JP2015034561A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the generation of noise, vibration and wobbling between a rotation radius adjusting mechanism and a connecting rod, in a four-node link mechanism type continuously variable transmission.SOLUTION: A continuously variable transmission 1 comprises: a lever crank mechanism 20 which converts rotational motion of an input shaft 2 into oscillatory motion of an oscillating link 18 which is pivoted to an output shaft 3; and a one-way clutch 17. The lever crank mechanism 20 comprises: a rotation radius adjusting mechanism 4; and a connecting rod 15 which connect the rotation radius adjusting mechanism with the oscillating link 18. A connecting rod bearing 16 is arranged between the rotation radius adjusting mechanism 4 and the connecting rod 15. A buffer part 100 which alleviates an impact between the connecting rod 15 and the connecting rod bearing 16 when the oscillating link 18 is moved to a direction in which power is not transmitted, is arranged between the connecting rod bearing 16 and the connecting rod 15.

Description

  The present invention relates to a continuously variable transmission of a four-bar linkage mechanism type that can change speed by adjusting a rotation radius with a rotation radius adjustment mechanism provided on a rotation center axis of an input shaft.

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

  The input shaft, the output shaft, the turning radius adjusting mechanism, the swing link, and the connecting rod of Patent Document 1 constitute a lever crank mechanism. Between the swing link and the output shaft, the swing link is fixed to the output shaft when trying to rotate relative to the output shaft on one side, and the output shaft is fixed when trying to rotate relative to the other side. On the other hand, a one-way clutch is provided as a one-way rotation prevention mechanism that idles the swing link.

  The turning radius adjusting mechanism includes a disk-like rotating portion having a through hole formed eccentrically from the center, a ring gear provided on the inner peripheral surface of the through hole, and a first pinion fixed to the input shaft and meshing with the ring gear. And a carrier to which the driving force from the adjusting drive source is transmitted, and two second pinions that are pivotally supported by the carrier so as to rotate and revolve, and mesh with the ring gear. The first pinion and the two second pinions are arranged so that a triangle whose apex is the central axis thereof is an equilateral triangle.

  When the rotational speed of the input shaft that is rotated by the main drive source and the carrier that is rotated by the adjustment drive source is the same, the eccentricity of the center point of the rotating portion with respect to the input center axis of the input shaft is maintained, and the rotation radius The radius of the rotation locus of the adjusting mechanism is also kept constant. When the rotational speed of the input shaft rotated by the main drive source and the carrier rotated by the adjustment drive source are different, the amount of eccentricity of the center point of the rotating part with respect to the rotation center axis of the input shaft changes, and the rotation radius adjustment mechanism The radius of rotational motion also changes.

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

  In such a continuously variable transmission, the distance between the center point of the equilateral triangle whose apex is the center axis of the three pinions and the input center axis of the input shaft, and the center point of the equilateral triangle and the center point of the rotating part By setting the distance to be equal to each other, the rotation center axis of the input shaft and the center point of the rotating part can be overlapped to make the amount of eccentricity zero. When the amount of eccentricity is 0, even when the input shaft is rotating, the swing width of the swing end of the swing link is 0, and the output shaft is not rotated.

JP 2012-1048 A

  In a four-bar linkage type continuously variable transmission, a driving force can be transmitted when the swing link is rotated in one direction, and a driving force cannot be transmitted when the swing link is rotated in the other direction. Then, noise, vibration, or rattling may occur between the turning radius adjusting mechanism and the connecting rod or between the connecting rod bearings arranged therebetween.

  In view of the above, an object of the present invention is to provide a continuously variable transmission that suppresses generation of noise, vibration, or rattling between a turning radius adjusting mechanism and a connecting rod.

  In order to achieve the above object, the present invention provides an input shaft that rotates within a case by transmission of a driving force of a main drive source, an output shaft that is arranged in parallel to the rotation center axis of the input shaft, A lever crank mechanism having a swinging link that is pivotally supported and converting the rotational motion of the input shaft into the swinging motion of the swinging link; and the swinging link relatively to one side with respect to the output shaft The swing link is fixed to the output shaft when trying to rotate, and the swing link relative to the output shaft when the swing link tries to rotate relative to the other relative to the output shaft. The lever crank mechanism includes a turning radius adjusting mechanism capable of adjusting a turning radius, and a connecting rod for connecting the turning radius adjusting mechanism and the swing link. The turning radius adjusting mechanism and the front A continuously variable transmission in which a connecting rod bearing is disposed between the connecting rod and the connecting rod, and the connecting rod between the connecting rod and the connecting rod; A buffer portion is provided to reduce a collision with the connecting rod bearing.

