JP6033204B2 - 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 main drive source (driving drive source) such as an engine is transmitted, an output shaft arranged in parallel with the rotation center axis of the input shaft, and a plurality of lever crank mechanisms are provided. A four-link mechanism type continuously variable transmission is known (for example, see Patent Document 1).

  In the continuously variable transmission described in Patent Document 1, the lever crank mechanism is provided with a rotating portion that is rotatable about the rotation center axis of the input shaft, and a rotating radius adjusting mechanism that can adjust the rotating radius of the rotating portion; , A swing link provided with a swing end and pivotally supported by the output shaft, one end rotatably connected to the rotating portion of the turning radius adjusting mechanism, and the other end swinged And a connecting rod connected to the rocking end of the link.

  Between the swing link and the output shaft, when the swing link tries to rotate to one side around the output shaft, the swing link is fixed to the output shaft and tries to rotate to the other side. A one-way clutch is provided as a one-way rotation preventing mechanism that idles the swing link with respect to the output shaft.

  The turning radius adjustment mechanism is a disc-shaped cam part that rotates integrally with the input shaft while being eccentric with respect to the input shaft, and is rotatable while being eccentric with respect to the cam part, and the connecting rod is rotatable. And a sub-drive source that rotates the pinion shaft.

  The turning radius adjusting mechanism is attached to a disk-like rotating part having a through hole formed eccentrically from the center and the inner peripheral surface of the through hole of the rotating part, in addition to the structure shown in Patent Document 1. The internal gear, the first pinion fixed to the input shaft and meshing with the internal gear, the carrier to which the driving force from the auxiliary driving source (adjusting driving source) is transmitted, and each of which can rotate and revolve by the carrier. There are also ones constituted by two second pinions that are pivotally supported by the inner gear and mesh with the internal gear.

  The cam portion is formed with a through-hole penetrating in the direction of the rotation center axis of the input shaft and drilled at a position eccentric with respect to the center of the cam portion. The cam portion has a notch hole that communicates the outer peripheral surface of the cam portion and the inner peripheral surface of the through hole in a region opposite to the center of the cam portion across the rotation center axis of the input shaft. Yes. Adjacent cam portions are fixed with bolts to form a cam portion coupling body.

  The cam part connection body is connected to one end in the axial direction of the cam part connection body and an input part to which the driving force from the driving source for transmission is transmitted, and the cam part connection body and the input part constitute an input shaft (camshaft). . In addition, the input shaft (camshaft) has a configuration shown in Patent Document 1, and a configuration in which a cam portion or a cam portion connecting body is attached to the outer surface of a hollow rod-like input portion by spline coupling or the like. .

  The cam part coupling body is hollow by connecting through holes of the cam parts, and a pinion shaft is inserted therein. And the pinion shaft inserted in the cam part coupling body is exposed from the notch hole of each cam part.

  The rotating part is provided with a receiving hole for receiving an input shaft (camshaft). Internal teeth are formed on the inner peripheral surface of the receiving hole. The internal teeth mesh with the pinion shaft exposed from the notch (through hole) of each cam portion.

  When the rotational speeds of the input shaft (cam shaft) and the pinion shaft are the same, the rotatable rotating portion that is eccentric with respect to the cam portion does not rotate relative to the cam portion. The radius of the rotational movement of the input side fulcrum is maintained. On the other hand, when the rotational speeds of the input shaft (camshaft) and the pinion shaft are different, the rotating portion rotates relative to the cam portion, the radius of the rotational movement of the input side fulcrum is changed, and the gear ratio changes. .

  In this continuously variable transmission, when the input shaft (camshaft) is rotated and the rotating portion is rotated together with the cam portion, one end portion of the connecting rod that is externally fitted to the rotating portion is rotated and connected. A swing link connected to the other end of the rod swings. And since the rocking | fluctuation link is pivotally supported by the output shaft via the one-way clutch, only when rotating to one side, rotational drive force (torque) is transmitted to an output shaft.

  In addition, the cam portions are set so as to have different phases, and the plurality of cam portions make a round in the circumferential direction of the rotation center axis of the input shaft. For this reason, the connecting rods externally fitted to the rotating portions provided in the respective cam portions allow the respective swing links to transmit torque to the output shaft in order so that the output shaft can be smoothly rotated.

JP 2012-251613 A

  By the way, the connecting rod of the continuously variable transmission provided with such a lever crank mechanism has an output-side annular portion at the end on the output shaft side.

  Further, the swing end provided on the swing link has a pair of projecting pieces projecting so as to sandwich the output-side annular portion from the axial direction, and the pair of projecting pieces corresponds to the output-side annular portion. An insertion hole corresponding to the inner diameter is provided.

  The connecting rod and the swing link are connected so as to be relatively rotatable by inserting a connecting pin as a swing shaft into the output-side annular portion and the insertion hole.

  Therefore, a clearance (clearance) in the axial direction of the connecting pin is ensured to some extent between the connecting rod and the swing link, specifically, between the output side annular portion and the pair of projecting pieces for the convenience of assembly. It is necessary to keep it.

