JP6132689B2 - 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, a hollow shaft-like input portion to which driving force from a driving source for traveling such as an engine is transmitted, an output shaft having a rotation center axis parallel to the rotation center axis of the input portion, and a plurality of lever crank mechanisms A four-bar linkage mechanism type continuously variable transmission is known (see, for example, Patent Document 1).

  In the continuously variable transmission described in Patent Document 1, the lever crank mechanism includes a rotation radius adjustment mechanism that can adjust a rotation radius and can rotate about a rotation center axis of an input unit, and a swing supported by an output shaft. The moving link and one end are rotatably fitted to the turning radius adjusting mechanism, and the other end is connected to a swinging end of the swinging link. The lever crank mechanism converts the rotational motion of the turning radius adjusting mechanism into the swing motion of the swing link.

  Between the swing link and the output shaft, the swing link is fixed with respect to the output shaft when the swing link is about to rotate relative to the output shaft about the rotation center axis of the output shaft. In addition, a one-way clutch is provided as a one-way rotation prevention mechanism that idles the swing link with respect to the output shaft when attempting to rotate relative to the other side.

  The turning radius adjustment mechanism is a disc-shaped cam part that rotates integrally with the input part in a state of being eccentric with respect to the rotation center axis of the input part, and is rotatable to the cam part in a state of being eccentric with respect to the cam part. The rotating part is fitted externally, the pinion shaft is provided so that a plurality of pinions are rotated together in the axial direction, and an adjustment drive source.

  The rotating part is provided with a receiving hole for receiving the cam part at a position eccentric from the center thereof. Internal teeth are formed on the inner peripheral surface of the receiving hole.

  The pinion shaft is disposed concentrically with the rotation center axis of the input unit in the input unit, and is rotatable relative to the input unit by a driving force from an adjustment driving source. Further, external teeth are provided on the outer peripheral surface of the pinion.

  By the way, the input portion is formed with a notch hole that is located in a direction opposite to the eccentric direction of the cam portion with respect to the rotation center axis of the input portion and communicates the inner peripheral surface with the outer peripheral surface.

  The external teeth of the pinion are exposed from the cutout holes of the input part and mesh with the internal teeth formed on the inner peripheral surface of the receiving hole of the rotating part.

  When the rotational speeds of the input unit and the pinion shaft are the same, the rotational radius of the rotational radius adjusting mechanism, that is, the amount of eccentricity is maintained. When the rotational speeds of the input unit and the pinion shaft are different, the rotational radius of the rotational radius adjusting mechanism, that is, the amount of eccentricity is changed.

  Therefore, this turning radius adjustment mechanism controls the rotation speed of the output shaft relative to the rotation speed of the input section by changing the rotation radius, thereby changing the swing width of the swing end of the swing link, and thus the gear ratio. To do.

  In this continuously variable transmission, when the turning radius adjusting mechanism is rotated by rotating the input section, one end of the connecting rod rotates and swings connected to the other end of the connecting rod. The link swings. Since the swing link is pivotally supported on the output shaft via the one-way clutch, the rotational driving force (torque) is transmitted to the output shaft only when rotating on one side with respect to the output shaft.

  In addition, the cam portions are set so that the phases thereof are different from each other, and the plurality of cam portions make a round in the circumferential direction of the input portion. For this reason, the connecting rods externally fitted to the respective turning radius adjusting mechanisms allow the respective oscillating links to transmit torque to the output shaft in order so that the output shaft can be smoothly rotated.

  By the way, the receiving hole of the rotating part is composed of a small-diameter small-diameter hole located in the center in the axial direction and a pair of large-diameter holes arranged so as to sandwich the small-diameter hole from the axial direction and having a larger diameter than the small-diameter hole. . A step portion is formed between the small-diameter hole and the large-diameter hole due to the difference in diameter. The inner teeth are provided on the inner peripheral surface of the small diameter hole.

  A bearing is provided between the outer peripheral surface of the cam portion and the inner peripheral surfaces of the pair of large-diameter holes. This bearing is composed of a plurality of rolling elements made of a cylindrical roller, a cage for maintaining the interval between the plurality of rolling elements, and an outer ring.

JP 2013-19429 A

  In a conventional continuously variable transmission, in order to support a load applied to a rotating part from a connecting rod while maintaining a left-right balance, a pair of bearings are arranged so as to sandwich a step part of the rotating part. It is supported by.

  Here, in order to sufficiently support the load with the bearing, the bearing needs to have a certain width (length in the axial direction). In the conventional continuously variable transmission, since one rotating part is supported by two bearings, there is a problem that if the width of one bearing is sufficiently secured, the shaft length becomes long.

  The present invention has been made in view of the above points, and provides a continuously variable transmission of a four-bar linkage mechanism type capable of shortening an axial length while supporting a load applied to a rotating portion from a connecting rod in a well-balanced manner. For the purpose.