  In a four-bar linkage type continuously variable transmission, a driving force can be transmitted when the swing link is rotated in one direction, and a driving force cannot be transmitted when the swing link is rotated in the other direction.

  The inventors of the present application have found that a relatively large amount of noise, vibration, or rattling occurs in the connecting rod bearing when the swing link is rotated to the other.

  According to the present invention, noise generated between the connecting rod and the turning radius adjusting mechanism when the swing link is rotated to the other side can be suppressed by the buffer portion, and the noise of the continuously variable transmission as a whole can be reduced. Vibration and backlash can be suppressed.

  In the present invention, the buffer portion is provided over the entire circumference of the connecting rod bearing, and the buffer portion is more buffered when the swing link is moved to one side than when the swing link is moved to the other. It can comprise so that an effect | action may weaken.

  According to such a configuration, a buffering action can be exhibited even between the connecting rod and the turning radius adjusting mechanism when the swing link is rotated in one direction without hindering transmission of the driving force.

  Further, in the present invention, when the swinging link is moved to the other side, the shock absorber is provided only in a portion where the turning radius adjusting mechanism pushes the connecting rod, and when the swinging link is moved to one side, the turning radius is adjusted. It does not have to be provided in the portion where the mechanism pushes the connecting rod.

  According to this configuration, it is possible to reduce noise and the like without reducing torque transmission responsiveness.

  Moreover, in this invention, a buffer part is arrange | positioned between a metal outer ring part, the metal inner ring part arrange | positioned inside an outer ring part, and an outer ring part and an inner ring part. It can be composed of an elastic body such as rubber.

  According to such a configuration, the buffer portion can be easily assembled to the connecting rod and the connecting rod bearing.

Explanatory drawing which shows embodiment of the power transmission device of this invention in a partial cross section. Explanatory drawing which shows the lever crank mechanism of this embodiment. Explanatory drawing which shows the change of the rotation radius of this embodiment. 3A shows a state where the turning radius is maximum, FIG. 3B shows a case where the turning radius is medium, FIG. 3C shows a case where the turning radius is small, and FIG. 3D shows a state where the turning radius is zero. Explanatory drawing which shows the change of the rocking | fluctuation range of the rocking | fluctuation link with respect to the change of the rotation radius of this embodiment. FIG. 4A shows the swing range when the turning radius is the maximum, FIG. 4B shows the inside of the turning radius, and FIG. 4C shows the swing range when the turning radius is small. Explanatory drawing which shows the X-axis and Y-axis in this embodiment. Explanatory drawing which shows the change of a load direction when the turning radius adjustment mechanism in this embodiment makes 1 rotation. FIG. 7A is an explanatory view showing a buffer portion of the present embodiment. 7B is a cross-sectional view showing a state cut along line X in FIG. 7A. Explanatory drawing which shows the change of a buffer part when the load of this embodiment is added.

  An embodiment of a four-bar linkage mechanism type continuously variable transmission according to the present invention will be described with reference to FIGS. The continuously variable transmission according to the present embodiment is a transmission capable of setting the speed ratio h (h = 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 IVT (Infinity Variable Transmission).

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

  1 and 2, each turning radius adjusting mechanism 4 includes a cam disk 5 as a cam part and a rotating disk 6 as a rotating part. The cam disks 5 have a disk shape, 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 opened in a direction opposite to the direction decentered with respect to the rotation center axis P1, and a notch hole 5b for communicating the outer peripheral surface of the cam disk 5 with the inner peripheral surface constituting the through hole 5a. Is provided.

  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 on the most main drive source side on the rotation center axis P1 is formed integrally with the input shaft end 2a. In this way, the input shaft 2 including the cam disk 5 is configured by the input shaft end portion 2 a and the plurality of cam disks 5.

  The input shaft 2 includes an insertion hole 60 formed by connecting the through holes 5 a of the cam disk 5. Thereby, the input shaft 2 is configured in a hollow shaft shape in which one end opposite to the main drive source ENG is open and the other end is closed. The cam disk 5 located at the other end on the main drive source side is formed integrally with the input shaft end 2a. As a method of integrally forming the cam disk 5 and the input shaft end 2a, integral molding may be used, or the cam disk 5 and the input shaft end 2a may be integrated by welding. .