  However, when the continuously variable transmission is driven after assembly, since there is a clearance, the output-side annular portion and the pair of protruding pieces of the swing end portion are relatively positioned in the axial direction of the connecting pin. Since they are movable, there is a risk that they may collide and generate vibration and noise.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a continuously variable transmission that can suppress generation of vibrations and noises at a connecting portion between a swing link and a connecting rod.

  In order to achieve the above object, a continuously variable transmission according to the present invention includes an input shaft to which a driving force of a travel drive source is transmitted, an output shaft disposed in parallel with the rotation center axis of the input shaft, and an input shaft. A rotating radius adjusting mechanism that is provided with a rotating portion that is rotatable around the rotation center axis of the rotating shaft, and is capable of adjusting a rotating radius of the rotating portion; a swing link that is provided with a swing end portion and is pivotally supported by the output shaft; One end portion is rotatably connected to the rotating portion of the turning radius adjusting mechanism, and the other end portion has a connecting rod connected to the swing end portion of the swing link, and swings the rotational motion of the input shaft. The lever crank mechanism that converts to the swing motion of the dynamic link and the swing link is fixed to the output shaft when the swing link is about to rotate to one side, and output when it is about to rotate to the other side. A one-way rotation prevention mechanism that idles the swing link with respect to the shaft In the continuously variable transmission, the swinging end of the swinging link and the other end of the connecting rod are connected to each other by a swinging shaft so as to be relatively rotatable, and the swinging end and the other end are connected to each other. A buffer member for biasing the swinging link or the connecting rod in the axial direction of the swinging shaft is disposed therebetween.

  Thus, in the continuously variable transmission according to the present invention, the swing link or the connecting rod is urged in the axial direction of the swing shaft between the swing end of the swing link and the output-side annular portion of the connecting rod. A cushioning member is disposed. By the buffer member, the swing end portion in the axial direction of the swing shaft does not collide with the output side annular portion.

  As a result, the continuously variable transmission of the present invention can suppress the occurrence of vibration and noise at the connecting portion between the swing link and the connecting rod.

  Further, in the continuously variable transmission according to the present invention, when the buffer member is constituted by a plurality of disc springs, the plurality of disc springs are arranged such that the inner diameter side end contacts the swing link and the connecting rod. It is preferable that they are arranged in combination.

  Since the rocking link and the connecting rod rotate with the axis of the rocking shaft as the rotation center axis, the radius of rotation increases as the position becomes farther from the axis of the rocking shaft. That is, the further away from the axis of the oscillating shaft, the longer the sliding distance of the contact portion between the oscillating link and the connecting rod and the buffer member.

  Therefore, for example, a plurality of disc springs constituting the buffer member are arranged in combination (in series) so that the end portions on the outer diameter side are in contact with each other, and a plurality of discs are attached to the swing link and the connecting rod. It is preferable to contact the inner diameter end of the spring.

  If comprised in this way, the sliding distance of the contact part of a rocking | fluctuation link and a connecting rod, and a buffer member is set so that the edge part of the outer diameter side of several disc springs may contact a rocking | fluctuation link and a connecting rod. Compared to the arrangement, it becomes shorter. As a result, it is possible to suppress not only noise and vibration generated by the sliding but also resistance due to friction.

  Alternatively, in the continuously variable transmission according to the present invention, when the rocking link and the connecting rod have a clearance between the rocking shaft and the buffer member is constituted by a disk spring, the disk spring is rocked. Of the links or connecting rods, it is preferable that the end of the inner diameter side be in contact with a member having a large clearance from the swing shaft.

  The swing link and the connecting rod are in contact with the swing shaft and transmit power. Therefore, in this way, the end portion on the inner diameter side of the disc spring is brought into contact with a member having a large clearance with respect to the swing shaft among these members, that is, in a direction perpendicular to the shaft of the swing shaft. If a part that has a short sliding distance and a low resistance due to friction is brought into contact with a movable member, the member will be easier to move than if the end on the outer diameter side is in contact with it. The time until the moving shaft comes into contact, that is, the response time in power transmission can be shortened.

  In the continuously variable transmission according to the present invention, a plurality of lever crank mechanisms, a transmission case that houses the lever crank mechanism and the one-way rotation prevention mechanism, and one end of the input shaft or the output shaft are attached to the transmission case. In the case of including a plurality of bearings that rotatably support the side or the other end side, it is preferable that the buffer member has a higher spring constant as the buffer member is closer to the bearing.

  When a plurality of lever crank mechanisms are provided and both ends of the input shaft or output shaft are supported by fixed bearings, the load applied to the input shaft and output shaft from the lever crank mechanism when the continuously variable transmission is driven Thus, the closer to the bearing, the larger the deflection is caused to incline with respect to the rotation center axis of the input shaft or output shaft that is not driven.

  For this reason, the connecting rod arranged closer to the bearing is inclined with respect to the swing link, so that the swing link and the connecting rod are likely to collide with each other.