In order to achieve the above object, a continuously variable transmission according to the present invention includes an input unit to which a driving force of a traveling drive source is transmitted, an output shaft having a rotation center axis parallel to the rotation center axis of the input unit, An adjustment drive source, a rotation radius adjustment mechanism capable of adjusting the rotation radius by using the driving force of the adjustment drive source and rotatable about the rotation center axis of the input unit, and a swing supported by the output shaft A lever, a connecting rod for connecting the turning radius adjusting mechanism and the swinging link, a lever crank mechanism for converting the rotational motion of the turning radius adjusting mechanism into the swinging motion of the swinging link, and the swinging link output Rotation link is fixed to the output shaft when trying to rotate to one side with respect to the output shaft around the rotation center axis of the shaft, and oscillating with respect to the output shaft when trying to rotate to the other side One-way rotation prevention mechanism that idles the link and The turning radius adjustment mechanism includes a pinion, a cam portion that rotates eccentrically with respect to the rotation center axis of the input portion, and a receiving hole through which the pinion and the cam portion are inserted at a position eccentric from the center. The cam portion is provided with a through-hole through which the pinion is inserted and a notch hole through which the pinion is exposed. The continuously variable transmission having an internal tooth that meshes with the pinion exposed from the notch hole, wherein the cam portion includes a first cam portion that pivotally supports the rotating portion, and a rotation center of the input portion of the first cam portion. A second cam portion connected to an end portion on either side of the axial direction of the axis and having a notch hole, and the rotating portion includes a first rotating portion pivotally supported by the first cam portion, 2 a position corresponding to the cam portion, the axial direction of the rotation center axis of the input portion of the first rotating part Is articulated displacement or the other end side only, a second rotating part has internal teeth are formed, is provided on the outer peripheral surface of the first rotating part, the outer one of the end portions of the connecting rod is rotatably fitted A fitting portion, and one bearing is provided between the first cam portion and the first rotating portion.

  As described above, the continuously variable transmission according to the present invention is configured so that the load applied to the rotating portion from the connecting rod is aligned with the direction of the load by the first rotating portion, the bearing, and the first cam portion. It has a structure to support.

  Therefore, the load can be sufficiently supported by one bearing, and generation of a load in a direction in which the outer fitting portion falls can be prevented.

  In addition, by reducing the number of bearings used to support one rotating part, the space required for arranging the bearings is reduced due to the integration of the cage constituting the bearings. Since it can be made narrower than the continuously variable transmission, the axial length of the input unit and the pinion shaft can be shortened.

  In the continuously variable transmission according to the present invention, when the driving force of the adjusting drive source is transmitted to the pinion, the second rotating portion is connected to the end of the first rotating portion on the adjusting drive source side. May be.

  The pinion shaft of the continuously variable transmission according to the present invention is twisted by the driving force transmitted from the adjusting drive source and the reaction force applied from the rotating portion. The twist becomes larger as the position is farther from the adjusting drive source.

  Therefore, the second rotating part in which the internal teeth meshing with the external teeth of the pinion shaft and the second cam part in which the second rotating part is externally fitted are more than the first cam part and the first rotating part. By arranging the pinion shaft on the adjustment drive source side where the twist angle is small, the rotation radius of the rotation radius adjustment mechanism, that is, the amount of eccentricity can be accurately controlled.

  Further, in the continuously variable transmission according to the present invention, when a plurality of lever crank mechanisms are provided, the second rotating portion of the lever crank mechanism is disposed adjacent to the second rotating portion of another adjacent lever crank mechanism. May be.

  With such a configuration, the external teeth of the pinion shaft meshing with the internal teeth formed on the two second rotating portions can be made common to form one external tooth.

  As a result, the continuously variable transmission of the present invention can increase the rigidity of the external teeth of the pinion shaft as compared with a continuously variable transmission that is not configured as described above.

  In the continuously variable transmission according to the present invention, the bearing may have a cylindrical rolling element.

  In the continuously variable transmission of the present invention, since there is only one bearing, the space for arranging the bearings per one can be made larger than the space where the bearings of the conventional continuously variable transmission are arranged. it can.

  As a result, even if the rolling element of the bearing is cylindrical, the rolling element can be a cylinder having a sufficiently large axial length with respect to the diameter. Absent.

Sectional drawing which shows the continuously variable transmission of 1st Embodiment of this invention. The schematic diagram which shows the turning radius adjustment mechanism, connecting rod, and rocking | fluctuation link of the continuously variable transmission which 1st Embodiment showed from the axial direction. It is a schematic diagram which shows the change of the rotation radius of the rotation radius adjustment mechanism of the continuously variable transmission of 1st Embodiment, (a) is a rotation radius at the maximum, (b) is a rotation radius, (c) is a rotation radius. Is small and (d) shows the case where the radius of rotation is “0”. It is a schematic diagram which shows the relationship between the change of the rotation radius of the rotation radius adjustment mechanism of the continuously variable transmission of 1st Embodiment, and the rocking | fluctuation angle of the rocking | fluctuation motion of a rocking | fluctuation link, (a) is a rotation radius being the maximum. , (B) shows the swing angle of the swinging motion of the swing link when the rotational radius is medium and (c) is the small rotational radius. It is a schematic diagram showing the relationship between the cam parts of the lever crank mechanism of the continuously variable transmission of 1st Embodiment, (a) is the arrangement | positioning relationship of each cam part, (b) is the relationship of the phase of each cam part, ( c) shows the relationship between the inter-axis distances of the cam portions. Sectional drawing which expands and shows the part around the pinion shaft arrange | positioned at the continuously variable transmission of 1st Embodiment. Sectional drawing which expands and shows the surroundings of the pinion shaft arrange | positioned at the continuously variable transmission of 2nd Embodiment of this invention. It is a schematic diagram showing the relationship of the cam parts of the lever crank mechanism in the modification of the continuously variable transmission of 1st Embodiment or 2nd Embodiment, (a) is the relationship of the phase of each cam part, (b) is The relationship of the distance between the axes of each cam part is shown.

Hereinafter, embodiments of the continuously variable transmission of the present invention will be described. The continuously variable transmission of the present embodiment is a four-bar linkage type continuously variable transmission, and outputs with a gear ratio i (i = rotational speed of the input section / rotational speed of the output shaft) set to infinity (∞). This is a kind of transmission that can make the rotational speed of the shaft "0", so-called IVT (Infinity Variable Transmission).
[First Embodiment]
With reference to FIGS. 1-6, 1st Embodiment of the continuously variable transmission of this invention is described.

  First, with reference to FIG.1 and FIG.2, the structure of 1 A of continuously variable transmission of this embodiment is demonstrated.

  The continuously variable transmission 1A of the present embodiment includes an input unit 2 that rotates about a rotation center axis P1 by receiving a rotation driving force from a driving source for driving such as an engine or electric motor that is an internal combustion engine, and a rotation center axis. An output shaft 3 that is arranged in parallel with P1 and transmits rotational power to drive wheels (not shown) of the vehicle via a differential gear, and six turning radius adjustment mechanisms 4A provided on the rotation center axis P1 are provided. . A propeller shaft may be provided instead of the differential gear.

  Each turning radius adjusting mechanism 4A is provided so as to rotate about the rotation center axis P1, and a cam disk 5 as a cam part, a rotating disk 6 as a rotating part, and a pinion shaft including a plurality of pinions. 7.

  The cam disks 5 are eccentric from the rotation center axis P1 and are provided in each rotation radius adjustment mechanism 4A so as to form one set with respect to one rotation radius adjustment mechanism 4A. 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.

  In addition, each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the rotation center axis P1 with six sets of cam disks 5 with a phase difference of 60 degrees.

  Further, the cam disk 5 is connected to the cam disk 5 of the adjacent turning radius adjusting mechanism 4A to form an integral cam portion. This integrated cam portion may be formed by integral molding, or may be integrated by welding two cam disks 5.

  Further, adjacent cam disks 5 are fixed with bolts (not shown). The cam disk 5 located closest to the driving source for traveling on the rotation center axis P <b> 1 is connected to the input unit 2 integrally. In this way, the camshaft 50 is configured by the input unit 2 and the cam disk 5.

  The camshaft 50 has an insertion hole 50a configured by connecting the through holes 5a of the cam disk 5. Thereby, the camshaft 50 is configured in a hollow shaft shape in which one end opposite to the driving source for driving is opened and the other end is closed.

  The cam disk 5 located at the other 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.

  The rotating disk 6 is provided with a receiving hole 6a at a position eccentric from the center thereof, and is fitted around the receiving disk 6a so as to be rotatable with respect to each set of cam disks 5 one by one. The receiving hole 6 a of the rotating disk 6 is provided with an internal tooth 6 b at a position between the pair of cam disks 5.

  Further, the receiving hole 6a of the rotating disk 6 has a distance Ra from the rotation center axis P1 of the input unit 2 to the center P2 of the cam disk 5 (center of the receiving hole 6a) and the center P2 of the cam disk 5 to the center of the rotating disk 6. The cam disk 5 is eccentric so that the distance Rb to P3 is the same.

  In the insertion hole 50a of the camshaft 50, the pinion shaft 7 is disposed concentrically with the rotation center axis P1 so as to be rotatable relative to the camshaft 50.

  The pinion shaft 7 has external teeth 7 a at locations corresponding to the internal teeth 6 b of the rotary disk 6. The external teeth 7a may be configured separately from the pinion shaft 7, and the external teeth 7a may be connected to the pinion shaft 7 by spline coupling. The external teeth 7 a mesh with the internal teeth 6 b of the rotating disk 6 through the cutout holes 5 b of the cam disk 5.

  The pinion shaft 7 is provided with a bearing 7b positioned between the adjacent external teeth 7a. The pinion shaft 7 supports the camshaft 50 through the bearing 7b.

  The differential mechanism 8 is configured as a planetary gear mechanism, and includes a sun gear 9, a first ring gear 10 coupled to the input unit 2, a second ring gear 11 coupled to the pinion shaft 7, the sun gear 9 and the first ring gear 10. And a carrier 13 that pivotally supports a stepped pinion 12 including a small-diameter portion 12b meshing with the second ring gear 11 so as to rotate and revolve. The sun gear 9 of the differential mechanism 8 is connected to a rotating shaft 14a of an adjustment drive source 14 composed of an electric motor for the pinion shaft 7.

  Therefore, when the rotation speed of the rotating shaft 14a of the adjustment drive source 14 is the same as the rotation speed of the input unit 2, the sun gear 9 and the first ring gear 10 rotate at the same speed. As a result, the four elements of the sun gear 9, the first ring gear 10, the second ring gear 11, and the carrier 13 are locked so as not to rotate relative to each other, and the pinion shaft 7 connected to the second ring gear 11 has the same speed as the input unit 2. Rotate with.

  When the rotational speed of the rotating shaft 14a of the adjustment 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 sun gear 9 and the first ring gear 10 Where j is the gear ratio (number of teeth of the first ring gear 10 / number of teeth of the sun gear 9), the rotation speed of the carrier 13 is (j · NR1 + Ns) / (j + 1). Further, 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 / number of teeth of the small diameter portion 12b). ) Is k, the rotation speed of the second ring gear 11 is {j (k + 1) NR1 + (k−j) Ns} / {k (j + 1)}.

  When there is a difference between the rotational speed of the input unit 2 and the rotational speed of the pinion shaft 7, the rotating disk 6 rotates the periphery of the cam disk 5 around the center P <b> 2 of the cam disk 5.

  As shown in FIG. 2, the rotating disk 6 has a distance Ra from the rotation center axis P1 of the input portion to the center P2 of the cam disk, and from the center P2 of the cam disk to the center P3 of the rotating disk. The distance Rb is decentered to be the same.

  Therefore, the center P3 of the rotary disk 6 is positioned on the same line as the rotation center axis P1 of the input unit 2, and the distance between the rotation center axis P1 of the input unit 2 and the center P3 of the rotary disk 6 (of the turning radius adjusting mechanism 4A). The rotation radius), that is, the eccentricity R1 can be set to “0”.

  A connecting rod 15 is rotatably fitted around the periphery of the rotating disk 6 of the turning radius adjusting mechanism 4A.

  The connecting rod 15 has a large-diameter large-diameter annular portion 15a at one end, and a small-diameter annular portion 15b having a smaller diameter than the diameter of the large-diameter annular portion 15a at the other end. The large-diameter annular portion 15a of the connecting rod 15 is externally fitted to the rotary disk 6 via a connecting rod bearing 16 formed of a ball bearing.

  A swing link 18 is pivotally supported on the output shaft 3 via a one-way clutch 17 as a one-way rotation prevention mechanism.

  The one-way clutch 17 fixes the swing link 18 with respect to the output shaft 3 and rotates the other side with respect to the output shaft 3 when trying to rotate relative to the output shaft 3 around the rotation center axis P4 of the output shaft 3. When the relative rotation is to be performed, the swing link 18 is idled with respect to the output shaft 3.

  The swing link 18 is provided with a swing end 18a. The swing end portion 18a is provided with a pair of projecting pieces 18b formed so that the small-diameter annular portion 15b can be sandwiched in the axial direction. The pair of projecting pieces 18b are formed with through holes 18c corresponding to the inner diameter of the small-diameter annular portion 15b. The connecting rod 15 and the swing link 18 are connected by inserting the connecting pin 19 into the through hole 18c and the small-diameter annular portion 15b.

  In the present embodiment, the input portion 2 and the cam disk 5 constitute a camshaft 50, and the camshaft 50 includes an insertion hole 50a configured by connecting the through holes 5a of the cam disk 5. explained.

  However, the camshaft in the continuously variable transmission according to the present invention is not limited to such a configuration. For example, the input portion is configured in a hollow shaft shape having an insertion hole so that one end is opened, and a disc-shaped cam is formed. A through hole may be formed larger than that of the present embodiment so that the input portion can be inserted into the disc, and the cam disc may be splined to the outer peripheral surface of the input portion configured in a hollow shaft shape.

  In this case, the input portion formed of the hollow shaft is provided with a notch hole corresponding to the notch hole of the cam disk. Then, the pinion inserted into the input part meshes with the internal teeth of the rotating disk via the notch hole of the input part 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 used in the continuously variable transmission of the present invention is limited to the one-way clutch 17. Absent.

  For example, you may comprise with the two-way clutch (two-way clutch) comprised so that a rotation direction with respect to the output shaft of the rocking | fluctuation link which can transmit a torque from a rocking | fluctuation link to an output shaft is switchable.

  Next, the lever crank mechanism of the continuously variable transmission according to this embodiment will be described with reference to FIGS.

  As shown in FIG. 2, in the continuously variable transmission 1A of the present embodiment, a lever radius mechanism 4A, a connecting rod 15, and a swing link 18 constitute a lever crank mechanism 20 (four-bar link mechanism). ing.

  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 1A of the present embodiment includes a total of six lever crank mechanisms 20 as shown in FIG.

  In the lever crank mechanism 20, when the rotation radius of the rotation radius adjustment mechanism 4 </ b> A, that is, the eccentric amount R <b> 1 is not “0”, when the input unit 2 and the pinion shaft 7 are rotated at the same speed, each connecting rod 15 is While the phase is changed by 60 degrees, the swing link 18 is swung by alternately repeating the pushing to the output shaft 3 side and the pulling to the input unit 2 side between the input unit 2 and the output shaft 3.

  A one-way clutch 17 is provided between the swing link 18 and the output shaft 3. The one-way clutch 17 is configured such that the swing link 18 is fixed to the output shaft 3 when the swing link 18 is pushed or pulled by the connecting rod 15. The output shaft 3 is configured to rotate by transmitting the force of 18 swinging motions.

  In the one-way clutch 17, when the swing link 18 is pushed or pulled, the swing link 18 idles and the swing link 18 swings around the output shaft 3. The force of movement is not transmitted and the output shaft 3 is configured not to rotate.

  Since the six turning radius adjusting mechanisms 4A are arranged by changing the phase by 60 degrees, the output shaft 3 is sequentially rotated by the six turning radius adjusting mechanisms 4A.

  In the continuously variable transmission 1A of the present embodiment, as shown in FIG. 3, the rotational radius of the rotational radius adjustment mechanism 4A, that is, the eccentric amount R1 is adjustable.

  FIG. 3A shows a state in which the eccentric amount R1 is “maximum”, and the rotation center axis P1 of the input unit 2, the center P2 of the cam disk 5, and the center P3 of the rotation disk 6 are aligned. The pinion shaft 7 and the rotating disk 6 are located. In this case, the gear ratio i 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. 3C illustrates 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. 3A in FIG. 3B, and “large” which is larger than the gear ratio i in FIG. 3B in FIG. Become. FIG. 3D shows a state where the eccentricity R1 is set to “0”, and the rotation center axis P1 of the input unit 2 and the center P3 of the rotary disk 6 are located concentrically. In this case, the gear ratio i is infinite (∞).

  FIG. 4 is a schematic diagram showing the relationship between the rotation radius of the rotation radius adjusting mechanism 4A of this embodiment, that is, the change in the eccentricity R1, and the swing angle of the swing motion of the swing link 18.

  4A shows the case where the eccentric amount R1 is “maximum” in FIG. 3A (when the gear ratio i is the minimum), and FIG. 4B shows the case where the eccentric amount R1 is “ 4 (c) shows the case where the eccentric amount R1 is “small” in FIG. 3 (c) (when the gear ratio i is large). The swing range θ2 of the swing link 18 with respect to the rotational motion of the turning radius adjusting mechanism 4A is shown.

  Here, the distance from the rotation center axis P4 of the output shaft 3 to the connecting point of the connecting rod 15 and the swinging end portion 18a, that is, the center P5 of the connecting pin 19, is the length R2 of the swinging link 18.

  As is apparent from FIG. 4, as the eccentric amount R1 becomes smaller, the swing range θ2 of the swing link 18 becomes narrower, and when the eccentric amount R1 becomes “0”, the swing link 18 swings. Stops moving.

  In the continuously variable transmission 1A of the present embodiment, as shown in FIG. 5A, the turning radius adjusting mechanism 4A included in each of the six lever crank mechanisms 20 is provided on the side opposite to the engine. That is, in order from the adjustment drive source 14 side, the first to sixth turning radius adjusting mechanisms 41 to 46 are used, and each set of cam disks 5 included in each of them is referred to as the first to sixth cam disks 51 to 56. Yes.

  And as shown in FIG.5 (b), the phase of the 1st cam disk 51 and the 2nd cam disk 52 has shifted | deviated 180 degrees. Further, the phases of the second cam disk 52 and the third cam disk 53 are shifted by 60 ° counterclockwise in FIG. 5B. The phases of the third cam disk 53 and the fourth cam disk 54 are shifted by 180 °. The phases of the fourth cam disk 54 and the fifth cam disk 55 are shifted by 60 ° counterclockwise in FIG. The phases of the fifth cam disk 55 and the sixth cam disk 56 are shifted by 180 °.

  Further, as shown in FIG. 5C, the first to sixth cam disks 51 to 56 are arranged at equal intervals in the axial direction of the input shaft 2.

  In the continuously variable transmission 1A of the present embodiment, the phase of the first to sixth cam disks 51 to 56, that is, the phase and arrangement of the first to sixth turning radius adjusting mechanisms 41 to 46 are set in such a relationship. Accordingly, the centrifugal forces generated in the respective rotation radius adjustment mechanisms 4A cancel each other, and vibrations generated when the respective rotation radius adjustment mechanisms 4A rotate are suppressed.

  Next, the turning radius adjusting mechanism 4A of the continuously variable transmission 1A according to the present embodiment will be described in detail with reference to FIG.

  As shown in FIG. 6, the turning radius adjusting mechanism 4 </ b> A of the continuously variable transmission 1 </ b> A of the present embodiment includes a cam disk 5 and a rotating disk 6.

  The cam disk 5 includes a first cam portion 5c and a second cam portion 5d.

  The first cam portion 5 c is formed in an annular shape and is rotatably supported on the pinion shaft 7 via a bearing 7 b disposed on the outer peripheral surface of the pinion shaft 7.

  The 2nd cam part 5d is a member in which the notch hole 5b was formed, and is connected with the axial direction edge part of the rotation center axis line P1 of the input part 2 of the 1st cam part 5c. The external teeth 7a of the pinion shaft 7 are exposed from the notch hole 5b. Note that the cam disk 5 in FIG. 2 represents the second cam portion 5d.

  The rotating disk 6 includes a first rotating part 6c, a second rotating part 6d, and an external fitting part 6e.

  The first rotating portion 6 c is an annular member, and is rotatably supported by the first cam portion 5 c via the bearing 21.

  6 d of 2nd rotation parts are cyclic | annular members, are the positions corresponding to the 1st cam part 5c, and are connected with the axial direction edge part of the rotation center axis line P1 of the input part 2 of the 1st rotation part 6c. Yes. Moreover, the internal tooth 6b is formed in the internal peripheral surface.

  The outer fitting portion 6e is a disk-shaped member provided on the outer peripheral surface of the first rotating portion 6c, and the large-diameter annular portion 15a of the connecting rod 15 rotates on the outer peripheral surface via the connecting rod bearing 16. It is supported freely.

  The bearing 21 is used for maintaining a plurality of cylindrical rollers 21a disposed between the outer peripheral surface of the first cam portion 5c and the inner peripheral surface of the first rotating portion 6c, and the interval between the plurality of rollers. It is comprised with the holder | retainer 21b.

  Thus, the continuously variable transmission 1A of the present embodiment is configured to include the bearing 21 only between the first cam portion 5c and the first rotating portion 6c that is externally fitted to the first cam portion 5c. .

  That is, the continuously variable transmission 1A of the present embodiment includes the first rotating portion 6c, the bearing 21, and the first load that are applied to the rotating disk 6 from the connecting rod 15 in a line with respect to the direction of the load. The structure is supported by the cam portion 5c.

  Therefore, only one bearing 21 can sufficiently support the load, and generation of a load in a direction in which the outer fitting portion 6e falls can be prevented.

  Moreover, since the continuously variable transmission 1A of this embodiment has only one bearing 21 used to support one rotating disk 6, two bearings are used to support one rotating part. Compared to the necessary conventional continuously variable transmission, the space required for arranging the bearing 21 can be reduced due to the integration of the cage 21b, etc., and the axial length of the input unit 2 and the pinion shaft 7 can be reduced. Can be shortened. Furthermore, the number of parts can be reduced, and the manufacturing process and manufacturing cost can be reduced.

  Further, in the continuously variable transmission 1A of the present embodiment, since there is only one bearing 21, the space for arranging the bearings 21 per one is the space where the bearings of the conventional continuously variable transmission are arranged. It can be made larger.

  As a result, as the cylindrical roller 21a which is a rolling element of the bearing 21, a roller having a sufficiently large axial length with respect to its diameter can be used, so that the roller 21a does not fall down.

  Further, in the continuously variable transmission 1A of the present embodiment, the outer fitting portion 6e is not connected to the second rotating portion 6d formed with the inner teeth 6b that mesh with the outer teeth 7a of the pinion shaft 7, but to the first rotating portion 6c. It is connected.

  As a result, the load applied to the outer fitting portion 6e from the connecting rod 15 is supported by the first cam portion 5c supported by the pinion shaft 7 via the first rotating portion 6c and the bearing 21. The part 6e does not fall down.

  Furthermore, in the continuously variable transmission 1A of the present embodiment, the second rotating portion 6d formed with the internal teeth 6b that mesh with the external teeth 7a of the pinion shaft 7 is more pinion than the connected first rotating portion 6c. It is arranged on the side of the adjusting drive source 14 where the shaft twist angle is small.

This is because the external teeth 7a of the pinion shaft 7 and the internal teeth 6b of the rotary disk 6 are meshed at a position where the twist angle of the pinion shaft 7 that adjusts the rotational radius of the rotational radius adjusting mechanism 4A is small. Therefore, the continuously variable transmission 1A of the present embodiment can easily control the rotational radius of the rotational radius adjusting mechanism 4A, that is, the eccentricity R1, with higher accuracy than the conventional continuously variable transmission.
[Second Embodiment]
A continuously variable transmission 1B according to a second embodiment of the present invention will be described with reference to FIG. However, the continuously variable transmission 1B of the present embodiment has the same configuration as the continuously variable transmission 1A of the first embodiment except for the rotation radius adjustment mechanism, and therefore only the rotation radius adjustment mechanism will be described.

  As shown in FIG. 7, the continuously variable transmission 1 </ b> B of the present embodiment includes a first cam portion 5 c on the traveling drive source side in a rotation radius adjustment mechanism 4 </ b> B <b> 1 out of two adjacent rotation radius adjustment mechanisms. The second rotating portion 6d is disposed, and the second cam portion 5d, the first rotating portion 6c, and the external fitting portion 6e are disposed on the adjustment drive source 14 side.

  On the other hand, in the rotation radius adjustment mechanism 4B2 adjacent to the rotation radius adjustment mechanism 4B1, on the contrary to the adjacent rotation radius adjustment mechanism 4B1, the second cam portion 5d and the first rotation portion 6c are provided on the traveling drive source side. The outer fitting portion 6e is disposed, and the first cam portion 5c and the second rotating portion 6d are disposed on the adjustment drive source 14 side.

  For this reason, the second rotating portions 6d of the two adjacent turning radius adjusting mechanisms 4B1 and 4B2 are disposed adjacent to each other, so that the internal teeth 6b formed on the two second rotating portions 6d are also adjacent. become. Therefore, the external teeth 7a of the pinion shaft 7 meshing with the two internal teeth 6b adjacent to each other can be made common to form one external tooth 7a.

  As a result, the continuously variable transmission 1B according to the present embodiment has the outer teeth 7a of the pinion shaft 7 as compared with the continuously variable transmission 1A according to the first embodiment that includes the outer teeth 7a for the respective inner teeth 6b. The rigidity can be increased.

  Further, since the first cam portions 5c of the two adjacent turning radius adjusting mechanisms 4B1 and 4B2 are arranged adjacent to each other, the bearing 7b of the pinion shaft 7 for pivotally supporting the two second cam portions 5d. Can also be made into a single bearing 7b.

  As a result, the continuously variable transmission 1B of the present embodiment has fewer parts than the continuously variable transmission 1A of the first embodiment in which the bearings 7b of the pinion shaft 7 are provided for each second cam portion 5d. can do. In addition, when the bearing 7b uses a cylindrical rolling element, the rolling element can be prevented from falling.

  Although the illustrated embodiment has been described above, the present invention is not limited to such a form.

  In the continuously variable transmission in each of the above embodiments, the roller 21a is used as the rolling element, but the continuously variable transmission of the present invention is not limited to such a configuration, and the first rotating portion 6c is connected to the first cam. Any shape that can be pivotally supported by the portion 5c may be used. For example, a ball bearing may be used.

  In the continuously variable transmission of each of the above embodiments, the outer fitting portion 6e of the rotating disk 6 is connected to the first rotating portion 6c that is pivotally supported by the first cam portion 5c. The configuration of the transmission is not limited to such a configuration, and may be connected to the second rotating unit 6d.

  In the above-described embodiment, the phase difference of the cam disks of the six lever crank mechanisms 20 is set to 180 °, 60 °, 180 °, 60 °, and 180 ° in order from one side of the rotation center axis P1 of the input shaft 2. However, the continuously variable transmission of the present invention is not limited to such a form.

  For example, as illustrated in FIG. 8, the input shaft 2 may be configured to be 120 °, 120 °, −60 °, 120 °, and 120 ° in order from one side of the rotation center axis P1.

  Even in such a case, the centrifugal forces generated in the respective turning radius adjusting mechanisms cancel each other, and vibrations generated when the respective turning radius adjusting mechanisms rotate can be suppressed.

DESCRIPTION OF SYMBOLS 1A, 1B ... Continuously variable transmission, 2 ... Input part, 2a ... Notch hole, 3 ... Output shaft, 4A, 4B1, 4B2 ... Turning radius adjustment mechanism, 5 ... Cam disk (cam part), 5a ... Through-hole, 5b ... notch hole, 5c ... first cam part, 5d ... second cam part, 6 ... rotating disk (rotating part), 6a ... receiving hole, 6b ... internal teeth, 6c ... first rotating part, 6d ... second rotating part 6e ... external fitting portion, 7 ... pinion shaft, 7a ... external teeth, 7b ... bearing, 8 ... differential mechanism, 9 ... sun gear, 10 ... first ring gear, 11 ... second ring gear, 12 ... stepped pinion, 12a ... large diameter part, 12b ... small diameter part, 13 ... carrier, 14 ... adjusting drive source, 14a ... rotating shaft, 15 ... connecting rod, 15a ... large diameter annular part, 15b ... small diameter annular part, 16 ... connecting rod bearing, 17 ... one-way clutch (one-way rotation prevention mechanism), DESCRIPTION OF SYMBOLS 8 ... Swing link, 18a ... Swing end part, 18b ... Projection piece, 18c ... Through-hole, 19 ... Connection pin, 20 ... Lever crank mechanism, 21 ... Bearing, 21a ... Roller (rolling element), 21b ... Cage , 41 ... first turning radius adjusting mechanism, 42 ... second turning radius adjusting mechanism, 43 ... third turning radius adjusting mechanism, 44 ... fourth turning radius adjusting mechanism, 45 ... fifth turning radius adjusting mechanism, 46 ... sixth. Rotating radius adjusting mechanism 50 ... cam shaft 50a ... insertion hole 51 ... first cam disk 52 ... second cam disk 53 ... third cam disk 54 ... fourth cam disk 55 ... fifth cam disk 56... Sixth cam disk, i... Gear ratio, P1... Rotation center axis of input part 2, P2... Center of cam disk 5, P3... Center of rotation disk 6 (input fulcrum), P4. Center axis, P5 ... connecting pin 1 Center (output fulcrum), Ra... P1 and P2 distance, Rb... P2 and P3 distance, R1... P1 and P3 distance (eccentricity, rotational radius of rotational radius adjusting mechanisms 4A, 4B1 and 4B2), R2. ... distance between P4 and P5 (length of the swing link 18), θ1 ... rotation angle of the turning radius adjusting mechanisms 4A, 4B1, 4B2, and θ2 ... swing range of the swing link 18.

Claims (4)

An input unit to which the driving force of the driving source for traveling is transmitted;
An output shaft having a rotation center axis parallel to the rotation center axis of the input unit;
An adjustment drive source, a rotation radius adjustment mechanism capable of adjusting a rotation radius by using a driving force of the adjustment drive source, and rotatable about a rotation center axis of the input unit, and supported by the output shaft Lever mechanism, and a connecting rod connecting the turning radius adjusting mechanism and the turning link, and a lever crank mechanism for converting the rotational motion of the turning radius adjusting mechanism into the swinging motion of the swing link. When,
When the swing link is about to rotate to one side with respect to the output shaft about the rotation center axis of the output shaft, the swing link is fixed to the output shaft and is about to rotate to the other side. A one-way rotation prevention mechanism that idles the swing link with respect to the output shaft when
The turning radius adjusting mechanism is provided with a pinion, a cam portion that rotates eccentrically with respect to the rotation center axis of the input portion, and a receiving hole through which the pinion and the cam portion are inserted at a position eccentric from the center. A rotating part that is rotatable in an eccentric state with respect to the cam part,
The cam portion is provided with a through hole through which the pinion is inserted, and a notch hole through which the pinion is exposed,
A continuously variable transmission in which inner teeth engaging with the pinion exposed from the notch hole are formed on the inner peripheral surface of the receiving hole,
Said cam portion, said a first cam portion for supporting the rotary portion, is connected to an end portion of either one side in the axial direction of the rotation center axis of the input portion of the first cam portion, the cutout hole A second cam portion formed,
The rotating part is a position corresponding to the first rotating part pivotally supported by the first cam part and the second cam part, and the axial direction of the rotation center axis of the input part of the first rotating part The second rotating portion connected to only one of the end portions of the first rotating portion and the outer peripheral surface of the first rotating portion is provided, and one end portion of the connecting rod is rotatable. An external fitting part that fits externally,
A continuously variable transmission comprising a bearing between the first cam portion and the first rotating portion. The continuously variable transmission according to claim 1,
The driving force of the adjustment drive source is transmitted to the pinion,
The continuously variable transmission, wherein the second rotating part is connected to an end of the first rotating part on the adjustment drive source side. The continuously variable transmission according to claim 1,
A plurality of lever crank mechanisms are provided,
The continuously variable transmission, wherein the second rotating portion of the lever crank mechanism is disposed adjacent to the second rotating portion of another adjacent lever crank mechanism. The continuously variable transmission according to any one of claims 1 to 3,
The said bearing has a cylindrical rolling element, The continuously variable transmission characterized by the above-mentioned.