JP6087320B2 - Continuously variable transmission - Google Patents

Description

  The present invention converts the rotational motion of the rotating portion into the swinging motion of the oscillating portion by the motion converting mechanism, transmits power through the one-way rotation prevention mechanism, and reduces the rotational radius of the rotating portion by the rotational radius adjusting mechanism. The present invention relates to a continuously variable transmission that changes speed.

  Conventionally, a cam portion coupling body as an input portion that rotates by transmitting a driving force from a driving source such as an engine provided in a vehicle, and an output shaft that is arranged in parallel with the rotation center axis of the cam portion coupling body, A plurality of turning radius adjusting mechanisms provided on the cam portion coupling body, a plurality of turning portions pivotally supported by the output shaft, and a rotation radius adjusting mechanism that is rotatably fitted at one end. There is known a four-bar link mechanism type continuously variable transmission having an input-side annular portion and a connecting rod connected to the swing end of the swing link at the other end (for example, a patent Reference 1).

  In Patent Document 1, each turning radius adjusting mechanism includes a disc-shaped cam portion provided eccentrically with respect to the rotation center axis of the input shaft, and a rotating portion provided eccentrically on the cam portion and rotatably provided. And a pinion shaft provided integrally with a plurality of pinions in the axial direction. In addition, a one-way rotation prevention mechanism constituted by a one-way clutch is provided between the swinging portion and the output shaft. The one-way rotation prevention mechanism fixes the swinging portion to the output shaft when the swinging portion attempts to rotate relative to the output shaft, and causes the output shaft to rotate relative to the other side. Oscillates the rocking part.

  The cam part connection body is hollow by connecting through holes of the cam parts, and a pinion shaft is inserted into the inside. The inserted pinion shaft is exposed from the notch portion of each cam portion. The rotating part is provided with a receiving hole for receiving the cam part connecting body. Internal teeth are formed on the inner peripheral surface of the rotating part that forms the receiving hole.

  The internal teeth mesh with the pinion exposed from the notch portion of the cam portion coupling body. When the cam unit coupling body and the pinion are rotated at the same speed, the rotation radius of the rotating unit is maintained. If the rotational speeds of the cam unit coupling body and the pinion are made different, the rotation radius of the rotating unit is changed, and the gear ratio is changed.

  When the connecting part of the cam part is rotated and the rotating part is rotated, the input side annular part of the connecting rod rotates and the swinging end part of the swinging part connected to the other end of the connecting rod swings. Move. That is, a lever crank mechanism (motion conversion mechanism) is configured by the turning radius adjusting mechanism (cam portion, rotating portion, pinion), connecting rod, and swinging portion. Since the oscillating portion is provided on the output shaft via the one-way rotation prevention mechanism, the oscillating portion transmits the rotational driving force (torque) to the output shaft only when rotating to one side.

  The eccentric direction of the cam part of each turning radius adjusting mechanism is set so as to make a round around the rotation center axis of the cam part connecting body with different phases. Accordingly, the connecting rods externally fitted to the rotating parts cause the swinging parts to sequentially transmit torque to the output shaft via the one-way rotation preventing mechanism, so that the output shaft can be smoothly rotated.

International Publication No. 2013/001859

  In the conventional turning radius adjusting mechanism of a continuously variable transmission, a notch is provided in a portion of the cam portion opposite to the eccentric direction. And the pinion exposed from this notch part meshes with the internal tooth provided in the rotation part. However, the cam portion is provided with a receiving hole for receiving a pinion, and the cam portion has relatively low rigidity on the opposite side to the rigidity on the eccentric direction side. In addition, since the notch is provided in the portion opposite to the eccentric direction where the rigidity is low, the rigidity is further lowered, and there is a problem that the rigidity of the cam coupling body as a whole is low.

  An object of the present invention is to provide a continuously variable transmission in which the rigidity of a cam coupling body is improved in view of the above points.