  Therefore, if the spring member of the lever crank mechanism at a position close to the bearing is set to have a higher spring constant than the buffer member of the lever crank mechanism at a position farther from the bearing than the buffer member, the swing link and the connecting rod Can be effectively prevented, and noise and vibration caused by the collision can also be effectively suppressed.

1 is a partial cross-sectional view showing a first embodiment of a continuously variable transmission according to the present invention. The side view which shows the lever crank mechanism of the continuously variable transmission of FIG. FIG. 3 is an explanatory diagram showing changes in the rotation radius of the input side fulcrum of the lever crank mechanism of the continuously variable transmission of FIG. 1, 3A is the maximum rotation radius, 3B is the rotation radius, 3C is the rotation radius is small, and 3D is The case where the turning radius is “0” is shown. FIG. 4 is an explanatory diagram showing a relationship between a swing range of an output side fulcrum with respect to a change in a rotation radius of an input side fulcrum of the lever crank mechanism of the continuously variable transmission of FIG. 1, wherein 4A is the maximum swing range, and 4B is a swing. The range is medium, 4C indicates a small swing range, and 4D indicates a case where the swing range is “0”. FIG. 3 is a cross-sectional view taken along line AA in the lever crank mechanism of FIG. 2, illustrating a configuration around a connecting portion between a swing link and a connecting rod of the lever crank mechanism of the continuously variable transmission of FIG. 1. FIG. 2 is a partial cross-sectional view showing bending of an input shaft and an output shaft in a driving state of the continuously variable transmission of FIG. 1. Sectional drawing which shows the structure of the connection part periphery of the rocking | fluctuation link and connecting rod in the lever crank mechanism of 2nd Embodiment of the continuously variable transmission of this invention.

  Hereinafter, embodiments of a continuously variable transmission according to the present invention will be described with reference to the drawings. The continuously variable transmission of the present embodiment is a four-bar linkage type continuously variable transmission, and outputs with a gear ratio h (h = rotational speed of the input shaft / 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]
A continuously variable transmission 1A of the present embodiment will be described with reference to FIGS.

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

  As shown in FIG. 1, the continuously variable transmission 1 </ b> A of the present embodiment includes an input unit 2, an output shaft 3 arranged in parallel with the rotation center axis P <b> 1 of the input unit 2, and a rotation center axis P <b> 1 of the input unit 2. And six turning radius adjusting mechanisms 4 provided on the top.

  The input unit 2 rotates around the rotation center axis P <b> 1 by transmitting a driving force from an engine ENG (traveling drive source) that is a main drive source. In addition, as a main drive source, you may use an electric motor other than an internal combustion engine.

  The output shaft 3 transmits rotational power to drive wheels (not shown) of the vehicle via a differential gear (not shown). A propeller shaft may be provided instead of the differential gear.

  The turning radius adjusting mechanism 4 includes a cam disk 5 (cam part) provided on the rotation center axis P <b> 1 of the input unit 2 and a rotating disk 6 (rotating part) that is rotatably fitted on the cam disk 5. Have.

  The cam disks 5 have a disk shape, and are provided in pairs so that they can rotate integrally with the input unit 2 while being eccentric with respect to the rotation center axis P1 of the input unit 2. Each set of cam disks 5 is set so as to have a phase difference of 60 °, and is arranged so that the six sets of cam disks 5 make a round in the circumferential direction of the rotation center axis P1 of the input unit 2.

  The cam disk 5 is formed with a through hole 5 a that penetrates in the direction of the rotation center axis P <b> 1 of the input unit 2 and is formed at a position eccentric with respect to the center P <b> 2 of the cam disk 5. Further, the cam disk 5 communicates with the outer peripheral surface of the cam disk 5 and the inner peripheral surface of the through hole 5a in a region opposite to the center P2 of the cam disk 5 across the rotation center axis P1 of the input portion 2. A notch hole 5b is formed.

  A set of two cam disks 5 is fixed with bolts (not shown). Further, one of the two cam disks 5 is formed integrally with the other of the other two cam disks 5 of the adjacent turning radius adjusting mechanism 4 to form an integral cam portion. Yes. The cam disk 5 located closest to the engine ENG among the cam disks 5 is formed integrally with the input unit 2. In this way, the input unit 2 and the plurality of cam disks 5 constitute an input shaft (camshaft).

  The two cam disks 5 may be fixed by other means instead of bolts. The integral cam portion may be formed by integral molding, or may be integrated by welding two cam disks 5. In addition, as a method of integrally forming the cam disk 5 and the input portion 2 that are closest to the engine ENG, the cam disc 5 and the input portion 2 may be integrally formed. May be used.

  As shown in FIG. 2, the rotary disk 6 has a disk shape in which a receiving hole 6 a is provided at a position eccentric from the center P <b> 3, and is provided to be rotatable with respect to the rotation center axis P <b> 1 of the input unit 2. . A set of cam disks 5 is rotatably fitted in the receiving holes 6a. Further, as shown in FIG. 1, an internal tooth 6 b is provided in the receiving hole 6 a of the rotating disk 6 at a position between the pair of cam disks 5.

