a disk-shaped eccentric disk is supported on the outer periphery of the eccentric cam so as to be relatively rotatable in an eccentric state. By rotating the eccentric disk relative to the eccentric cam with the transmission shaft arranged inside, the eccentric ratio of the eccentric disk with respect to the axis of the input shaft is changed to change the gear ratio.

German publication 102009039993

By the way, in the conventional continuously variable transmission, when the eccentric disk rotates relative to the eccentric cam integral with the input shaft in accordance with the change of the gear ratio, the distance between the axis of the input shaft and the center of gravity position of the eccentric disk increases or decreases. Therefore, the inertial moment of inertia of the eccentric disk around the input shaft changes according to the increase or decrease of the distance, and as a result, the rotational load of the input shaft may fluctuate and vibration may occur.

The present invention has been made in view of the above-described circumstances, and an object of the present invention is to minimize the occurrence of vibration associated with the change in the amount of eccentricity of an eccentric disk of a continuously variable transmission.

In order to achieve the above object, according to the present invention, an eccentric cam fixed in an eccentric state on the outer periphery of an input shaft connected to a drive source, and an eccentric cam that supports relative rotation in an eccentric state are supported. An eccentric disc, a transmission shaft that is coaxially fitted inside the input shaft and rotates the eccentric disc with respect to the eccentric cam, a one-way clutch provided on the outer periphery of the output shaft, and the eccentric disc And a connecting rod which is connected to both ends of the one-way clutch and reciprocates, and the rotation of the input shaft is intermittently transmitted to the output shaft via the connecting rod and the one-way clutch, and the transmission shaft A continuously variable transmission for changing a gear ratio by changing an amount of eccentricity of the eccentric disk with respect to an axis of the input shaft, wherein the eccentric disk The center of gravity position, a continuously variable transmission according to the first, characterized in that fitted to the eccentric center of rotation relative to the eccentric cam of the eccentric disk is proposed.

Further, according to the present invention, in addition to the first feature, a continuously variable transmission is proposed in which the transmission shaft is driven by a transmission actuator.

According to the present invention, in addition to the first or second feature, the eccentric disk is thinned so that the position of the center of gravity of the eccentric disk coincides with the eccentric rotation center of the eccentric disk with respect to the eccentric cam. A continuously variable transmission having a third feature is provided.

Further, according to the invention, in addition to any one of the first to third features, the eccentric disk is configured so that a center of gravity position of the eccentric disk coincides with an eccentric rotation center of the eccentric disk with respect to the eccentric cam. A continuously variable transmission having a fourth feature of providing a weight on the disk is proposed.

The engine E of the embodiment corresponds to the drive source of the present invention, the center O1 of the eccentric cam of the embodiment corresponds to the eccentric rotation center of the present invention, and the lightening recess 19c of the embodiment corresponds to the present invention. Corresponds to the meat removal part.

According to the first feature of the present invention, when the input shaft connected to the drive source rotates, the eccentric cam fixed in the eccentric state on the outer periphery of the input shaft rotates eccentrically, and in the eccentric state on the outer periphery of the eccentric cam. The supported eccentric disk rotates eccentrically. When the connecting rod connected at one end to the eccentric disk reciprocates, the output shaft rotates intermittently via a one-way clutch connected at the other end of the connecting rod. When the eccentric disk is rotated relative to the eccentric cam with the transmission shaft coaxially fitted inside the input shaft, the eccentric amount of the eccentric disk with respect to the input shaft changes, and the reciprocating stroke of the connecting rod changes. The gear ratio is changed by changing the intermittent rotation angle of the shaft.

Since the center of gravity of the eccentric disk is aligned with the center of eccentric rotation, even if the eccentric disk is eccentrically rotated with respect to the eccentric cam in order to change the gear ratio, the distance from the axis of the input shaft to the center of gravity of the eccentric disk is There is no change. Therefore, even if the gear ratio is changed, the inertial moment of inertia of the eccentric disk with respect to the axis of the input shaft does not change, and the occurrence of vibration associated with the change of the gear ratio can be minimized.