[1] In order to achieve the above object, the present invention provides:
An input unit that is rotated by the driving force of the driving source for traveling;
An output shaft provided parallel to the rotation center axis of the input unit;
A motion conversion mechanism that has a rotating portion that rotates together with the input portion and a swinging portion provided on the output shaft, and that converts the rotational motion of the rotating portion into the swinging motion of the swinging portion;
The swinging portion is fixed to the output shaft when the swinging portion is about to rotate relative to the output shaft, and the swinging portion is relatively positioned relative to the output shaft. A one-way rotation prevention mechanism that idles the rocking portion with respect to the output shaft when attempting to rotate;
A transmission portion that rotates by transmitting the driving force of the adjusting drive source; a pinion that is concentric with the rotation center axis; and a cam portion that is arranged eccentrically with respect to the rotation center axis. A rotation radius adjusting mechanism having a through hole for inserting the pinion, and capable of adjusting a rotation radius of the rotating portion by adjusting a relative phase between the pinion and the cam portion;
A continuously variable transmission that changes a gear ratio by changing a rotation radius of a rotating part,
The rotating part is provided with a receiving hole that is received in an eccentric state with respect to the cam part,
The receiving hole is provided with internal teeth,
The cam portion is provided with an intermediate gear that meshes with the pinion and the internal teeth,
The intermediate gear has a straight line passing through the rotation center of the pinion and perpendicular to the eccentric direction of the cam portion, and a notch portion provided on the eccentric direction side of the cam portion with respect to the boundary line. It meshes with the internal teeth.

  According to the present invention, the pinion and the internal teeth mesh with each other through the intermediate gear through the notch portion provided on the eccentric direction side of the cam portion. Therefore, the cam portion of the present invention can be more rigid than the conventional cam portion in which the cam portion is provided with a notch portion on the opposite side to the eccentric direction where the rigidity is relatively low, and the cam portion is connected. The overall rigidity of the cam portion coupling body can also be improved.

  [2] In the present invention, it is preferable that a bolt connecting the cam portion is inserted through the center of the intermediate gear. According to such a configuration, the center of the intermediate gear can be effectively used to improve the degree of freedom in arranging the bolts, and the bolt can be arranged in the notch portion, so that the rigidity of the cam coupling body can be improved. it can.

  [3] In the present invention, the intermediate gear can be arranged so that the center of the intermediate gear is located on a straight line extending from the rotation center of the pinion in the eccentric direction of the cam portion.

Explanatory drawing which shows embodiment of the continuously variable transmission of this invention. Explanatory drawing which shows the motion conversion mechanism of this embodiment. Explanatory drawing which expands and shows the rotation radius adjustment mechanism of this embodiment. Sectional drawing which expands and shows the rotation radius adjustment mechanism of this embodiment. Explanatory drawing which shows the change of the rotation radius of the rotation part of this embodiment. Explanatory drawing which shows the change of the rocking | fluctuation range of the rocking | swiveling part with respect to the change of the rotation radius of this embodiment. Explanatory drawing which shows the turning radius adjustment mechanism of a reference example. Sectional drawing which shows the turning radius adjustment mechanism of a reference example.

  A continuously variable transmission according to an embodiment of the present invention includes a motion conversion mechanism including a four-bar linkage mechanism, and a transmission gear ratio h (h = rotational speed of an input shaft / rotational speed of an output shaft) is set to infinity (∞). It is a kind of transmission that can make the rotation speed of the output shaft "0", so-called IVT (Infinity Variable Transmission).

  Referring to FIG. 1, a continuously variable transmission 1 of a four-bar linkage mechanism type receives a driving force from a traveling drive source (not shown) such as an engine or an electric motor that is an internal combustion engine, so that a rotation center axis P1 is obtained. An input shaft 2 serving as an input portion that rotates about the center, and an output shaft 3 that is arranged in parallel to the rotation center axis P1 and that transmits rotational power to drive wheels (not shown) of the vehicle via a differential gear (not shown). And six turning radius adjusting mechanisms 4 provided on the rotation center axis P1. A propeller shaft may be provided instead of the differential gear.