  Further, the receiving hole 6a of the rotating disk 6 has a distance Rx from the rotation center axis P1 of the input portion 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 Ry to P3 is the same.

  The input shaft configured by the input unit 2 and the plurality of cam disks 5 includes an insertion hole 50 configured by connecting through holes 5 a of the cam disk 5. Thereby, the input shaft has a hollow shaft shape in which one end opposite to the engine ENG is open and the other end is closed.

  In the insertion hole 50, the pinion shaft 7 is arranged concentrically with the rotation center axis P1 so as to be rotatable relative to the input shaft.

  The pinion shaft 7 has a pinion 7 a at a position corresponding to the internal teeth 6 b of the rotary disk 6. Further, the pinion shaft 7 is positioned between adjacent pinions 7 a in the direction of the rotation center axis P <b> 1 of the input unit 2, and a pinion bearing 7 b is provided. The pinion shaft 7 supports the input shaft via the pinion bearing 7b.

  The pinion 7 a is formed integrally with the shaft portion of the pinion shaft 7. The pinion 7 a 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 7a may be configured separately from the pinion shaft 7 and connected to the pinion shaft 7 by spline coupling. In the present embodiment, the term “pinion 7 a” is defined as including the pinion shaft 7.

  The pinion shaft 7 is connected to a differential mechanism 8 constituted by a planetary gear mechanism or the like.

  As shown in FIG. 1, the differential mechanism 8 is configured as a planetary gear mechanism, for example, and includes a sun gear 9, a first ring gear 10 connected to an input shaft configured by the input unit 2 and a plurality of cam disks 5. A stepped pinion 12 comprising a second ring gear 11 connected to the pinion shaft 7, a large diameter portion 12 a meshing with the sun gear 9 and the first ring gear 10, and a small diameter portion 12 b meshing with the second ring gear 11 is rotated and rotated. It has a carrier 13 that is pivotably supported.

  The sun gear 9 is transmitted with driving force from an actuator 14 (adjusting drive source) which is a sub drive source for the pinion shaft 7. Therefore, the driving force of the actuator 14 is also transmitted to the pinion 7 a via the differential mechanism 8.

  When the rotation speed of the pinion shaft 7 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 that they cannot rotate relative to each other, and the pinion shaft 7 connected to the second ring gear 11 is the same as the input unit 2. Rotates at speed.

  When the rotational speed of the pinion shaft 7 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 (first When j is the number of teeth of the ring gear 10 / the number of teeth of the sun gear 9, the number of rotations of the carrier 13 is (j · NR1 + Ns) / (j + 1). 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)}.

  That is, when there is a difference between the rotational speed of the input unit 2 and the rotational speed of the pinion shaft 7, the driving force transmitted from the actuator 14 transmitted through the internal teeth 6 b of the rotating disk 6 that meshes with the pinion 7 a of the pinion shaft 7. Thus, the rotating disk 6 rotates the periphery of the cam disk 5 around the center P2 of the cam disk 5.

  Incidentally, as shown in FIG. 2, the rotating disk 6 rotates with respect to the cam disk 5 from the rotation center axis P <b> 1 of the input unit 2 to the center P <b> 2 of the cam disk 5 and the center P <b> 2 of the cam disk 5. It is eccentric so that the distance Ry to the center P3 of the disk 6 is 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 rotation radius adjusting mechanism 4). The rotation radius), that is, the eccentricity R1 can be set to “0”.

  At the periphery of the rotary disk 6, there is a large-diameter input-side annular portion 15 a at one end (on the input portion 2 side), and at the other end (output shaft 3), the diameter of the input-side annular portion 15 a is larger. A connecting rod 15 having a small-diameter output-side annular portion 15b is rotatably connected.

  The input side annular portion 15a of the connecting rod 15 is rotatably fitted to the rotary disk 6 via connecting rod bearings 16 each consisting of a set of two ball bearings arranged in the axial direction.

  Six swing links 18 are pivotally supported on the output shaft 3 in correspondence with the connecting rod 15 via a one-way clutch 17 (one-way rotation prevention mechanism).

  The one-way clutch 17 is provided between the swing link 18 and the output shaft 3, and the swing link 18 tends to rotate relative to the output shaft 3 on one side about the rotation center axis P <b> 5 of the output shaft 3. In this case, the swing link 18 is fixed to the output shaft 3 (fixed state), and the swing link 18 is idled with respect to the output shaft 3 (idle state) when relative rotation is to be made on 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 from 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.

  The connecting rod 15 and the swing link 18 are connected so as to be relatively rotatable by inserting a connecting pin 19 as a swing shaft into the insertion hole 18c and the output side annular portion 15b.

  In the continuously variable transmission 1A of the present embodiment, a lever crank mechanism 20 is configured by the turning radius adjusting mechanism 4, the swing link 18, and the connecting rod 15 having the above-described configuration.

  The lever crank mechanism 20 and the one-way clutch 17 are housed in a transmission case 21. Below the transmission case 21, lubricating oil forms an oil reservoir.

  The swing link 18 is disposed such that the swing end portion 18a is immersed in an oil reservoir of lubricating oil collected below the transmission case 21.