  Each set of cam disks 5 is rotatably fitted with a disk-shaped rotating disk 6 having a receiving hole 6a for receiving the cam disk 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 Ra between the rotation center axis P1 and the center point P2, and the center point P2 and the center point. It is eccentric with respect to the cam disk 5 so that the distance Rb 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 camshaft 51, the pinion 70 is positioned so as to be concentric with the rotation center axis P <b> 1 and corresponding to the inner teeth 6 b of the rotary disk 6, and the pinion 70 rotates relative to the input shaft 2 having the cam disk 5. It is arranged to be free. 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.

  The pinion 70 meshes with the internal teeth 6 b of the rotating disk 6 through the notch hole 5 b of the cam disk 5. The pinion shaft 72 is provided with a pinion bearing 74 positioned between the adjacent pinions 70. The pinion shaft 72 supports the input shaft 2 via the pinion bearing 74. A differential mechanism 8 composed of a planetary gear mechanism or the like is connected to the pinion shaft 72. The driving force of the adjusting drive source 14 is transmitted to the pinion 70 via the differential mechanism 8.

  Since the rotating disk 6 is eccentric with respect to the cam disk 5 such that the distance Ra and the distance Rb are the same, the center point P3 of the rotating disk 6 is positioned on the same axis as the rotation center axis P1. Thus, the distance between the rotation center axis P1 and the center point P3, that is, the eccentricity R1 can be set to “0”.

  The peripheral edge of the rotary disk 6 is provided with a large-diameter input-side annular portion 15a at one end (on the input shaft 2 side), and at the other end (output shaft 3 side) at the end of the input-side annular portion 15a. An input side annular portion 15a of a connecting rod 15 having a small-diameter output side annular portion 15b is externally fitted rotatably via a connecting rod bearing 16 comprising two ball bearings arranged side by side in the axial direction. 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 on one side, the swing link 18 is connected to the output shaft. 3 (fixed state), and the rocking link 18 is idled with respect to the output shaft 3 (idle state) when trying to rotate relatively 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 projecting pieces 18b projecting 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 as a swing shaft 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 present embodiment, the gear ratio is defined as the rotational speed of the input shaft / the rotational speed of the output shaft.

  FIG. 3 shows the positional relationship between the pinion shaft 72 and the rotating disk 6 in a state where the eccentric amount R1 (rotating radius) of the rotating radius adjusting mechanism 4 is changed. FIG. 3A shows a state where 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. 3B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 3A, and FIG. The gear ratio h is “medium” which is larger than the gear ratio h in FIG. 3A in FIG. 3B and “large” which is larger than the gear ratio h in FIG. 3B in FIG. FIG. 3D 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 (∞). The continuously variable transmission 1 of the present embodiment allows the rotation radius of the rotation radius adjustment mechanism 4 to be adjusted by changing the eccentricity R1 by the rotation radius adjustment mechanism 4.

  FIG. 4 shows a change in the swing range of the swing link 18 when the eccentric amount R1 of the turning radius adjusting mechanism 4 is changed. 4A shows the swing range of the swing link 18 when the eccentric amount R1 is the maximum, FIG. 4B 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. 4 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 (four-bar linkage mechanism). Then, the lever crank mechanism 20 converts the rotational motion of the input shaft 2 into the swing motion of the swing link 18. The continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20. When the input shaft 2 is rotated and the pinion shaft 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. Accordingly, the swing link 18 swings between the input shaft 2 and the output shaft 3 by alternately pushing the swing end 18a toward the output shaft 3 or pulling it toward 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.

  In addition, the power transmission device of the present embodiment includes a control unit (not shown) that controls the adjustment drive source 14. The control unit is an electronic unit composed of a CPU, a memory, and the like, and the control program stored in the memory is executed by the CPU, thereby controlling the adjustment drive source 14 and the amount of eccentricity of the turning radius adjustment mechanism 4. It functions to regulate R1.

  By the way, in the four-bar linkage mechanism type continuously variable transmission 1 of the present embodiment, the driving force can be transmitted when the swing link is rotated in one direction, and the drive force is transmitted when the swing link is rotated in the other direction. I can't communicate.

  Referring to FIG. 6, when the connecting rod 15 pushes the swing link 18 to one side to transmit the driving force, noise, vibration and backlash are compared between the turning radius adjusting mechanism 4 and the connecting rod 15. It is hard to occur. On the other hand, when the connecting rod 15 does not transmit the driving force by pulling the swing link 18 to the other side, noise, vibration, and rattling are relatively likely to occur between the turning radius adjusting mechanism 4 and the connecting rod 15. As a result of the experiment, I found out.