  As shown in FIGS. 2 to 4, each turning radius adjusting mechanism 4 includes a cam disk 5 as a cam part and a rotating disk 6 as a rotating part. The cam disks 5 have a disk shape, are eccentric from the rotation center axis P <b> 1, and are provided in each rotation radius adjustment mechanism 4 so as to form one set with respect to one rotation radius adjustment mechanism 4. . The cam disk 5 is provided with a through hole 5a penetrating in the direction of the rotation center axis P1. Further, the cam disk 5 is provided with a notch hole 5b that opens in a direction eccentric to the rotation center axis P1 and communicates the outer peripheral surface of the cam disk 5 with the inner peripheral surface constituting the through hole 5a. .

  Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the rotation center axis P <b> 1 with six sets of cam disks 5 with a phase difference of 60 degrees.

  The cam disk 5 is formed integrally with the cam disk 5 of the adjacent turning radius adjusting mechanism 4 to constitute an integrated cam portion 5c. The integrated cam portion 5c may be formed by integral molding, or may be integrated by welding two cam portions. A pair of cam disks 5 of each turning radius adjusting mechanism 4 are fixed by bolts (not shown). The cam disk 5 located closest to the driving source for traveling on the rotation center axis P1 is formed integrally with the input end 2a. In this way, the input shaft 2 (camshaft) is configured by the input end 2a and the cam disk 5.

  The input shaft 2 (camshaft) includes an insertion hole 60 formed by connecting the through holes 5 a of the cam disk 5. Thereby, the input shaft 2 (camshaft) is formed in a hollow shaft shape in which one end on the opposite side (left side in FIG. 1) to the driving source for driving is open and the other end is closed. As a method for integrally forming the cam disk 5 and the input end 2a, integral molding may be used, or the cam disk 5 and the input end 2a may be integrated by welding.

  The disc-shaped rotating disk 6 is provided with a receiving hole 6a for receiving the cam disk 5 in an eccentric state. In other words, a disc-shaped rotating disk 6 is rotatably fitted on each set of cam disks 5 in an eccentric state.

  As shown in FIG. 2, the rotating disk 6 has a cam disk 5 center point P2 and a rotating disk 6 center point P3, a distance La between the rotation center axis P1 and the center point P2, and a center point P2 and a center point. It is eccentric with respect to the cam disk 5 so that the distance Lb of P3 is the same.

  The receiving hole 6 a of the rotating disk 6 is provided with internal teeth 6 b that are positioned between the pair of cam disks 5.

  In the insertion hole 60 of the input shaft 2, the pinion 70 is positioned concentrically with the rotation center axis P 1 and at a position corresponding to the inner teeth 6 b of the rotating disk 6 so that the pinion 70 can rotate relative to the input shaft 2. Has been placed. The pinion 70 is formed integrally with the pinion shaft 72. The pinion 70 may be configured separately from the pinion shaft 72, and the pinion 70 may be connected to the pinion shaft 72 by spline coupling. In the present embodiment, the term “pinion 70” is defined as including the pinion shaft 72. In the present embodiment, the pinion 70 corresponds to the transmission unit of the present invention.

  An intermediate gear 100 that meshes with the pinion 70 and the internal teeth 6b of the rotary disk 6 is rotatably provided in the cutout hole 5b. In other words, the pinion 70 meshes with the internal teeth 6b via the intermediate gear 100. The pinion shaft 72 is provided with a bearing 74 positioned between the adjacent pinions 70. The pinion shaft 72 supports the input shaft 2 through the bearing 74. The speed reduction mechanism 8 is connected to the pinion shaft 72. The driving force of the adjusting drive source 14 is transmitted to the pinion 70 via the speed reduction mechanism 8.

  As shown in FIG. 2, the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance La and the distance Lb are the same, so that the center point P3 of the rotating disk 6 is the same as the rotation center axis P1. The distance between the rotation center axis P1 and the center point P3, that is, the eccentric amount R1 can be set to “0” so as to be positioned on the axis.