  Therefore, when the lever crank mechanism 20 is driven, the oscillating end 18a is lubricated by the oil reservoir, and the lubricating oil in the oil reservoir is lifted up by the oscillating motion of the oscillating link 18, so that the other of the continuously variable transmission 1A. The parts can be lubricated.

  Further, the transmission case 21 is spaced from one end wall 21a fixed to the engine ENG, the other end wall 21b disposed to face the one end wall 21a, the lever crank mechanism 20 and the one-way clutch 17. And is formed by a peripheral wall portion 21c that connects the outer edge of the one end wall portion 21a and the outer edge of the other end wall portion 21b.

  An opening for supporting the input shaft and an opening for supporting the output shaft 3 are formed in the one end wall portion 21a and the other end wall portion 21b. 22 is fitted.

  In the present embodiment, the one provided with the six lever crank mechanisms 20 has been described. However, the number of lever crank mechanisms in the continuously variable transmission of the present invention is not limited to that number. For example, five or less lever crank mechanisms may be provided, or seven or more lever crank mechanisms may be provided. May be.

  Further, in the present embodiment, the input shaft 2 and the plurality of cam disks 5 constitute an input shaft, and the input shaft is provided with the insertion hole 50 configured by connecting the through holes 5 a of the cam disk 5. . However, the input shaft in the continuously variable transmission of the present invention is not limited to that configured as described above.

  For example, the input part is configured in a hollow shaft shape having an insertion hole so that one end is opened, and the through hole is formed to be larger than that of the present embodiment so that the input part can be inserted into a disc-shaped cam disk. The cam disk 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.

  Further, in the present embodiment, the one-way rotation prevention mechanism using the one-way clutch 17 has been described. However, the one-way rotation prevention mechanism in the continuously variable transmission of the present invention is not limited to the one-way clutch, and for example, the rotation direction of the swing link capable of transmitting torque from the swing link to the output shaft can be switched. A two-way clutch may be used.

  Next, the lever crank mechanism 20 of the continuously variable transmission according to this embodiment will be described with reference to FIGS.

  As shown in FIG. 1, the continuously variable transmission 1A of the present embodiment includes a total of six lever crank mechanisms 20 (four-bar linkage mechanisms). As shown in FIG. 2, the lever crank mechanism 20 includes a connecting rod 15, a swing link 18, and a rotating radius adjusting mechanism 4 having a rotating disk 6 and having an adjustable rotating radius. The lever crank mechanism 20 converts the rotational motion of the input shaft into the swing motion of the swing link 18.

  In this lever crank mechanism 20, when the rotation radius (eccentricity R1) of the center P3 (input side fulcrum) of the rotary disk 6 of the rotation radius adjusting mechanism 4 is not "0", the input unit 2 and the pinion shaft 7 are the same. When rotating at a speed, each connecting rod 15 pushes the swing end 18a between the input unit 2 and the output shaft 3 toward the output shaft 3 or pulls it toward the input unit 2 while changing the phase. The rocking link 18 is rocked by alternately repeating.

  Since the one-way clutch 17 is provided between the swing link 18 and the output shaft 3, when the swing link 18 is swung by being pushed and pulled by the connecting rod 15, the swing link 18 is pushed in the pushing direction side. Alternatively, when rotating in one of the tension direction sides, the swing link 18 is fixed to the output shaft 3 and the output shaft 3 rotates, and when the swing link 18 rotates in the other direction, the swing link 18 It idles with respect to the output shaft 3.

  In the continuously variable transmission 1A of the present embodiment, the rotational radius adjusting mechanisms 4 of the six lever crank mechanisms 20 are arranged by changing the phase by 60 degrees, so that the output shaft 3 has six lever cranks. The mechanism 20 is rotated in order.

  FIG. 3 is a diagram showing the positional relationship between the pinion shaft 7 and the rotating disk 6 in a state where the rotating radius (the eccentric amount R1) of the center P3 (input side fulcrum) of the rotating disk 6 of the rotating radius adjusting mechanism 4 is changed. is there.

  FIG. 3A shows a state in which the amount of eccentricity R1 is set to “maximum”, and the pinion shaft 7 so that 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. And the rotating disk 6 are positioned. In this case, 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. 3C shows a state in which the eccentric amount R1 is set to be “small” which is further smaller than that in FIG. The gear ratio h is “medium” which is larger than the gear ratio h in FIG. 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 of the input unit 2 and the center P3 of the rotary disk 6 are located concentrically. In this case, the gear ratio h is infinite (∞).

  4 shows the relationship between the rotation radius (eccentricity R1) of the center P3 (input side fulcrum) of the rotary disk 6 of the rotary radius adjusting mechanism 4 and the swing range θ2 of the swing motion of the swing link 18. FIG.

  4A shows the case where the eccentric amount R1 is “maximum” in FIG. 3A (when the gear ratio h is minimum), and FIG. 4B shows the case where the eccentric amount R1 is “medium” in FIG. 4C shows the case where the eccentric amount R1 is “small” in FIG. 3C (when the gear ratio h is large), and FIG. 4D shows the eccentric amount R1 which is “0” in FIG. 3D. The case (when the gear ratio h is infinite (∞)) is shown.

  Here, R2 is the length of the swing link 18. More specifically, R2 is the distance from the rotation center axis P5 of the output shaft 3 to the connecting point between the connecting rod 15 and the swinging end portion 18a, that is, the center P4 of the connecting pin 19. Θ1 is the phase of the rotating disk 6 of the turning radius adjusting mechanism 4.

  As can be seen from FIG. 4, as the eccentric amount R1 becomes smaller, the swing range θ2 of the swing link 18 becomes narrower. Stops moving.

  Next, with reference to FIGS. 1, 2, 5, and 6, the structure around the connecting portion between the connecting rod 15 and the swing link 18 of the continuously variable transmission 1A of the present embodiment will be described in detail.

  As shown in FIG. 2, the output shaft 3 side end of the connecting rod 15 provided in the lever crank mechanism 20 and the swing end portion 18a of the swing link 18 are output formed at the end on the output shaft 3 side. By inserting the connecting pin 19 into the insertion hole 18c formed in the pair of protruding pieces 18b of the side annular portion 15b and the swinging end portion 18a, the side annular portion 15b is connected so as to be relatively rotatable. That is, the connecting pin 19 is a swing shaft in the present invention.

  Then, as shown in FIG. 5, the output side annular portion 15 b and the pair of protruding pieces 18 b of the swing link 18 connected in this way are connected so as to maintain the distance therebetween. A buffer member 23 that biases the pin 19 in the axial direction is disposed. The buffer member 23 is composed of two disc springs 23a and 23b.

  By the way, the connecting rod 15 and the swing link 18 rotate with the axis of the connection pin 19 as the rotation center axis, so that the rotation radius becomes larger as the position is away from the axis of the connection pin 19. That is, as the distance from the axis of the connecting pin 19 increases, the sliding distance of the contact portion between the connecting rod 15 and the swing link 18 and the buffer member 23 increases.

  Therefore, in the continuously variable transmission 1A of the present embodiment, the two disc springs 23a and 23b constituting the buffer member 23 are combined in series (in series) so that their outer diameter side ends are in contact with each other. At the same time, the end portions on the inner diameter side of the two disc springs 23a and 23b are brought into contact with the output-side annular portion 15b of the connecting rod 15 and the protruding piece 18b of the swing link 18.

  Therefore, the sliding distance between the connecting rod 15 and the contact portion between the swing link 18 and the buffer member 23 is such that two disc springs 23 a and 24 b are provided on the output side annular portion 15 b of the connecting rod 15 and the projecting piece 18 b of the swing link 18. Compared to the case where the end of the outer diameter side of 23b is arranged to contact, it is shorter.

  As shown in FIG. 1, the continuously variable transmission 1 </ b> A of the present embodiment includes six lever crank mechanisms 20, a transmission case 21 that houses the lever crank mechanism 20 and the one-way clutch 17, and a transmission case 21. And a plurality of bearings 22 that are fitted to the one end wall portion 21a and the other end wall portion 21b and rotatably support one end side or the other end side of the input shaft or the output shaft 3.

  Therefore, in the driven state, as shown in FIG. 6, the input shaft is positioned closer to the bearing 22 due to the load applied from the lever crank mechanism 20, and the rotation center axis of the input unit 2 in the non-driven state. It bends greatly so as to be inclined with respect to P1a.

  Similarly, in the driven state, the output shaft 3 is inclined with respect to the rotation center axis P5a of the output shaft 3 in the non-driven state as the position is closer to the bearing 22 due to the load applied from the lever crank mechanism 20. It bends greatly.

  Therefore, the buffer member 23 provided in each of the six lever crank mechanisms 20 is set such that the spring member 23 closer to the bearing 22 has a higher spring constant, and the lever crank mechanism 20 closer to the bearing 22 is connected to the connecting rod 15. The relative movement in the axial direction of the connecting pin 19 with the swing end 18a of the swing link 18 is strongly suppressed.

  As described above, in the continuously variable transmission 1A according to the present embodiment, the connecting rod 15 or the swinging rod is provided between the output-side annular portion 15b of the connecting rod 15 and the protruding piece 18b of the swinging end portion 18a of the swinging link 18. A buffer member 23 that urges the protruding piece 18b of the moving link 18 in the axial direction of the connecting pin 19 is disposed.

  Therefore, the shock-absorbing member 23 prevents the projecting piece 18b of the swinging end portion 18a in the axial direction of the connecting pin 19 from colliding with the output-side annular portion 15b.

  As a result, in the continuously variable transmission 1A of the present embodiment, generation of vibration and noise at the connecting portion between the connecting rod 15 and the swing link 18 is suppressed.

  In the continuously variable transmission 1 </ b> A of the present embodiment, the two disc springs 23 a and 23 b constituting the buffer member 23 are provided on the inner diameter side of the output side annular portion 15 b of the connecting rod 15 and the protruding piece 18 b of the swing link 18. It arrange | positions so that the edge part of may contact.

  As a result, the connecting rod 15 is compared to the case where the outer end of the two disc springs 23a, 23b are in contact with the output-side annular portion 15b of the connecting rod 15 and the protruding piece 18b of the swing link 18. 15, the sliding distance of the contact portion between the swing link 18 and the buffer member 23 is shortened, and not only noise and vibration generated by the sliding but also resistance due to friction is reduced.

  Further, in the continuously variable transmission 1A of the present embodiment, the buffer member 23 has a higher spring constant as the buffer member 23 closer to the bearing 22 and swings with the connecting rod 15 as the lever crank mechanism 20 closer to the bearing 22. The relative movement in the axial direction of the connecting pin 19 with the swing end 18a of the link 18 is strongly suppressed.

  As a result, the collision between the connecting rod 15 and the rocking end 18a of the rocking link 18 is effectively prevented, and noise and vibration caused by the collision are also effectively suppressed.

[Second Embodiment]
With reference to FIG. 7, the continuously variable transmission 1B of the present embodiment will be described. However, among the configurations of the continuously variable transmission 1B of the present embodiment, the same components as those of the continuously variable transmission 1A of the first embodiment are denoted by the same reference numerals, and descriptions thereof are omitted.

  As shown in FIG. 1, in the continuously variable transmission 1 </ b> B of the present embodiment, the connecting rod 15 and the swing end 18 a of the swing link 18 are output side annular portions 15 b formed at the end of the connecting rod 15. And a connecting pin 19 is inserted into the insertion hole 18c formed in the pair of projecting pieces 18b of the swinging end portion 18a so as to be relatively rotatable. That is, the connecting pin 19 is a swing shaft in the present invention.

  A buffer that biases them in the axial direction of the connecting pin 19 so as to maintain a gap between the connected output-side annular portion 15b and the pair of projecting pieces 18b of the swing link 18. A member 24 is arranged.

  By the way, between the connecting pin 19 that is the swing shaft and the inner peripheral surface of the output-side annular portion 15b formed in the connecting rod 15 through which it is inserted, there is no swing for assembly. In order to make it possible, a predetermined gap (clearance) is provided.

  Similarly, between the connecting pin 19 and the inner peripheral surface of the insertion hole 18c formed in the protruding piece 18b of the swing end 18a of the swing link 18 through which it is inserted, Alternatively, a predetermined gap (clearance) is provided to enable swinging.

  In the continuously variable transmission 1B of the present embodiment, among these clearances, the clearance between the connecting pin 19 and the output side annular portion 15b is more than the clearance between the connecting pin 19 and the projecting piece 18b. large. That is, the connecting rod 15 can move more in the direction perpendicular to the axis of the connecting pin 19 than the swing link 18 in relation to the connecting pin 19.

  Therefore, in the continuously variable transmission 1B of the present embodiment, the buffer member 24 is constituted by a disc spring, and the connecting rod 15 having a larger clearance from the connecting pin 19 than the swing link 18 is connected to the disc spring of the buffer member 24. It is comprised so that the edge part of an internal diameter side may contact.

  That is, the continuously variable transmission 1 </ b> B of the present embodiment is based on friction applied from the disc spring of the buffer member 24 to the connecting rod 15 that can move more in the direction perpendicular to the axis of the connecting pin 19 than the swing link 18. It is comprised so that resistance may become small.

  Therefore, the connecting rod 15 is easy to move and the time until the connecting rod 15 and the connecting pin 19 come into contact with each other, that is, the response time in the power transmission is shorter than in the case where the end on the outer diameter side contacts.

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

  For example, in the above embodiment, the connecting rod 15 and the swing link 18 are connected to the insertion hole 18c of the projecting piece 18b of the output end annular portion 15b and the swing end portion 18a with the connecting pin 19 as the swing shaft. By inserting the pin 19, it is connected so that relative rotation is possible.

  However, the swing shaft of the present invention is not limited to such a connecting pin 19 as long as the connecting rod and the swing link are connected so as to be relatively rotatable. For example, a shaft portion formed on one of the connecting rod and the swing link may be used as a swing shaft, and the shaft portion may be inserted into a hole formed on the other.

  Moreover, in the said embodiment, the buffer members 23 and 24 are comprised by the disk spring. However, the buffer member of the present invention is a buffer member other than a disc spring, such as a coil spring, a leaf spring, rubber, or the like, as long as it can maintain the clearance between the swing link and the connecting rod. But you can.

  Moreover, in the said 1st Embodiment, the buffer member 23 is comprised by two disc springs 23a and 23b. However, when the buffer member of the present invention is constituted by a disc spring, it is constituted by three or more disc springs as long as the portion contacting the connecting rod and the swing link is arranged to be an end on the inner diameter side. May be.

  Moreover, in the said 2nd Embodiment, the buffer member 24 is comprised by one disc spring. However, when the shock-absorbing member of the present invention is configured by a disc spring, the portion of the swing link and the connecting rod that contacts the member having a large clearance with the connecting pin is disposed so as to be the end on the inner diameter side. If so, it may be constituted by two or more disc springs.

  In the second embodiment, the clearance between the output side annular portion 15 b of the connecting rod 15 and the connecting pin 19 is such that the protruding piece 18 b of the swing end portion 18 a of the swing link 18 and the connecting pin 19 Since the clearance is larger than the clearance, the disc spring as the buffer member 24 is arranged so that the end portion on the inner diameter side contacts the output-side annular portion 15b. However, the arrangement of the disc springs in the present invention is not limited to such a configuration.

  For example, when the clearance between the output-side annular portion 15b and the connecting pin 19 is smaller than the clearance between the protruding piece 18b of the swinging end portion 18a and the connecting pin 19, a disc spring which is a buffer member 24 is used. It is preferable that the inner end of the swinging end 18a is in contact with the protruding piece 18b.

DESCRIPTION OF SYMBOLS 1A, 1B ... Continuously variable transmission, 2 ... Input part, 3 ... Output shaft, 4 ... Turning radius adjustment mechanism, 5 ... Cam disk (cam part), 5a ... Through-hole, 5b ... Notch hole, 6 ... Rotating disk ( Rotating part), 6a ... receiving hole, 6b ... internal teeth, 7 ... pinion shaft, 7a ... pinion, 7b ... pinion bearing, 8 ... differential mechanism, 14a ... rotating shaft, 9 ... sun gear, 10 ... first ring gear, 11 2nd ring gear, 12 ... Stepped pinion, 12a ... Large diameter part, 12b ... Small diameter part, 13 ... Carrier, 14 ... Actuator (adjusting drive source (sub drive source)), 15 ... Connecting rod, 15a ... Input side Annular part, 15b ... Output side annular part, 16 ... Connecting rod bearing, 17 ... One-way clutch (one-way rotation prevention mechanism), 18 ... Oscillating link, 18a ... Oscillating end, 18b ... Projection piece, 18c ... Insertion Hole, 19 Connecting pin (rocking shaft), 20 lever lever mechanism, 21 transmission case, 21a one end wall portion, 21b other end wall portion, 21c peripheral wall portion, 22 bearing, 23, 24 buffer member, 23a , 23b ... disc spring, 50 ... insertion hole, ENG ... engine (driving drive source (main drive source)), h ... gear ratio, P1 ... rotation axis of the input shaft, P1a ... input shaft in the undriven state , P2..., The center of the rotating disk 6 (input side fulcrum), P4... The center of the connecting pin 19 (output side fulcrum), P5. ... rotation center axis of the output shaft 3 in a non-driven state, Rx ... distance between P1 and P2, Ry ... distance between P2 and P3, R1 ... distance between P1 and P3 (eccentricity, center P3 of the rotary disk 6 (input) Side fulcrum) turning radius), R2 Distance P4 and P5 (the length of the swing link 18), .theta.1 ... rotational radius adjusting mechanism 4 of the phase, .theta.2 ... swing range of the swing link 18.

Claims (4)

An input shaft to which the driving force of the driving source for traveling is transmitted;
An output shaft disposed parallel to the rotation center axis of the input shaft;
A rotating part that is rotatable about the rotation center axis of the input shaft is provided and a turning radius adjusting mechanism that can adjust the turning radius of the rotating part is provided, and a swinging end is provided to swing freely on the output shaft. A supported swinging link, and a connecting rod having one end rotatably connected to the rotating part of the turning radius adjusting mechanism and the other end connected to the swinging end of the swinging link. A lever crank mechanism for converting the rotational motion of the input shaft into the swing motion of the swing link;
When the swing link is about to rotate to one side, the swing link is fixed to the output shaft, and when the swing link is about to rotate to the other side, the swing link is idle with respect to the output shaft. A continuously variable transmission including a one-way rotation prevention mechanism,
The swing end portion of the swing link and the other end portion of the connecting rod are coupled by a swing shaft so as to be relatively rotatable,
A cushioning member for urging the swing link or the connecting rod in the axial direction of the swing shaft is disposed between the swing end and the other end. Step transmission. The continuously variable transmission according to claim 1,
The buffer member is constituted by a plurality of disc springs,
The continuously variable transmission is characterized in that the plurality of disc springs are arranged in combination with the swing link and the connecting rod so that the inner diameter side end portion is in contact with the swing link and the connecting rod. The continuously variable transmission according to claim 1,
The swing link and the connecting rod have a clearance between the swing shaft and
The buffer member is constituted by a disc spring,
The disc spring is disposed such that an end on the inner diameter side contacts a member having a large clearance from the swing shaft of the swing link or the connecting rod. Step transmission. The continuously variable transmission according to any one of claims 1 to 3,
A plurality of lever crank mechanisms; a transmission case that houses the lever crank mechanisms and the one-way rotation prevention mechanism;
A plurality of bearings attached to the transmission case and rotatably supporting one end side or the other end side of the input shaft or the output shaft;
With
The continuously variable transmission is characterized in that the buffer member has a higher spring constant as the buffer member is closer to the bearing.