JP6014503B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission of a four-bar linkage mechanism type using a lever crank mechanism.

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

  In Patent Document 1, each turning radius adjusting mechanism includes a disc-shaped cam portion provided eccentrically on the input shaft, a rotating portion provided eccentrically on the cam portion, and a plurality of pinions. It consists of a pinion shaft provided integrally in the axial direction. A one-way clutch is provided between the swing link and the output shaft. The one-way clutch fixes the swing link to the output shaft when the swing link is about to rotate relative to the output shaft, and To idle the swing link.

  Each cam portion includes a through-hole penetrating in the axial direction of the input shaft and a notch hole provided at a position facing the eccentric direction with respect to the input shaft and communicating the outer peripheral surface of the cam portion with the through-hole. The notch hole is provided from one end surface in the axial direction of the cam portion to the other end surface. Adjacent cam portions are fixed with bolts, thereby forming a cam portion coupling body. One end in the axial direction of the cam portion coupling body is coupled to the input shaft, and the cam portion coupling body and the input shaft constitute a cam shaft.

  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 hole of each cam portion. The rotating part is provided with a receiving hole for receiving the camshaft. 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 shaft exposed from the notch hole of the camshaft. When the input shaft and the pinion shaft are rotated at the same speed, the radius of rotational motion on the input shaft side of the rotational radius adjusting mechanism is maintained. When the rotational speeds of the input shaft and the pinion shaft are made different, the radius of the rotational motion on the input shaft side of the rotational radius adjusting mechanism is changed, and the gear ratio is changed.

  When the rotation radius adjustment mechanism is rotated by rotating the input shaft, the input-side annular portion of the connecting rod rotates, and the swing end of the swing link connected to the other end of the connecting rod swings. Move. That is, a lever crank mechanism is configured by the turning radius adjusting mechanism, the connecting rod, and the swing link. Since the swing link is provided on the output shaft via the one-way clutch, the rotational drive force (torque) is transmitted to the output shaft only when rotating to one side.

  The eccentric direction of the cam portion of each turning radius adjusting mechanism is set so as to make a round around the input shaft with different phases. Therefore, the connecting rod that is externally fitted to each turning radius adjusting mechanism causes the swing link to transmit torque to the output shaft in order, so that the output shaft can be smoothly rotated.

JP-T-2005-502543

  In the conventional four-bar link type continuously variable transmission, the pinion shaft cannot pass through the through hole provided in the cam portion unless the inner diameter of the through hole of the cam portion is made larger than the pinion of the pinion shaft. For this reason, there exists a problem that a cam part will become large.

  In order to make the cam portion small, it is conceivable to make the pinion shaft small together with the pinion. However, a relatively large force is applied to the pinion from the connecting rod, the cam portion, or the like. For this reason, when the pinion is made small, there is a problem that the strength required for the pinion cannot be obtained.

  In view of the above, an object of the present invention is to provide a four-bar link type continuously variable transmission capable of reducing the size of a cam portion as compared with the conventional one while maintaining the strength of a pinion.

  [1] In order to achieve the above object, the present invention provides an input unit to which a driving force from a traveling drive source is transmitted, an output shaft disposed in parallel with a rotation center axis of the input unit, and the output shaft A plurality of lever crank mechanisms that convert the rotational motion of the input unit into the swing motion of the swing link, the swing link, and the output shaft. The swing link is fixed to the output shaft when attempting to rotate relative to the output shaft, and relative to the output shaft when attempting to rotate relative to the other side. A one-way rotation prevention mechanism that idles the swing link, and the lever crank mechanism uses an adjustment drive source and a radius of rotational motion on the input unit side using the drive force of the adjustment drive source. An adjustable turning radius adjusting mechanism, the turning radius adjusting mechanism and the rocking lever A continuously variable transmission including a connecting rod for connecting to the input portion, wherein the rotational radius adjusting mechanism is a cam portion that rotates integrally with the input portion while being eccentric with respect to a rotation center axis of the input portion. And a rotating part that is rotatable in an eccentric state with respect to the cam part, and a pinion to which the driving force of the adjusting drive source is transmitted. The cam part penetrates concentrically with the rotation center axis. The input portion and the cam portion constitute a camshaft, and the pinion is spline-coupled to a pinion shaft to which the driving force of the adjusting drive source is transmitted, and the pinion The power of the adjusting drive source is transmitted through the pinion shaft, and the camshaft is provided with an insertion hole through which the pinion shaft is inserted. The pinion has a diameter corresponding to the diameter of the insertion hole. Characterized in that also a larger diameter.