  The continuously variable transmission 1 has a connecting rod 15 having an input-side annular portion 15a having a large diameter at one end and an output-side annular portion 15b having a smaller diameter than the diameter of the input-side annular portion 15a at the other end. Is provided.

  An input side annular portion 15a of the connecting rod 15 is externally fitted to the periphery of the rotary disk 6 via a connecting rod bearing 16 formed of a roller bearing. In addition, the connecting rod bearing 16 may comprise two ball bearings arranged in the axial direction as a set. Six swing links 18 corresponding to the connecting rod 15 are provided on the output shaft 3 via a one-way clutch 17.

  The one-way clutch 17 is provided between the swing link 18 and the output shaft 3. When the swing link 18 is about to rotate relative to the output shaft 3 in one direction, the swing link 18 is connected to the output shaft 3. The rocking link 18 is idled with respect to the output shaft 3 when it is fixed and tries to rotate relative to the other side.

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

  In the present embodiment, the oscillating end 18a is disposed below the output shaft 3 so that the oscillating end 18a of the oscillating link 18 is immersed in the oil reservoir of lubricating oil collected below the case 80. Has been. As a result, the oscillating end 18a can be lubricated with the oil reservoir, and the lubricating oil in the oil reservoir can be lifted by the oscillating motion of the oscillating link 18 to lubricate other components of the continuously variable transmission 1. it can.

  In the description of the embodiment, the gear ratio is defined as the rotational speed of the input shaft / the rotational speed of the output shaft.

  FIG. 5 shows the positional relationship between the pinion shaft 72 and the rotating disk 6 in a state where the eccentric amount R1 as the rotating radius of the rotating disk 6 of the rotating radius adjusting mechanism 4 is changed. FIG. 5A shows a state in which the eccentric amount R1 is “maximum”, and the pinion shaft is such that the rotation center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotation disk 6 are aligned. 72 and the rotary disk 6 are located. At this time, the gear ratio h is minimized.

  FIG. 5B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 5A, and FIG. 5C shows a state in which the eccentric amount R1 is set to “small” which is further smaller than that in FIG. The gear ratio h is “medium” which is larger than the gear ratio h in FIG. 5A in FIG. 5B and “large” which is larger than the gear ratio h in FIG. 5B in FIG.

  FIG. 5D shows a state where the amount of eccentricity R1 is “0”, and the rotation center axis P1 and the center point P3 of the rotating disk 6 are located concentrically. The gear ratio h at this time is infinite (∞). In the continuously variable transmission 1 of the first embodiment, the radius of rotational motion on the input shaft 2 side can be adjusted by changing the amount of eccentricity R1 by the rotational radius adjusting mechanism 4. As apparent from FIG. 5, the turning radius adjusting mechanism 4 adjusts the eccentric amount R <b> 1 (turning radius) of the rotating disk 6 by adjusting the relative base of the pinion 70 and the cam disk 5.

  FIG. 6 shows a change in the swing range of the swing link 18 when the eccentric amount R1 (rotation radius) of the turning radius adjusting mechanism 4 is changed. 6A shows the swing range of the swing link 18 when the eccentric amount R1 is the maximum, FIG. 6B shows the swing range of the swing link 18 when the eccentric amount R1 is medium, and FIG. The swing range of the swing link 18 when the eccentric amount R1 is small is shown. It can be seen from FIG. 6 that the swing range becomes narrower as the eccentric amount R1 becomes smaller. When the eccentric amount R1 becomes “0”, the swing link 18 does not swing.

  In the present embodiment, the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 constitute a lever crank mechanism 20 (motion conversion mechanism). Then, the lever crank mechanism 20 converts the rotational motion of the input shaft 2 into the swing motion of the swing link 18. The continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20.

  When the input shaft 2 is rotated and the pinion shaft 72 is rotated at the same speed as the input shaft 2 when the eccentric amount R1 is not “0”, each connecting rod 15 changes its phase by 60 degrees, and the eccentric amount R1. On the basis of this, it is repeatedly swung between the input shaft 2 and the output shaft 3 by alternately pushing to the output shaft 3 side or pulling to the input shaft 2 side.