According to the second feature of the present invention, the center of gravity of the eccentric disk is made coincident with the center of eccentric rotation, so that the moment for rotating the eccentric disk relative to the eccentric cam even if an inertial force acts on the eccentric disk. Will not occur. Therefore, the moment is not transmitted back to the transmission actuator from the eccentric disk via the transmission shaft to the transmission actuator that drives the transmission shaft, and the control accuracy of the transmission actuator is improved.

According to the third feature of the present invention, since the eccentric disk is provided with the thinning portion so that the center of gravity of the eccentric disk coincides with the eccentric rotation center of the eccentric disk with respect to the eccentric cam, the eccentric disk has a simple structure. Can be adjusted.

According to the fourth aspect of the present invention, since the weight of the eccentric disk is provided in order to make the position of the center of gravity of the eccentric disk coincide with the center of eccentric rotation with respect to the eccentric cam of the eccentric disk, the center of gravity of the eccentric disk has a simple structure. The position can be adjusted.

FIG. 1 is an overall view of a continuously variable transmission. (First embodiment) FIG. 2 is a partially broken perspective view of a main part of the continuously variable transmission. (First embodiment) 3 is a cross-sectional view taken along line 3-3 of FIG. (First embodiment) FIG. 4 is an enlarged view of part 4 of FIG. (First embodiment) 5 is a cross-sectional view taken along line 5-5 of FIG. (First embodiment) FIG. 6 is a diagram showing the shape of the eccentric disk. (First embodiment) FIG. 7 is a diagram showing the relationship between the amount of eccentricity of the eccentric disk and the gear ratio. (First embodiment) FIG. 8 is a diagram showing the relationship between the amount of eccentricity of the eccentric disk and the locus of the center of gravity. (First embodiment) FIG. 9 corresponds to FIG. (Second Embodiment)

12 Input shaft 13 Output shaft 15 Transmission shaft 18 Eccentric cam 19 Eccentric disk 19c Thinning recess (thickening portion)
19e Weight 23 Variable speed actuator 33 Connecting rod 36 One-way clutch E Engine (drive source)
G Center of gravity of eccentric disk L Input shaft axis O1 Center of eccentric cam (center of eccentric rotation)
ε Eccentric disc eccentricity

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

First embodiment

First, a first embodiment of the present invention will be described with reference to FIGS.

As shown in FIGS. 1 to 5, a transmission case 11 of a continuously variable transmission T for an automobile includes a frame 51 having a frame main body 51a and a pair of first and

second side walls

51b and 51c and an upper surface being opened. The upper cover 52 and the lower cover 53 are divided into two parts covering the periphery of the frame 51. The input shaft 12 and the output shaft 13 are supported in parallel to each other on the first and

second side walls

51b and 51c of the transmission case 11, and the rotation of the input shaft 12 connected to the engine E is six transmission units 14 and It is transmitted to the drive wheel via the output shaft 13. A variable speed shaft 15 sharing an axis L with the input shaft 12 is fitted into the hollow formed input shaft 12 via seven needle bearings 16 so as to be relatively rotatable. Since the structure of the six transmission units 14 is substantially the same, the structure will be described below with one transmission unit 14 as a representative.

The transmission unit 14 includes a pinion 17 provided on the outer peripheral surface of the transmission shaft 15, and the pinion 17 is exposed from an opening 12 a formed in the input shaft 12. A disc-shaped eccentric cam 18 divided into two in the direction of the axis L is splined to the outer periphery of the input shaft 12 so as to sandwich the pinion 17. The center O1 of the eccentric cam 18 is eccentric with respect to the axis L of the input shaft 12 by a distance d. Further, the six eccentric cams 18 of the six transmission units 14 are offset in phase by 60 ° from each other.

On the outer peripheral surface of the eccentric cam 18, a pair of

eccentric recesses

19 a and 19 a formed on both end surfaces in the axis L direction of the disc-shaped eccentric disk 19 are rotatably supported via a pair of

needle bearings

20 and 20. . The center O1 of the

eccentric recesses

19a, 19a (that is, the center O1 of the eccentric cam 18) is shifted from the center O2 of the eccentric disk 19 by a distance d. That is, the distance d between the axis L of the input shaft 12 and the center O1 of the eccentric cam 18 and the distance d between the center O1 of the eccentric cam 18 and the center O2 of the eccentric disk 19 are the same.

A pair of crescent-

shaped guide portions

18a and 18a are provided on the split surface of the eccentric cam 18 divided into two in the direction of the axis L so as to be coaxial with the center O1 of the eccentric cam 18. The tooth tips of the ring gear 19b formed so as to communicate between the bottoms of the

recesses

19a and 19a slidably contact the outer peripheral surfaces of the

guide portions

18a and 18a of the eccentric cam 18. Then, the pinion 17 of the transmission shaft 15 meshes with the ring gear 19b of the eccentric disk 19 through the opening 12a of the input shaft 12.

The one end side of the input shaft 12 is directly supported by the first side wall 51b of the mission case 11 via the ball bearing 21. Further, a cylindrical portion 18b provided integrally with one eccentric cam 18 positioned on the other end side of the input shaft 12 is supported by the second side wall 51c of the transmission case 11 via the ball bearing 22, and the eccentricity thereof. The other end side of the input shaft 12 splined to the inner periphery of the cam 18 is indirectly supported by the mission case 11.

The speed change actuator 23 that changes the speed ratio of the continuously variable transmission T by rotating the speed change shaft 15 relative to the input shaft 12 is a side cover 42 of the transmission case 11 so that the motor shaft 24a is coaxial with the axis L. And an planetary gear mechanism 25 connected to the electric motor 24. The planetary gear mechanism 25 includes a carrier 27 that is rotatably supported by an electric motor 24 via a needle bearing 26, a sun gear 28 that is fixed to the motor shaft 24a, and a plurality of two stations that are rotatably supported by the carrier 27. A pinion 29, a first ring gear 30 splined to the shaft end of the hollow input shaft 12 (strictly speaking, the cylindrical portion 18b of the one eccentric cam 18), and a spline to the shaft end of the transmission shaft 15 And a second ring gear 31 coupled thereto. Each double pinion 29 includes a first pinion 29a having a large diameter and a second pinion 29b having a small diameter. The first pinion 29a meshes with the sun gear 28 and the first ring gear 30, and the second pinion 29b has a second ring gear. Mesh with 31.

On the outer periphery of the eccentric disk 19, an annular portion 33a on one end side of the connecting rod 33 is supported via a roller bearing 32 so as to be relatively rotatable.

The output shaft 13 is supported on the first and

second side walls

51b and 51c of the mission case 11 by a pair of

ball bearings

34 and 35, and a one-way clutch 36 is provided on the outer periphery thereof. The one-way clutch 36 includes a ring-shaped outer member 38 pivotally supported at the tip of the rod portion 33b of the connecting rod 33 via a pin 37, and an inner member disposed inside the outer member 38 and fixed to the output shaft 13. 39 and a plurality of rollers 41 arranged in a wedge-shaped space formed between the inner circular arc surface of the outer member 38 and the outer peripheral plane of the inner member 39 and biased by a plurality of springs 40. … And.

As shown in FIG. 6, since the center O1 of the

eccentric recesses

19a and 19a (that is, the center O1 of the eccentric cam 18) is shifted by a distance d with respect to the center O2 of the eccentric disc 19, the outer periphery of the eccentric disc 19 and the eccentric recess The space | interval with the inner periphery of 19a and 19a is non-uniform | heterogenous in the circumferential direction, and the crescent-shaped thinning recessed

parts

19c and 19c are formed in the part with the large space | interval. The thinning

recesses

19c, 19c are formed so as to face each other on both sides of the eccentric disk 19 with the thin bottom wall 19d interposed therebetween. The thinning recess 19c may be formed so as to penetrate the eccentric disk 19 in the thickness direction.

If there are no hollowing

recesses

19c, 19c, the center of gravity G of the eccentric disk 19 exists in the vicinity of the center O2, but the center of gravity of the eccentric disk 19 is formed by forming the hollowing recesses 19c, 19c. The position G moves in a direction away from the thinning

recesses

19c and 19c, and in the present embodiment, is aligned with the center O1 of the

eccentric recesses

19a and 19a (that is, the center O1 of the eccentric cam 18).

Next, the operation of one transmission unit 14 of the continuously variable transmission T will be described.

As is apparent from FIGS. 5 and 7A to 7D, when the input shaft 12 is rotated by the engine E when the center O2 of the eccentric disk 19 is eccentric with respect to the axis L of the input shaft 12. As the annular portion 33a of the connecting rod 33 rotates eccentrically around the axis L, the rod portion 33b of the connecting rod 33 reciprocates. As a result, the outer member 38 of the one-way clutch 36 connected to the rod portion 33b of the connecting rod 33 by the pin 37 reciprocates within a predetermined angle range, and when the outer member 38 rotates in one direction, the rollers 41 are wedge-shaped. The rotation is transmitted to the inner member 39 by biting into the space, and when the outer member 38 rotates in the other direction, the rollers 41 slip and the transmission of the rotation to the inner member 39 is blocked.

Thus, since the rotation of the input shaft 12 is transmitted to the output shaft 13 for a predetermined time while the input shaft 12 makes one rotation, the output shaft 13 rotates intermittently when the input shaft 12 rotates continuously. Since the eccentric disks 19 of the six transmission units 14 are out of phase with each other by 60 °, the six transmission units 14 alternately transmit the rotation of the input shaft 12 to the output shaft 13. Thus, the output shaft 13 rotates continuously.

At this time, as the eccentric amount ε of the eccentric disk 19 increases, the reciprocating stroke of the connecting rod 33 increases, and the rotation angle of the output shaft 13 increases one time, and the transmission ratio of the continuously variable transmission T decreases. Conversely, the smaller the eccentric amount ε of the eccentric disk 19, the smaller the reciprocating stroke of the connecting rod 33, the smaller the rotation angle of the output shaft 13, and the higher the gear ratio of the continuously variable transmission T. When the eccentric amount ε of the eccentric disk 19 becomes zero, the connecting rod 33 stops moving even when the input shaft 12 rotates, so the output shaft 13 does not rotate, and the gear ratio of the continuously variable transmission T is maximized ( Infinity).

When the transmission shaft 15 does not rotate relative to the input shaft 12, that is, when the input shaft 12 and the transmission shaft 15 rotate at the same speed, the transmission ratio of the continuously variable transmission T is maintained constant. In order to rotate the input shaft 12 and the transmission shaft 15 at the same speed, the electric motor 24 may be rotationally driven at the same speed as the input shaft 12. The reason is that the first ring gear 30 of the planetary gear mechanism 25 is connected to the input shaft 12 and rotates at the same speed as the input shaft 12, but when the electric motor 24 is driven at the same speed, the sun gear 28 and the first ring gear 30. Rotate at the same speed, the planetary gear mechanism 25 is locked and rotates as a whole. As a result, the input shaft 12 and the transmission shaft 15 connected to the first ring gear 30 and the second ring gear 31 that rotate integrally are integrated and rotate at the same speed without relative rotation.

When the rotational speed of the electric motor 24 is increased or decreased with respect to the rotational speed of the input shaft 12, the first ring gear 30 coupled to the input shaft 12 and the sun gear 28 connected to the electric motor 24 rotate relative to each other. The carrier 27 rotates relative to the first ring gear 30. At this time, the gear ratio of the first ring gear 30 and the first pinion 29a meshing with each other is slightly different from the gear ratio of the second ring gear 31 and the second pinion 29b meshing with each other. And the transmission shaft 15 connected to the second ring gear 31 rotate relative to each other.

When the transmission shaft 15 rotates relative to the input shaft 12 in this manner, the

eccentric recesses

19 a and 19 a of the eccentric disk 19 in which the ring gear 19 b is engaged with the pinion 17 of each transmission unit 14 are integrated with the input shaft 12. The cam 18 rotates while being guided by the

guide portions

18a, 18a, and the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 changes.

FIG. 7A shows a state where the speed ratio is minimum (speed ratio: TD). At this time, the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 is the axis L of the input shaft 12. To a center O1 of the eccentric cam 18 and a maximum value equal to 2d, which is the sum of the distance d from the center O1 of the eccentric cam 18 to the center O2 of the eccentric disk 19. When the transmission shaft 15 rotates relative to the input shaft 12, the eccentric disk 19 rotates relative to the eccentric cam 18 integral with the input shaft 12, as shown in FIGS. 7B and 7C. Furthermore, the amount of eccentricity ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 gradually decreases from the maximum value 2d, and the gear ratio increases. When the transmission shaft 15 further rotates relative to the input shaft 12, the eccentric disk 19 further rotates relative to the eccentric cam 18 integrated with the input shaft 12, and finally, as shown in FIG. The center O2 of the eccentric disk 19 overlaps the axis L of the input shaft 12, the eccentricity ε becomes zero, the transmission gear ratio is maximized (infinite) (transmission ratio: UD), and power is transmitted to the output shaft 13. Blocked.

FIG. 8A shows the state of the minimum speed ratio (speed ratio: TD) in which the amount of eccentricity ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 reaches the maximum value 2d. The eccentric direction of the center O1 of the eccentric cam 18 with respect to the axis L (upward in the figure) and the eccentric direction of the center O2 of the eccentric disk 19 with respect to the center O1 of the eccentric cam 18 (upward in the figure) are the same direction. At this time, the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 18.

FIG. 8B shows the state of the maximum gear ratio (gear ratio: UD) in which the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 is the minimum value zero. The eccentric direction of the center O1 of the eccentric cam 18 with respect to the axis L (upward in the figure) is opposite to the eccentric direction of the center O2 of the eccentric disk 19 with respect to the center O1 of the eccentric cam 18 (downward in the figure). At this time, the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 18.

That is, according to the present embodiment, since the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 18, the eccentric disk 19 is moved around the center O1 of the eccentric cam 18 with the change of the gear ratio. Even if it rotates eccentrically, the gravity center position G of the eccentric disk 19 always exists on the center O1 of the eccentric cam 18, and the distance between the axis L of the input shaft 12 and the gravity center position G of the eccentric disk 19 changes from a constant value d. Never do.

If it is assumed that the distance from the axis L of the input shaft 12 to the center of gravity G of the eccentric disk 19 changes as the speed ratio changes, the inertia moment of inertia of the eccentric disk 19 around the input shaft 12 increases the distance. Therefore, the rotation load of the input shaft 12 may fluctuate with the change of the gear ratio, and vibration may occur. However, according to the present embodiment, even if the gear ratio is changed, the inertia moment of the eccentric disk 19 around the input shaft 12 does not change, so that the vibration of the input shaft 12 can be minimized.

Since the eccentric disk 19 is supported by the eccentric cam 18 so as to be relatively rotatable, if the center of gravity G of the eccentric disk 19 does not coincide with the center O1 of the eccentric cam 18, the rotational speed of the input shaft 12 increases. Alternatively, when it decreases, the eccentric disk 19 tends to rotate relative to the eccentric cam 18 with inertial force, and the moment is transmitted from the ring gear 19b of the eccentric disk 19 to the electric motor 24 of the transmission actuator 23 via the pinion 17. Unnecessary torque may act on the electric motor 24 to reduce the accuracy of the shift control.

However, according to the present embodiment, since the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 18, even if the rotational speed of the input shaft 12 increases or decreases, the eccentric disk 19 is inertial. No moment is generated to rotate relative to the eccentric cam 18 by force, thereby preventing unnecessary torque from acting on the electric motor 24 and ensuring the accuracy of the shift control.

Second embodiment

Next, a second embodiment of the present invention will be described with reference to FIG.

In the first embodiment, the center of gravity position G of the eccentric disc 19 is made to coincide with the center O1 of the

eccentric recesses

19a, 19a by forming the

hollow recesses

19c, 19c in the eccentric disc 19. In the embodiment, a pair of

weights

19e, 19e are further provided on the side of the eccentric disc 19 opposite to the thinned

recesses

19c, 19c so that the center of gravity G of the eccentric disc 19 is located at the center O1 of the

eccentric recess

19a, 19a. Match. The reason why the

weights

19e and 19e are divided into two is to avoid the interference with the roller bearing 32 and the connecting rod 33.

According to the present embodiment, even if the center of gravity position G cannot be sufficiently moved only by forming the

hollow portions

19c and 19c, the center of gravity position G of the eccentric disk 19 is further increased by the

weights

19e and 19e. It can be moved to coincide with the center O1 of the

eccentric recesses

19a, 19a. Of course, it is also possible to eliminate the lightening recesses 19c and 19c and make the center of gravity G of the eccentric disk 19 coincide with the center O1 of the

eccentric recesses

19a and 19a only by the

weights

19e and 19e.

According to this embodiment. As in the first embodiment, the center of gravity G of the eccentric disk 19 can be adjusted with a simple structure.

Although the embodiments of the present invention have been described above, various design changes can be made without departing from the scope of the present invention.

For example, the drive source of the present invention is not limited to the engine E of the embodiment, and may be another drive source such as an electric motor.

Further, the lightening part of the present invention is not limited to the lightening recessed part 19c of the embodiment, and may be a lightening hole penetrating the eccentric disk 19.

In addition, the weight 19e of the present invention is not necessarily formed integrally with the eccentric disk 19, and may be configured by a separate member and fixed to the eccentric disk 19.

Claims

An eccentric cam (18) fixed in an eccentric state on the outer periphery of the input shaft (12) connected to the drive source (E);
An eccentric disk (19) supported on the outer periphery of the eccentric cam (18) so as to be relatively rotatable in an eccentric state;
A transmission shaft (15) that coaxially fits inside the input shaft (12) and rotates the eccentric disk (19) eccentrically with respect to the eccentric cam (18);
A one-way clutch (36) provided on the outer periphery of the output shaft (13);
A connecting rod (33) reciprocatingly connected to both ends of the eccentric disk (19) and the one-way clutch (36);
The rotation of the input shaft (12) is intermittently transmitted to the output shaft (13) through the connecting rod (33) and the one-way clutch (36), and the input shaft (15) is transmitted by the transmission shaft (15). 12) a continuously variable transmission that changes the gear ratio by changing the amount of eccentricity (ε) of the eccentric disk (19) with respect to the axis (L) of 12);
A continuously variable transmission characterized in that the center of gravity (G) of the eccentric disk (19) is made to coincide with the eccentric rotation center (O1) of the eccentric disk (19) with respect to the eccentric cam (18).
The continuously variable transmission according to claim 1, wherein the transmission shaft (15) is driven by a transmission actuator (23).
In order to make the center of gravity (G) of the eccentric disk (19) coincide with the eccentric rotation center (O1) of the eccentric disk (19) with respect to the eccentric cam (18), a hollow portion is formed on the eccentric disk (19). The continuously variable transmission according to claim 1 or 2, wherein (19c) is provided.
In order to make the center of gravity (G) of the eccentric disk (19) coincide with the eccentric rotation center (O1) of the eccentric disk (19) with respect to the eccentric cam (18), a weight (19e) is applied to the eccentric disk (19). The continuously variable transmission according to any one of claims 1 to 3, wherein a continuously variable transmission is provided.