  According to the present invention, the pinion and the pinion shaft are configured separately. Therefore, it is not necessary to make the diameter of the insertion hole for inserting the pinion shaft large in accordance with the pinion. Therefore, it is not necessary to make the pinion have a small diameter, and the insertion holes of the pinion shaft and the camshaft can be formed to have a small diameter without reducing the strength of the pinion. Thereby, this invention can achieve size reduction of a cam compared with the past.

  [2] In the present invention, the insertion hole of the camshaft can be configured by connecting the through hole of the cam portion.

  [3] In the present invention, the input portion is formed in a hollow shaft shape, the input portion is inserted into the through hole of the cam portion, and the cam portion and the input portion are spline-coupled, whereby the input portion and the cam It can also comprise so that a part may rotate integrally, and the penetration hole of a camshaft can also be comprised by the internal peripheral surface of an input part.

  [4] Further, the turning radius adjustment mechanism of the continuously variable transmission according to the present invention includes a plurality of cam portions divided in the direction of the rotation center axis, and the turning radius adjustment mechanism includes the rotation center axis of the plurality of cam portions. After inserting the pinion shaft into the through hole of the cam portion on the one end side in the direction, and then inserting the pinion shaft into the pinion to spline the pinion to the pinion shaft, the rotation center axis of the plurality of cam portions It can assemble by inserting in the through-hole of the cam part of the other end side of this direction.

The perspective view which shows the basic composition of the continuously variable transmission to which this invention is applied. 1 is a perspective view showing a basic configuration of a continuously variable transmission to which the present invention is partially cut away; FIG. 1 is a cross-sectional view showing a basic configuration of a continuously variable transmission to which the present invention is applied. Sectional drawing which expands and shows a part of FIG. The sectional view showing the basic composition of the continuously variable transmission to which the present invention is applied from the axial direction. (A) is explanatory drawing which shows a rotation part from an axial direction in order to demonstrate the basic composition of the continuously variable transmission to which this invention is applied. (B) is the BB sectional view taken on the line of Fig.6 (a). It is explanatory drawing which shows the change of the rotation radius (eccentric amount) of the rotational radius adjustment mechanism of the continuously variable transmission to which this invention is applied, (a) is the maximum eccentric amount, (b) is the eccentric amount, ( c) shows a small amount of eccentricity, and (d) shows a case where the amount of eccentricity is “0”. Explanatory drawing which shows the pinion and pinion shaft of 1st Embodiment of the continuously variable transmission of this invention. Explanatory drawing which shows the assembly method of the continuously variable transmission of 1st Embodiment. Sectional drawing which expands and shows the part of the rotation-radius adjustment mechanism of the continuously variable transmission of 1st Embodiment. Explanatory drawing which shows the relationship of the magnitude | size of the diameter of the insertion hole of the continuously variable transmission of 1st Embodiment, a pinion shaft, and a pinion. The perspective view which partially cuts and shows the continuously variable transmission of 2nd Embodiment. Sectional drawing which shows the continuously variable transmission of 2nd Embodiment. Sectional drawing which expands and shows a part of FIG. Sectional drawing which expands and shows the part of the rotation-radius adjustment mechanism of the continuously variable transmission of 2nd Embodiment. Explanatory drawing which shows the relationship of the magnitude | size of the diameter of the penetration hole of the continuously variable transmission of 2nd Embodiment, a pinion shaft, and a pinion. Sectional drawing which expands and shows the part of the rotation-radius adjustment mechanism of the continuously variable transmission of the reference example 1. FIG. Sectional drawing which expands and shows the part of the turning radius adjustment mechanism of the continuously variable transmission of the reference example 2. FIG.