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

  Further, the continuously variable transmission 1 of the present embodiment includes a control unit ECU that controls the adjustment drive source 14. The control unit ECU is an electronic unit composed of a CPU, a memory, and the like, and controls the adjustment drive source 14 by executing a control program held in the memory by the CPU, so that the eccentricity of the turning radius adjustment mechanism 4 is controlled. Serves to regulate the amount R1.

  When the rotational speed of the input shaft 2 connected to the input shaft 2 and the rotational speed of the pinion shaft 72 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 72, the rotating disk 6 rotates the periphery of the cam disk 5 around the center point P <b> 2 of the cam disk 5.

  As shown in FIG. 2, the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance La and the distance Lb are the same, so that the center point P3 of the rotating disk 6 is the same as the rotation center axis P1. The distance between the rotation center axis P1 and the center point P3, that is, the eccentric amount R1 can be set to “0” so as to be positioned on the axis.

  According to the continuously variable transmission 1 of the present embodiment, the pinion 70 and the internal teeth 6b mesh with each other via the intermediate gear 100 via the notch hole 5b as a notch provided in the eccentric direction side Ly of the cam disk 5. . Therefore, the cam disk 5 as the cam portion of the present embodiment can have higher rigidity than the conventional cam disk in which the cam disk 5 is provided with a notch portion on the opposite side to the eccentric direction where the rigidity is relatively low. In addition, it is possible to improve the overall rigidity of the input shaft 2 as a cam portion connecting body (camshaft) to which the cam disk 5 is connected.

  In the continuously variable transmission 1 of the present embodiment, a bolt 102 that connects a set of cam disks 5 is inserted through the center of the intermediate gear 100. Thus, the center of the intermediate gear 100 can be effectively used to improve the freedom of arrangement of the bolts 102 and the bolts 102 can be arranged in the notch holes 5b. The rigidity of the input shaft 2 can be improved.

  Further, in the continuously variable transmission 1 of the present embodiment, the intermediate gear 100 is disposed so that the center of the intermediate gear 100 is located on a straight line extending from the rotation center of the pinion 70 in the eccentric direction of the cam disk 5. Yes.

  7 and 8 show, as a reference example, a notch hole 5b as a notch portion provided on the side opposite to the eccentric direction of the cam disk 5, and the pinion 70 and the internal teeth 6b mesh with each other via the notch hole 5b. Show. Thus, if the notch hole 5b as the notch portion is positioned on the opposite side to the eccentric direction, the rigidity of the cam disk 5 and the input shaft 2 as the cam portion coupling body (camshaft) is lowered. There is.

  In the present embodiment, the intermediate gear 100 is arranged so that the center of the intermediate gear 100 is located on a straight line extending from the rotation center of the pinion 70 in the eccentric direction of the cam disk 5. However, the continuously variable transmission of the present invention is not limited to this, and the intermediate gear is cammed with respect to the boundary line Lx, with the straight line passing through the rotation center of the pinion being orthogonal to the eccentric direction Ly of the cam portion. What is necessary is just to arrange | position so that it may mesh with an internal tooth via the notch part provided in the eccentric direction side of the part.

  In the present embodiment, the input end 2a and the cam disk 5 constitute the input shaft 2 (camshaft) as the input portion, and the input shaft 2 is configured by the continuous through hole 5a of the cam disc 5. The thing provided with the insertion hole 60 to be described was demonstrated. However, the input unit of the present invention is not limited to this, and for example, the input unit is configured by a hollow shaft-shaped input shaft having an insertion hole so that one end is opened, and a plurality of disk-shaped cam disks. A through hole may be formed larger than the through hole of the first embodiment so that the input shaft can be inserted into the disk, and the cam disk may be splined to the outer peripheral surface of the input shaft.

  In this case, the input shaft formed of a hollow shaft is provided with a notch hole corresponding to the notch hole of the cam disk. The pinion inserted into the input shaft meshes with the internal teeth of the rotating disk via the notch hole of the input shaft and the notch hole of the cam disk.

  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. You may comprise with the two-way clutch (two-way clutch) comprised so that the rotation direction with respect to the output shaft 3 of the rocking | fluctuation link 18 which can be transmitted is switchable.

  In the present embodiment, the input unit is described as the input shaft 2 and the transmission unit is the pinion 70. However, the input unit and the transmission unit of the present invention are not limited thereto. For example, the input unit may be configured by the pinion 70 and the pinion shaft 72, and the transmission unit may be configured by the input shaft 2.

  Moreover, in this embodiment, the lever crank mechanism 20 was demonstrated as a motion conversion mechanism. However, the motion conversion mechanism of the present invention is not limited to this, and may have other configurations as long as it can convert the rotational motion of the rotating portion into the swinging motion of the swinging portion.

1 Continuously variable transmission 2 Input shaft (input unit)
3 Output shaft 4 Turning radius adjustment mechanism 5 Cam disc (cam part)
5a Through-hole 5b Notch hole 5c Integrated cam part 6 Rotating disk (rotating part)
6a Receiving hole (inner circumference)
6b Internal gear 8 Reduction mechanism (Planetary gear mechanism)
14 Driving source for adjustment (electric motor)
15 Connecting rod 15a Input side annular portion 15b Output side annular portion 16 Connecting rod bearing 17 One-way clutch 18 Oscillating link 18a Oscillating end portion 18b Projection piece 18c Insertion hole 19 Connecting pin 20 Lever crank mechanism (motion conversion mechanism)
60 Insertion hole 70 Pinion (Transmission part)
72 Pinion shaft 74 Bearing 80 Case 100 Intermediate gear 102 Bolt P1 Rotation center axis P2 Center point P3 of the cam disk Distance Lb between the center points La P1 and P2 of the rotation disk R1 Distance R1 between P2 and P3 Eccentricity (distance between P1 and P3)

Claims (3)

An input unit that is rotated by the driving force of the driving source for traveling;
An output shaft provided parallel to the rotation center axis of the input unit;
A motion conversion mechanism that has a rotating portion that rotates together with the input portion and a swinging portion provided on the output shaft, and that converts the rotational motion of the rotating portion into the swinging motion of the swinging portion;
The swinging portion is fixed to the output shaft when the swinging portion is about to rotate relative to the output shaft, and the swinging portion is relatively positioned relative to the output shaft. A one-way rotation prevention mechanism that idles the rocking portion with respect to the output shaft when attempting to rotate;
A transmission portion that rotates by transmitting the driving force of the adjusting drive source; a pinion that is concentric with the rotation center axis; and a cam portion that is arranged eccentrically with respect to the rotation center axis. A rotation radius adjusting mechanism having a through hole for inserting the pinion, and capable of adjusting a rotation radius of the rotating portion by adjusting a relative phase between the pinion and the cam portion;
A continuously variable transmission that changes a gear ratio by changing a rotation radius of a rotating part,
The rotating part is provided with a receiving hole that is received in an eccentric state with respect to the cam part,
The receiving hole is provided with internal teeth,
The cam portion is provided with an intermediate gear that meshes with the pinion and the internal teeth,
The intermediate gear has a straight line passing through the rotation center of the pinion and perpendicular to the eccentric direction of the cam portion, and a notch portion provided on the eccentric direction side of the cam portion with respect to the boundary line. A continuously variable transmission that meshes with the internal teeth. The continuously variable transmission according to claim 1,
A continuously variable transmission, wherein a bolt connecting the cam portion is inserted through the center of the intermediate gear. The continuously variable transmission according to claim 1 or 2,
The continuously variable transmission is characterized in that the intermediate gear is arranged so that the center thereof is located on a straight line extending from the rotation center of the pinion in the eccentric direction of the cam portion.