  6A shows a state in which the rotation radius adjustment mechanism 4 is in a no-load state in which the driving force is not transmitted even when the connecting rod 15 pushes the swing link 18 to one side in a state where the gear ratio h is relatively high (underdrive, UD). It is a graph which shows the change of the load direction when it makes 1 rotation. FIG. 6B shows a state in which the gear ratio h is relatively low (top drive, TD), and the turning radius adjusting mechanism 4 makes one rotation in a no-load state in which the driving force is not transmitted even when the connecting rod 15 pushes the swing link 18 in one direction. It is a graph which shows the change of the load direction when made to do.

  FIG. 6C is a state in which the gear ratio h is relatively high (underdrive, UD), and the turning radius adjusting mechanism 4 is rotated once in a load state in which a driving force is transmitted when the connecting rod 15 pushes the swing link 18 to one side. It is a graph which shows the change of the load direction when made to do. FIG. 6D shows a state in which the gear ratio h is relatively low (top drive, TD), and the turning radius adjusting mechanism 4 makes one rotation in a load state in which driving force is transmitted when the connecting rod 15 pushes the swing link 18 to one side. It is a graph which shows the change of the load direction when made to do.

  Therefore, in the continuously variable transmission 1 of the present embodiment, the buffer portion 100 is provided between the input-side annular portion 15 a and the connecting rod bearing 16. The buffer portion 100 is a metal annular outer ring portion 110 that is press-fitted into the input-side annular portion 15a, and a metal that is positioned inside the outer ring portion 110 and is fitted and fixed to the outer ring 16b of the connecting rod bearing 16. The ring-shaped inner ring portion 120 and a rubber elastic body 130 disposed between the outer ring portion 110 and the inner ring portion 120 are configured.

  The connecting rod bearing 16 includes a ball 16a and an outer ring 16b. In the present embodiment, the rotating disk 6 functions as an inner ring of the connecting rod bearing 16.

  Here, as shown in FIG. 5, a straight line passing through the center point P3 of the rotary disk 6 and the center point P4 of the connecting pin 19 that connects the swing link 18 and the output side annular portion 15b of the connecting rod 15 is X A straight line that is orthogonal to the straight line X and passes through the center point P3 is defined as Y.

  As shown in FIG. 7, the elastic body 130 of the buffer part 100 of the present embodiment is formed with a thin part 130a formed thin on the output shaft 3 side and a thicker part on the opposite side than the thin part 130a with the straight line Y as a boundary. It is comprised by the thick part 130b. In this embodiment, two connecting rod bearings 16 are arranged side by side in the axial direction in one lever crank mechanism 20, but in FIG. 7 and FIG. 8, the connecting rod bearing 16 is shown in a simplified manner.

  FIG. 8A shows a change of the buffer 100 when the driving force is transmitted. FIG. 8B shows the buffer unit 100 in a normal state (a state without any load). As shown in FIG. 8A, when the buffer 100 transmits driving force from the connecting rod 15 to the output shaft 3 through the swing link 18 and the one-way clutch 17, the outer ring 110 and the inner ring The thin portion 130a of the elastic body 130 is configured so as to be in contact with 120.

  Thereby, without interfering with the transmission of the driving force, in other words, without reducing the response of the torque transmission, the noise between the input side annular portion 15a, the connecting rod bearing 16, and the rotating disk 6 at the time of driving force transmission. Vibration, rattling can be suppressed.

  Further, as shown in FIG. 8C, the buffer 100 does not transmit the driving force from the connecting rod 15 to the output shaft 3, and the connecting rod 15 pulls the swing link 18 to the input shaft 2 side. The thick portion 130b of the elastic body 130 is configured so that the outer ring portion 110 and the inner ring portion 120 do not contact each other.

  As a result, according to the continuously variable transmission 1 of the present embodiment, noise generated between the connecting rod 15 and the turning radius adjusting mechanism 4 when the swing link 18 is rotated to the other side, that is, when being pulled, Vibration and backlash can be mitigated and suppressed by the buffer 100 having a buffering action, and noise and the like can be suppressed by the continuously variable transmission 1 as a whole.

  Moreover, in this embodiment, the buffer part 100 is comprised with the elastic body 130 between the metal outer ring part 110 and the metal inner ring part 120. This makes it easier to press-fit the connecting rod bearing 16 into the buffer 100 and fix the buffer 100 to the input-side annular portion 15a than when the buffer is made of only an elastic body such as rubber. Thus, it is easy to fix, and the buffer portion 100 can be easily assembled.