  With reference to the drawings, an embodiment of a four-bar linkage type continuously variable transmission of the present invention will be described. First, the basic configuration of a continuously variable transmission to which the present invention is applied will be described with reference to FIGS. The continuously variable transmission to which the present invention is applied has a gear ratio i (i = rotational speed of the input shaft / rotational speed of the output shaft) that is infinite (∞) and the rotational speed of the output shaft can be set to “0”. This is a kind of so-called IVT (Infinity Variable Transmission).

  1 to 5, a four-bar linkage type continuously variable transmission 1 receives a rotational driving force from a driving source such as an internal combustion engine such as an engine or an electric motor so that a rotation center axis P1 is obtained. An input unit 2 that rotates in the center, an output shaft 3 that is arranged in parallel to the rotation center axis P1, and that transmits rotational power to the driving wheels of the vehicle via a differential gear, a propeller shaft, and the like (not shown), and an input unit 2 And six turning radius adjusting mechanisms 4 provided.

  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 opposite to the direction decentered with respect to the rotation center axis P1 and communicates the outer peripheral surface of the cam disk 5 with the through hole 5a.

  Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the input section 2 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 P <b> 1 is formed integrally with the input unit 2. In this way, the camshaft 51 is configured by the input unit 2 and the cam disk 5.

  The camshaft 51 includes an insertion hole 60 formed by connecting the through holes 5 a of the cam disk 5. As a result, the camshaft 51 is configured in a hollow shape having an open end on the side opposite to the driving source for traveling. The cam disk 5 located at the other end on the traveling drive source side is formed integrally with the input unit 2. That is, the cam disk 5 located at the end on the traveling drive source side is formed integrally with the input unit 2. As a method of integrally forming the cam disk 5 and the input part 2, integral molding may be used, or the cam disk 5 and the input part 2 may be integrated by welding.

  Further, each set of cam disks 5 has a disk-shaped rotating disk 6 provided with a receiving hole 6a (see FIGS. 6A and 6B) for receiving the cam disk 5, and is rotatably mounted in an eccentric state. It is fitted.

  As shown in FIG. 5, 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 concentrically with the rotation center axis P <b> 1 and corresponding to the inner teeth 6 b of the rotary disk 6 so that the pinion 70 can rotate relative to the camshaft 51. Has been placed.

  Here, as shown in FIG. 17, the conventional pinion 70 'is formed integrally with the pinion shaft 72'. For this reason, the insertion hole 60 of the camshaft 51 needs to be formed larger than the outer diameter of the pinion 70 'so that the pinion 70' can be inserted. Therefore, the conventional continuously variable transmission 1 has a problem that the camshaft 51 becomes large. Although it is conceivable to make the pinion 70 'smaller, there is a possibility that the strength and rigidity required for the pinion 70' cannot be obtained.

  On the other hand, as shown in FIG. 8, the pinion 70 of the first embodiment of the continuously variable transmission 1 of the present invention is separate from the pinion shaft 72 and is configured to be splined to the pinion shaft 72. Has been.

  Therefore, in the continuously variable transmission 1 according to the first embodiment, the insertion hole 60 may be set larger than the outer diameter of the pinion shaft 72, and does not need to be set larger than the outer diameter of the pinion 70. Therefore, only the pinion shaft 72 can be reduced without reducing the pinion 70, and the camshaft 51 can be downsized.

  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 bearing 74 positioned between the adjacent pinions 70. The pinion shaft 72 supports the camshaft 51 via the bearing 74.

  The differential mechanism 8 is connected to the pinion shaft 72. The differential mechanism 8 includes a planetary gear mechanism, and includes a sun gear 9, a first ring gear 10 connected to the camshaft 51, a second ring gear 11 connected to the pinion shaft 72, the sun gear 9, and A carrier 13 is provided that supports a stepped pinion 12 including a large-diameter portion 12a that meshes with the first ring gear 10 and a small-diameter portion 12b that meshes with the second ring gear 11 so as to rotate and revolve freely.

  The sun gear 9 is connected to a rotating shaft 14 a of an adjustment drive source 14 that is an electric motor for the pinion shaft 72. If the rotational speed of the adjusting drive source 14 is the same as the rotational speed of the input unit 2, the sun gear 9 and the first ring gear 10 rotate at the same speed, and the sun gear 9, the first ring gear 10, and the second ring are rotated. The four elements of the gear 11 and the carrier 13 are locked so as not to rotate relative to each other, and the pinion shaft 72 connected to the second ring gear 11 rotates at the same speed as the input unit 2.

  When the rotational speed of the adjusting drive source 14 is made slower than the rotational speed of the input unit 2, the rotational speed of the sun gear 9 is Ns, the rotational speed of the first ring gear 10 is NR1, and the gear ratio between the sun gear 9 and the first ring gear 10. The number of rotations of the carrier 13 is (j · NR1 + Ns) / (j + 1) where j is the number of teeth of the first ring gear 10 / the number of teeth of the sun gear 9. The gear ratio between the sun gear 9 and the second ring gear 11 ((number of teeth of the second ring gear 11 / number of teeth of the sun gear 9) × (number of teeth of the large diameter portion 12a of the stepped pinion 12 / tooth of the small diameter portion 12b) If the number)) is k, the rotation speed of the second ring gear 11 is {j (k + 1) NR1 + (k−j) Ns} / {k (j + 1)}.

  When the rotational speed of the input unit 2 connected to the camshaft 51 and the rotational speed of the pinion shaft 72 are the same, the rotary disk 6 rotates together with the cam disk 5. When there is a difference between the rotational speed of the input unit 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. 5, the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance Ra and the distance Rb are the same, and therefore the center point P3 of the rotating disk 6 is the same as the 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.

  A connecting rod 15 having a large-diameter large-diameter annular portion 15a at one end and a small-diameter annular portion 15b having a smaller diameter than the large-diameter annular portion 15a at the other end is provided at the periphery of the rotating disk 6. A large-diameter annular portion 15a is rotatably fitted via a connecting rod bearing 16 made of a roller bearing. In addition, the connecting rod bearing 16 may comprise two ball bearings arranged in the axial direction as a set. The output shaft 3 is provided with six swing links 18 corresponding to the connecting rod 15 via a one-way clutch 17 as a one-way rotation prevention mechanism.

  The one-way clutch 17 as a one-way rotation prevention mechanism is provided between the swing link 18 and the output shaft 3, and swings on the output shaft 3 when attempting to rotate relative to the output shaft 3 on one side. The link 18 is fixed, and the swing link 18 is idled with respect to the output shaft 3 when attempting to rotate relative to the other side. The swing link 18 is swingable with respect to the output shaft 3 when the one-way clutch 17 is idle with respect to the output shaft 3.

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

  FIG. 7 shows the positional relationship between the pinion shaft 72 and the rotating disk 6 in a state where the eccentricity R1 of the turning radius adjusting mechanism 4 is changed. FIG. 7A shows a state in which the eccentric amount R1 is set to “maximum”, so 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. The pinion shaft 72 and the rotary disk 6 are located. At this time, the gear ratio i is minimized.

  FIG. 7B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 7A, and FIG. 7C shows that the eccentric amount R1 is smaller than that in FIG. Is shown. The gear ratio i is “medium” which is larger than the gear ratio i in FIG. 7A in FIG. 7B, and “large” which is larger than the gear ratio i in FIG. 7B in FIG. Become. FIG. 7D 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 i at this time is infinite (∞). In the continuously variable transmission 1 of the first embodiment, the radius of rotational motion on the input unit 2 side can be adjusted by changing the amount of eccentricity R1 by the rotational radius adjusting mechanism 4.

  In the first embodiment, the turning radius adjustment 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 unit 2 into the swing motion of the swing link 18. The continuously variable transmission 1 of the first embodiment includes a total of six lever crank mechanisms 20. When the input portion 2 is rotated and the pinion shaft 72 is rotated at the same speed as the input portion 2 when the eccentric amount R1 is not “0”, each connecting rod 15 changes its phase by 60 degrees, and the eccentric amount R1. Based on the above, the input unit 2 and the output shaft 3 are swung alternately repeatedly by pushing to the output shaft 3 side or pulling to the input unit 2 side.

  Since the small-diameter annular portion 15b of the connecting rod 15 is connected to the swing link 18 provided on the output shaft 3 via the one-way clutch 17, the swing link 18 is pushed and pulled by the connecting rod 15 to swing. Then, the output shaft 3 rotates only when the swing link 18 rotates in either the pushing direction side or the pulling direction side, and the output shaft 3 rotates when the swing link 18 rotates in the other direction. Thus, the force of the swing motion of the swing link 18 is not transmitted to the swing link 18, and the swing link 18 is idled. Since each 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.

  Next, an assembling method of the turning radius adjusting mechanism 4 of the first embodiment will be described with reference to FIG. The turning radius adjusting mechanism 4 first inserts the pinion shaft 72 into the through hole 5a of the cam disk 5 on the one end side in the direction of the rotation center axis P1 among the plurality of cam disks 5. Then, as shown in FIG. 9A, the pinion shaft 72 is inserted into the pinion 70, and the pinion 70 is splined to the pinion shaft 72.

  Then, the pinion shaft 72 is inserted through the bearing 74. Then, as shown in FIG. 9B, by inserting the cam disk 5 through the through hole 5a on the other end side in the direction of the rotation center axis P1 among the plurality of cam disks 5, as shown in FIG. 9C. Thus, the turning radius adjusting mechanism 4 can be assembled. FIG. 9C shows a state in which the pinion 70 and the bearing 74 of the adjacent turning radius adjusting mechanism 4 are also attached to the pinion shaft 72.

  According to the continuously variable transmission 1 of the first embodiment, the pinion 70 and the pinion shaft 72 are configured separately. Therefore, it is not necessary to make the diameter of the insertion hole 60 for inserting the pinion shaft 72 large in accordance with the pinion 70. Therefore, the pinion 70 does not need to have a small diameter, and the insertion hole 60 of the pinion shaft 72 and the camshaft 51 can be formed to have a small diameter without reducing the strength of the pinion 70. Thereby, the continuously variable transmission 1 according to the present embodiment can reduce the size of the cam disk 5 and the camshaft 51 which are cam portions as compared with the conventional art.

  Note that, like the continuously variable transmission 1 of the second embodiment shown in FIGS. 12 to 16, the input portion 2 ′ is formed in a hollow shaft shape having an insertion hole 60 so that one end is opened, and a disc-shaped cam disk. A through hole 5a is formed larger than that of the first embodiment so that the input portion 2 'can be inserted into 5', and the cam disk 5 'is splined on the outer peripheral surface of the input portion 2' configured as a hollow shaft. It may be combined. Also in the continuously variable transmission 1 of the second embodiment, it is possible to obtain the operational effect of the present invention that “the cam disk 5 ′ and the cam shaft 51, which are cam portions, can be reduced in size”.

  In the continuously variable transmission 1 of the second embodiment, a notch hole 2a 'is provided in the input portion 2' formed of a hollow shaft so as to correspond to the notch hole 5b of the cam disk 5 '. The pinion shaft 72 inserted into the input portion 2 ′ meshes with the internal teeth 6 b of the rotating disk 6 through the notch hole 2 a ′ of the input portion 2 ′ and the notch hole 5 b of the cam disk 5 ′.

  In the first embodiment and the second 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 thereto, and the swing link 18 is not limited thereto. Alternatively, the swing link 18 capable of transmitting torque to the output shaft 3 may be configured by a two-way clutch (two-way clutch) configured to be able to switch the rotation direction with respect to the output shaft 3.

  FIG. 18 shows a conventional example corresponding to the second embodiment, in which a pinion 70 ′ and a pinion shaft 72 ′ are integrally formed.

1 continuously variable transmission 2 input unit (first embodiment)
2 'input part (2nd Embodiment)
2a ′ cutout hole (second embodiment)
3 Output shaft 4 Turning radius adjusting mechanism 5 Cam disc (cam portion of the first embodiment)
5 'cam disc (cam portion of the second embodiment)
5a Through-hole 5b Notch hole 5c Integrated cam part 6 Rotating disk (rotating part)
6a Receiving hole (inner circumference)
6b Internal gear 8 Differential mechanism (Planetary gear mechanism)
9 Sun gear 10 1st ring gear 11 2nd ring gear 12 Stepped pinion 12a Large diameter part 12b Small diameter part 13 Carrier 14 Adjustment drive source (electric motor)
14a Rotating shaft 15 Connecting rod 15a Large-diameter annular portion 15b Small-diameter annular portion 16 Connecting rod bearing 17 One-way clutch (one-way rotation prevention mechanism)
18 Swing link 18a Swing end 18b Projection piece 18c Insert hole 19 Connecting pin 20 Lever crank mechanism (four-bar link mechanism)
51 Camshaft 60 Insertion hole 70 Pinion 72 Pinion shaft 74 Bearing P1 Rotation center axis P2 Cam disk center point P3 Rotation disk center point Ra Distance Rb between P1 and P2 Distance R1 between P2 and P3 Eccentricity (distance between P1 and P3) )

Claims (4)

An input unit to which driving force from the driving source for traveling is transmitted;
An output shaft disposed parallel to the rotation center axis of the input unit;
A plurality of lever crank mechanisms having a swing link pivotally supported on the output shaft, and converting the rotational motion of the input portion into the swing motion of the swing link;
The swing link is provided between the swing link and the output shaft, and the swing link is fixed to the output shaft when attempting to rotate relative to the output shaft and relative rotation to the other side. A one-way rotation prevention mechanism that idles the swing link with respect to the output shaft when
The lever crank mechanism includes an adjustment drive source, a rotation radius adjustment mechanism capable of adjusting a radius of rotational motion on the input unit side using a drive force of the adjustment drive source, the rotation radius adjustment mechanism, and the A continuously variable transmission comprising a connecting rod connecting the swing link;
The turning radius adjusting mechanism includes:
A cam portion that rotates integrally with the input portion in an eccentric state with respect to the rotation center axis of the input portion;
A rotating part rotatable in an eccentric state with respect to the cam part;
A pinion to which the driving force of the adjustment driving source is transmitted,
The cam portion is provided with a through-hole penetrating concentrically with the rotation center axis.
The input portion and the cam portion constitute a camshaft,
The pinion is splined to a pinion shaft to which the driving force of the adjusting drive source is transmitted,
The power of the adjustment drive source is transmitted to the pinion via the pinion shaft,
The camshaft is provided with an insertion hole through which the pinion shaft is inserted,
The continuously variable transmission, wherein the pinion is formed with a diameter larger than the diameter of the insertion hole. The continuously variable transmission according to claim 1,
The continuously variable transmission according to claim 1, wherein the insertion hole of the camshaft is configured by a continuous through hole of the cam portion. The continuously variable transmission according to claim 1,
The input part is formed in a hollow shaft shape, and the input part is inserted into the through hole of the cam part, and the cam part and the input part are spline-coupled, whereby the input part and the cam part are connected to each other. Configured to rotate integrally,
The continuously variable transmission according to claim 1, wherein the insertion hole of the camshaft comprises an inner peripheral surface of the input portion. A method for assembling a continuously variable transmission according to any one of claims 1 to 3,
The turning radius adjusting mechanism includes a plurality of the cam portions divided in the direction of the rotation center axis.
The turning radius adjusting mechanism causes the pinion shaft to pass through the through hole of the cam portion on one end side in the direction of the rotation center axis among the plurality of cam portions, and then causes the pinion shaft to pass through the pinion. And the pinion is splined to the pinion shaft and then inserted into the through hole of the cam portion on the other end side in the direction of the rotation center axis among the plurality of cam portions. How to assemble the machine.

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