  In addition, in this embodiment, it demonstrated using the thing provided with the elastic body 130 which has the thin part 130a as the buffer part 100, and extends over the perimeter of the connecting rod bearing 16. FIG. However, the buffer part of this invention is not restricted to this. For example, even if the thin body portion is deleted and the elastic body is composed only of the thick wall portion, and the portion where the thin wall portion is provided is configured such that the outer ring portion and the inner ring portion are always in contact, It is possible to obtain the effect of the present invention in which noise or the like when the moving link 18 is rotated to the other side is suppressed by the buffer portion.

  In the present embodiment, the connecting rod bearing 16 including the outer ring 16 b has been described. However, the inner ring portion 120 of the buffer portion 100 may be used as the outer ring of the connecting rod bearing 16.

  In the present embodiment, the input shaft end portion 2 a and the plurality of cam disks 5 constitute the input shaft 2, and the input shaft 2 is formed by connecting the through holes 5 a of the cam disk 5. Explained what provided.

  However, the input shaft of the present invention is not limited to this. For example, as a component part of the input shaft, a hollow input shaft core portion having an insertion hole whose one end is open and the other end is closed is provided. An input having a plurality of cam disks is formed by forming a through hole larger than that of the present embodiment so that the input shaft core portion can be inserted into the disk, and by connecting each cam disk to the outer peripheral surface of the input shaft core portion by spline. An axis may be configured.

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

  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. For example, torque is applied from the swing link to the output shaft. A two-way clutch configured to be able to switch the rotation direction with respect to the output shaft of the swing link capable of transmission may be used.

1 continuously variable transmission 2 input shaft 2a input shaft end 2b input shaft bearing 3 output shaft 3a output shaft bearing 4 turning radius adjusting mechanism 5 cam disk (cam portion)
5a Through-hole 5b Notch hole 5c Integral cam part 6 Rotating disc
6a Receiving hole (inner circumference)
6b Internal gear 8 Differential mechanism (Planetary gear mechanism)
12 Stepped pinion 14 Adjustment drive source (motor)
15 Connecting rod 15a Input side annular part 15b Output side annular part 16 Connecting rod bearing 16a Ball 16b Outer ring 17 One-way clutch 18 Oscillating link 18a Oscillating end 18b Projection piece 18c Insertion hole 19 Connecting pin 20 Lever crank mechanism (four-bar link) mechanism)
60 Insertion hole 70 Pinion 72 Pinion shaft 74 Pinion bearing 80 Case 100 Buffer portion 110 Outer ring portion 120 Inner ring portion 130 Elastic body (made of rubber)
130a Thin-walled portion 130b Thick-walled portion P1 Rotation center axis P2 Center point P3 of the cam disk Distance Rb between the center points Ra P1 and P2 of the rotation disk R1 Distance R1 between P2 and P3 Eccentricity (distance between P1 and P3)

Claims (4)

An input shaft that rotates in the case by transmission of the driving force of the main drive source,
An output shaft disposed parallel to the rotation center axis of the input shaft;
A lever crank mechanism having a swing link supported by the output shaft, and converting the rotational motion of the input shaft into the swing motion of the swing link;
When the swing link is about to rotate relative to the output shaft, the swing link is fixed to the output shaft, and the swing link is relative to the other relative to the output shaft. A one-way rotation prevention mechanism that idles the swing link with respect to the output shaft when attempting to rotate,
The lever crank mechanism includes a turning radius adjusting mechanism capable of adjusting a turning radius, and a connecting rod connecting the turning radius adjusting mechanism and the swing link,
A continuously variable transmission in which a connecting rod bearing is disposed between the turning radius adjusting mechanism and the connecting rod,
A buffer portion is provided between the connecting rod bearing and the connecting rod to reduce a collision between the connecting rod and the connecting rod bearing when the swing link is moved to the other. Step transmission. The continuously variable transmission according to claim 1,
The buffer portion is provided over the entire circumference of the connecting rod bearing,
The continuously variable transmission is characterized in that the buffer portion is configured such that the buffering action is weakened when the swing link is moved to one side rather than when the swing link is moved to the other. The continuously variable transmission according to claim 1,
The buffer portion is provided only in a portion where the turning radius adjustment mechanism pushes the connecting rod when the swing link is moved to the other, and the rotation radius adjustment is performed when the swing link is moved to one side. A continuously variable transmission characterized in that a mechanism is not provided at a portion for pushing the connecting rod. The continuously variable transmission according to any one of claims 1 to 3,
The buffer portion includes a metal outer ring portion, a metal inner ring portion disposed inside the outer ring portion, and an elastic body disposed between the outer ring portion and the inner ring portion. A continuously variable transmission comprising: