JP5702249B2 - Four-bar linkage type continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission with a four-bar link mechanism that can change speed by adjusting the amount of eccentricity with an eccentric mechanism provided on an input shaft.

  Conventionally, an input shaft to which driving force from a driving source such as an engine provided in a vehicle is transmitted, an output shaft arranged in parallel to the input shaft, a plurality of eccentric mechanisms provided on the input shaft, and an output shaft A plurality of oscillating links that are pivotally supported on one end, an input-side annular portion that is rotatably fitted to an eccentric mechanism at one end, and the other end oscillating the oscillating link. A four-bar linkage type continuously variable transmission including a connecting rod connected to an end is known (see, for example, Patent Document 1 and Patent Document 2).

  In Patent Document 1 and Patent Document 2, each eccentric mechanism includes a cam disk provided eccentrically on the input shaft and a rotating disk provided eccentrically on the cam disk and rotatably provided. A one-way clutch is provided between the swing link and the output shaft. The one-way clutch fixes the swing link to the output shaft when the swing link is about to rotate relative to the output shaft, and To idle the swing link.

  Each cam disk includes a through-hole penetrating in the axial direction of the input shaft and a notch hole provided at a position facing the eccentric direction with respect to the input shaft and communicating the outer peripheral surface of the cam disk with the through-hole. Further, the notch hole is provided from one end surface in the axial direction of the cam disk to the other end surface (see FIGS. 2 and 3 of Patent Document 2). Adjacent cam disks are fixed with bolts, thereby forming a cam disk coupling body. One end in the axial direction of the cam disk coupling body is coupled to the input shaft, and the cam disk coupling body and the input shaft constitute a cam shaft.

  The cam disk coupling body is hollow by connecting through holes of the cam disks, and a pinion shaft is inserted therein. The inserted pinion shaft is exposed from the notch hole of each cam disk. The rotating disk is provided with a receiving hole for receiving the camshaft. Internal teeth are formed on the inner peripheral surface of the rotating disk that forms the receiving hole.

  The internal teeth mesh with the pinion shaft exposed from the notch hole of the camshaft. When the input shaft and the pinion shaft are rotated at the same speed, the eccentric amount of the eccentric mechanism is maintained. When the rotational speeds of the input shaft and the pinion shaft are made different, the eccentric amount of the eccentric mechanism is changed, and the transmission gear ratio is changed.

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

  The eccentric direction of the cam disk of each eccentric mechanism is set so as to make a round around the input shaft with different phases. Therefore, the swinging link sequentially transmits the torque to the output shaft by the connecting rod fitted to each eccentric mechanism, so that the output shaft can be smoothly rotated.

JP-T-2005-502543 German Patent Application Publication No. 102009039993

  The four-bar linkage type continuously variable transmission receives the load applied from the connecting rod by the camshaft. Here, in the four-bar linkage mechanism type continuously variable transmission in which the pinion shaft is inserted into the camshaft as in Patent Document 1 and Patent Document 2, the pinion shaft and the internal teeth of the rotating disk are meshed with the camshaft. It is necessary to provide a notch hole. However, the inventor of the present application has found a problem that the rigidity of the camshaft is low because the load applied from the connecting rod is received at the portion where the notch hole of the camshaft is provided. In a four-bar linkage type continuously variable transmission, if the camshaft is low in rigidity, that is, if the camshaft bends, the eccentricity of the eccentric mechanism changes, so there is a difference between the gear ratio command value and the actual gear ratio. May occur, which causes problems in the merchantability and controllability of the transmission.

  In view of the above, an object of the present invention is to provide a four-bar link mechanism type continuously variable transmission that can improve the rigidity of a camshaft.

  [1] In order to achieve the above object, a four-bar linkage type continuously variable transmission according to the present invention includes an input shaft to which a driving force from a driving source is transmitted, and an output shaft disposed in parallel with the input shaft. A lever crank mechanism that is connected to the input shaft and the output shaft and converts a rotational motion of the input shaft into a swing motion on the output shaft side, and a pinion shaft that is concentrically disposed with the input shaft. The lever crank mechanism includes a cam disk provided eccentrically with respect to the input shaft, an eccentric mechanism having a rotary disk provided eccentrically with respect to the cam disk, and swinging about the output shaft. A swing link that is pivotally supported, an input-side annular portion that is rotatably fitted to the eccentric mechanism at one end, and the other end is a swing end of the swing link A connecting rod to be coupled, The swing link is fixed to the output shaft when it is about to rotate relative to the output shaft between the output shaft and the output shaft. A one-way rotation preventing mechanism for idly rotating the swing link with respect to the shaft is provided, and the input shaft and the cam disk constitute a cam shaft.

The camshaft is hollow, the pinion shaft is inserted into the camshaft, and a notch hole is formed in the camshaft at a location facing the eccentric direction of the cam disk. The pinion shaft extends from the notch hole. The rotating disk is provided with a receiving hole for receiving the input shaft and the cam disk, and an inner tooth is formed on an inner peripheral surface of the rotating disk forming the receiving hole. By engaging the pinion shaft exposed from the notch hole of the input shaft and rotating the input shaft and the pinion shaft at the same speed, the eccentric amount of the eccentric mechanism is maintained, and the input shaft and the pinion shaft By varying the rotational speed of the eccentric mechanism, the eccentric amount of the eccentric mechanism is changed to control the gear ratio, and the camshaft is formed with the notch hole. Part cylindrical portion is provided at an end portion in the axial direction of, receiving cylindrical part of the load from the connecting rod through the rotary disk, said lever crank mechanism is provided in plurality, the plurality of the cam disc the The spline teeth that are spline-coupled to the input shaft and formed at a plurality of locations for fixing the plurality of cam disks provided on the input shaft are set to have the same phase, and the number of teeth is set to the number of teeth. It is set to a multiple of the number of lever crank mechanism and said Rukoto.

  According to the present invention, since it is possible to receive a load from the connecting rod transmitted through the rotating disk at the cylindrical portion, the load is received only at a portion provided with a notch hole like a conventional camshaft. In comparison, the rigidity of the camshaft can be improved.

  [2] In the present invention, the cam disk may be configured separately from the input shaft and supported by the input shaft. With this configuration, the cam disk can be aligned with the input shaft. Therefore, even if the cam disk is molded by casting or the like to improve mass productivity, the deterioration of the eccentric accuracy of the cam disk is prevented, and the camshaft is molded by the machining process with low mass productivity. It can be as much as the case.

[3] In the present invention, the phase of the eccentric direction with respect to the input shaft of each cam disk may be varied, and the phase of the notch hole provided in the input shaft may also be varied . I to this lever, it is possible to rotate the output shaft smoothly.

[4] In the present invention, a plurality of cam disks are splined to the input shaft, and the spline teeth formed at a plurality of positions for fixing the plurality of cam disks provided on the input shaft have the same phase. And the number of teeth is set to a multiple of the number of lever crank mechanisms .

  According to this configuration, the spline teeth of the cam disks having different eccentric directions can be formed in the same phase, and the shapes of the cam disks can be the same. For this reason, there is no need to have a different shape for each cam disk, and the lever crank mechanism can be easily manufactured.

Sectional drawing which shows embodiment of the four-bar linkage mechanism type continuously variable transmission of this invention. The perspective view which decomposes | disassembles and shows the input shaft, pinion shaft, and eccentric mechanism of this embodiment. Sectional drawing which shows typically the input shaft and cam disk of this embodiment. Explanatory drawing which shows the lever crank mechanism of this embodiment from an axial direction. Explanatory drawing explaining the change of the eccentric amount of the eccentric mechanism of this embodiment. It is explanatory drawing which shows the relationship between the change of the eccentric amount of the eccentric mechanism of this embodiment, and the range of the rocking | fluctuation motion of a rocking | fluctuation link, (a) is the maximum amount of eccentricity, (b) is the amount of eccentricity, (C) shows the swing range of the swing link when the amount of eccentricity is small. The graph which shows the change of the angular velocity of a rocking | fluctuation link with respect to the change of the eccentric amount of the eccentric mechanism of this embodiment. 6 is a graph showing a state in which the output shaft is rotated by six lever crank mechanisms each having a phase difference of 60 degrees in the continuously variable transmission of the present embodiment.

  Embodiments of a four-bar linkage type continuously variable transmission according to the present invention will be described below. The continuously variable transmission according to the present embodiment is a transmission capable of setting the speed ratio i (i = rotational speed of the input shaft / rotational speed of the output shaft) to infinity (∞) and the rotational speed of the output shaft to “0”. It is a kind of so-called Infinity Variable Transmission (IVT).

  1 to 4, a continuously variable transmission 1 according to the present embodiment receives an input central axis P1 (by receiving rotational power from a drive source for a vehicle such as an engine or an electric motor, which is an internal combustion engine not shown). (See FIG. 4) A hollow input shaft 2 that rotates around the center of the input shaft 2 and the input shaft 2 are arranged in parallel, and the rotational power is transmitted to the drive wheels (not shown) of the vehicle via a differential gear, a propeller shaft, etc., not shown. An output shaft 3 to be operated, and six eccentric mechanisms 4 provided on the input shaft 2.

  Each eccentric mechanism 4 includes a cam disk 5 and a rotating disk 6 that are separate from the input shaft 2. The cam disk 5 is configured in a disk shape having a large diameter portion 51, a small diameter portion 52, and a through hole 53 that passes through the input shaft 2 concentrically. The cam disk 5 is fixed to the input shaft 2 by a pair of splines so that the input shaft 2 is inserted into the through hole 53 and is eccentric from the input center axis P1 and rotates integrally with the input shaft 2. Has been. One set of cam disks 5 of each eccentric mechanism 4 is arranged so that the phases thereof are sequentially changed by 60 degrees so that the six sets of cam disks 5 make a round in the circumferential direction of the input shaft 2.

  The input shaft 2 has spline teeth 2c (see FIG. 2) for fixing the cam disks 5 between the notches 2a in the axial direction corresponding to the cam disks 5 (parts on both sides of the notch 2a in the axial direction). A plurality are provided to be located in All the spline teeth 2c are formed in the same phase, and the number of teeth is set to a multiple of the number of the eccentric mechanisms 4 (that is, a multiple of 6). Thereby, the shape of each cam disk 5 including the spline teeth of the cam disk 5 coupled with the spline teeth 2c of the input shaft 2 can be formed identically. Fixing and positioning are easy.

  In the present embodiment, the portion of the input shaft 2 where the spline teeth 2c are provided and the large-diameter portion 51 of the cam disk 5 correspond to the cylindrical portion of the present invention.

  As shown in FIGS. 2 and 3, each set of cam disks 5 is fixed with a long bolt 5a in a state where two sets of adjacent cam disks 5 are overlapped so that the small diameter portions 52 face each other. ing. That is, each set of the cam disks 5 other than the two sets of cam disks 5 positioned at both ends in the axial direction is fixed by the two long bolts 5a. Two sets of cam disks positioned at both ends in the axial direction are fixed by one long bolt 5a and one short bolt 5b, respectively. With this configuration, there is no need to separately provide bolts for connecting the cam disks 5 of the adjacent eccentric mechanisms 4, and the number of parts can be reduced to reduce costs.

  In the present embodiment, the input shaft 2 and the six sets of cam disks 5 constitute a camshaft.

  Further, each set of cam disks 5 has a disk-shaped rotating disk 6 provided with a receiving hole 6a for receiving the cam disk 5 and is rotatable with respect to the cam disk 5 via an eccentric mechanism bearing 4a. It is fitted. In the rotating disk 6, the center point of the cam disk 5 is P2, the center point of the rotating disk 6 is P3, the distance Ra between the input center axis P1 and the center point P2, and the distance Rb between the center point P2 and the center point P3 are the same. So that it is eccentric with respect to the cam disk 5.

  Inner teeth 6b are provided in the receiving hole 6a of the rotating disk 6 so as to be positioned between the pair of cam disks 5 (at a position corresponding to the small diameter portion 52). The input shaft 2 is positioned between the pair of cam disks 5 (at a position corresponding to the small diameter portion 52), and the inner peripheral surface and the outer peripheral surface are communicated with each other at a location facing the eccentric direction of the cam disk 5. A notch hole 2a is formed. The small diameter portion 52 of the cam disk 5 is also formed with a notch hole 52 a corresponding to the notch portion 2 a of the input shaft 2 and communicating with the outer peripheral surface of the small diameter portion 52 and the inner peripheral surface of the through hole 53.

  The input shaft 2 is pivotally supported by the transmission case 1a via an input shaft bearing 2b. The input shaft bearing 2b is press-fitted into a hole provided in the transmission case 1a. The input shaft 2 is press-fitted into the input shaft bearing 2b. The input shaft bearing 2b or the input shaft 2 may be fitted to the transmission case 1a or the input shaft bearing 2b so as to have a very small gap. The adjustment accuracy of the gear ratio of the step transmission 1 is improved.

  In the hollow input shaft 2, a pinion shaft 7 that is arranged concentrically with the input shaft 2 and has external teeth 7 a at positions corresponding to the internal teeth 6 b of the rotary disk 6 is rotatable relative to the input shaft 2. Has been placed. The external teeth 7 a of the pinion shaft 7 mesh with the internal teeth 6 b of the rotating disk 6 through the cutout holes 2 a of the input shaft 2.

  A differential mechanism 8 is connected to the pinion shaft 7. The differential mechanism 8 is configured by a planetary gear mechanism, and includes a sun gear 9, a first ring gear 10 connected to the input shaft 2, a second ring gear 11 connected to the pinion shaft 7, a sun gear 9 and A carrier 13 is provided that supports a stepped pinion 12 including a large-diameter portion 12a that meshes with the first ring gear 10 and a small-diameter portion 12b that meshes with the second ring gear 11 so as to rotate and revolve freely.

  The sun gear 9 is connected to a rotating shaft 14 a of an actuator 14 that is an electric motor for the pinion shaft 7. When the rotational speed of the actuator 14 is the same as the rotational speed of the input shaft 2, the sun gear 9 and the first ring gear 10 rotate at the same speed, and the sun gear 9, the first ring gear 10, the second ring gear 11, and the like. The four elements of 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 rotates at the same speed as the input shaft 2.

  When the rotational speed of the actuator 14 is made slower than the rotational speed of the input shaft 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 The number of rotations of the carrier 13 is (j · Nr1 + Ns) / (j + 1) where j is the number of teeth of the ring gear 10 / the number of teeth of the sun gear 9). The gear ratio between the sun gear 9 and the second ring gear 11 ((number of teeth of the second ring gear 11 / number of teeth of the sun gear 9) × (number of teeth of the large diameter portion 12a of the stepped pinion 12 / tooth of the small diameter portion 12b) (Number)) is k, the rotation speed of the second ring gear 11 is {j (k + 1) Nr1 + (k−j) Ns} / {k (j + 1)}.

  When the rotational speed of the input shaft 2 to which the cam disk 5 is fixed and the rotational speed of the pinion shaft 7 are the same, the rotating disk 6 rotates together with the cam disk 5. When there is a difference between the rotational speed of the input shaft 2 and the rotational speed of the pinion shaft 7, the rotating disk 6 rotates the periphery of the cam disk 5 around the center point P <b> 2 of the cam disk 5.

  As shown in FIG. 4, the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance Ra and the distance Rb are the same, and therefore the center point P3 of the rotating disk 6 is the same as the input center axis P1. The distance between the input center axis P1 and the center point P3, that is, the amount of eccentricity R1 can be set to “0” so as to be positioned on the axis.

  On the periphery of the rotating disk 6, a connecting rod 15 is provided with an input-side annular portion 15a having a large diameter at one end and an output-side annular portion 15b having a smaller diameter than the diameter of the input-side annular portion 15a at the other end. The input side annular portion 15a is rotatably fitted via a roller bearing 16 for the connecting rod. The output shaft 3 is provided with six swing links 18 corresponding to the connecting rod 15 via a one-way clutch 17 as a one-way rotation prevention mechanism.

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

  FIG. 5 shows the positional relationship between the pinion shaft 7 and the rotating disk 6 in a state where the eccentric amount R1 of the eccentric mechanism 4 is changed. FIG. 5A shows a state in which the amount of eccentricity R1 is “maximum”, so that the input center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotating disk 6 are aligned. The pinion shaft 7 and the rotating disk 6 are located. At this time, the gear ratio i is minimized.

  FIG. 5B shows a state where the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 5A, and FIG. 5C shows that the eccentric amount R1 is smaller than that in FIG. Is shown. The gear ratio i is “medium” which is larger than the gear ratio i in FIG. 5A in FIG. 5B, and “large” which is larger than the gear ratio i in FIG. 5B in FIG. Become. FIG. 5D shows a state where the amount of eccentricity R1 is “0”, and the input center axis P1 and the center point P3 of the rotary disk 6 are located concentrically. The gear ratio i at this time is infinite (∞).

  As shown in FIG. 4, the eccentric mechanism 4, the connecting rod 15, and the swing link 18 of the present embodiment constitute a lever crank mechanism 20. The continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20. When the input shaft 2 is rotated and the pinion shaft 7 is rotated at the same speed as the input shaft 2 when the eccentric amount R1 is not “0”, each connecting rod 15 changes the phase amount R1 while changing the phase by 60 degrees. On the basis of the above, the pushing to the output shaft 3 side and the pulling to the input shaft 2 side are repeated alternately between the input shaft 2 and the output shaft 3.

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

  6A shows the case where the eccentric amount R1 is “maximum” in FIG. 5A (when the gear ratio i is the minimum), and FIG. 6B shows the case where the eccentric amount R1 is “ FIG. 6C shows the case where the eccentric amount R1 is “small” in FIG. 5C (when the gear ratio i is large). The swing range θ2 of the swing link 18 with respect to the rotational movement of the eccentric mechanism 4 is shown. As is apparent from FIG. 6, as the amount of eccentricity R1 becomes smaller, the swing range θ2 of the swing link 18 becomes narrower. When the eccentric amount R1 is “0”, the swing link 18 does not swing. In the present embodiment, the position closest to the input shaft 2 in the swing range θ2 of the swing end 18a of the swing link 18 is the internal dead center, and the position farthest from the input shaft 2 is the external dead center. .

  FIG. 7 shows the relationship between changes in the angular velocity ω accompanying changes in the amount of eccentricity R1 of the eccentric mechanism 4 with the rotational angle θ1 of the eccentric mechanism 4 of the continuously variable transmission 1 as the horizontal axis and the angular velocity ω of the swing link 11 as the vertical axis. Indicates. As apparent from FIG. 7, it can be seen that the angular velocity ω of the swing link 11 increases as the eccentric amount R1 increases (the transmission ratio i decreases).

  FIG. 8 shows each swing link with respect to the rotation angle θ1 of the eccentric mechanism 4 when the six eccentric mechanisms 4 having phases different by 60 degrees are rotated at the same speed of the input shaft 2 and the pinion shaft 7. An angular velocity ω of 18 is shown. FIG. 8 shows that the output shaft 3 is smoothly rotated by the six lever crank mechanisms 20.

  According to the four-link mechanism continuously variable transmission 1 of the present embodiment, the camshaft composed of the input shaft 2 and the six sets of cam disks 5 is the axial end of the portion where the cutout holes 2a and 52a are provided. The cylindrical portion (the portion where the spline teeth 2c of the input shaft 2 are provided and the large-diameter portion 51 of the cam disk 5) is included in the portion, and from the connecting rod 15 transmitted through the rotating disk 6 in this cylindrical portion. Can receive a load. Accordingly, the rigidity of the camshaft, that is, the input shaft 2 and the cam disk 5 can be improved as compared with the case where the load from the connecting rod is received only at the portion where the notch hole is provided as in the conventional camshaft. it can.

  Further, according to the four-bar linkage type continuously variable transmission of the present embodiment, the cam disks 5 of the eccentric mechanisms 4 are fixed to the input shaft 2, so that the centering of the cam disks 5 is performed by the input shaft 2. be able to. In addition, since each cam disk 5 is connected by the input shaft 2, when changing the phase angle of each cam disk 5, it is not necessary to change the mold for forming the cam disk 5, and a set of adjacent ones. It is only necessary to change the drilling positions of the holes for the bolts 5a and 5b between the cam disks 5. For this reason, the phase angle can be changed relatively easily. Therefore, the cam disk 5 and the input shaft 2 can be manufactured with high accuracy, and the degree of freedom in layout of the four-bar linkage mechanism type continuously variable transmission 1 can be increased.

  By the way, in general, the input shaft of the four-bar linkage mechanism type continuously variable transmission is easily bent because a large load is applied from the connecting rod through the eccentric mechanism. Since the four-bar link mechanism type continuously variable transmission changes the gear ratio by adjusting the amount of eccentricity of the eccentric mechanism, the accuracy of adjusting the gear ratio decreases when the input shaft is bent.

  According to the four-bar linkage mechanism continuously variable transmission 1 of the present embodiment, adjacent cam disks 5 are connected to each other with different phases. When the input shaft 2 bends, each pair of cam disks 5 tends to open, but since the adjacent pair of cam disks 5 of the present embodiment are connected to each other, each pair of cam disks 5 Opening between the disks 5 is prevented. Therefore, the input shaft 2 becomes difficult to bend, and the deflection of the input shaft 2 can be suppressed while maintaining the diameter without reducing the degree of freedom of layout and without increasing the diameter of the input shaft 2.

  Each set of cam disks 5 is arranged on the input shaft 2 so that the phase difference between the adjacent sets of cam disks 5 is reduced. For this reason, the overlapping region between adjacent sets of cam disks 5 increases, and it becomes easy to make a hole for inserting a long bolt 5a for connecting adjacent sets of cam disks 5. Further, since the phase difference between the adjacent cam disks 5 is constant, the shape of the cam disks 5 and the positions of the holes for the bolts 5a and 5b can be configured in the same way. Easy to manufacture.

  In this embodiment, the one-way clutch 17 is used as the one-way rotation prevention mechanism. However, the one-way rotation prevention mechanism of the present invention is not limited to this, and torque from the swing link 18 to the output shaft 3 is not limited. May be configured by a two-way clutch (two-way clutch) configured to be able to switch the rotation direction of the swing link 18 capable of transmitting the rotation with respect to the output shaft 3.

  In the present embodiment, the transmission is described as being used for a vehicle such as an automobile. However, the four-bar link continuously variable transmission according to the present invention is not limited to this, and is used for, for example, a ship. May be.

  In the present embodiment, the cam disk 5 is separated from the input shaft 2. However, the present invention is not limited to this, and the cam disk and the input shaft are integrated into one member as long as the cylindrical portion is provided. The camshaft may be configured with. Further, without supporting the cam disk 5 by the input shaft 2, for example, by connecting the large diameter portions 51 as the cylindrical portions of the cam disks 5 of the adjacent eccentric mechanism 4 to face each other in the axial direction, the cam disk is connected. The camshaft may be configured by configuring the body and connecting the end of the cam disk coupling body to the end of the input shaft. Even if comprised in this way, the load of the connecting rod 15 can be received by the cylindrical part of a camshaft, and the effect of this invention that the rigidity of a camshaft can be improved can be acquired.

DESCRIPTION OF SYMBOLS 1 ... Four-joint link mechanism type continuously variable transmission, 2 ... Input shaft, 2a ... Notch hole, 2b ... Input shaft bearing, 2c ... Spline tooth (cylindrical part), 3 ... Output shaft, 4 ... Eccentric mechanism, 4a ... Bearing for eccentric mechanism, 5 ... cam disk, 5a ... long bolt, 5b ... short bolt, 51 ... large diameter part, 52 ... small diameter part, 52a ... notch hole, 53 ... through hole, 6 ... rotating disk, 6a ... receiving hole 6b ... internal teeth, 7 ... pinion shaft, 7a ... external teeth, 15 ... connecting rod, 15a ... input-side annular portion, 17 ... one-way clutch (one-way rotation prevention mechanism), 18 ... rocking link, 18a ... rocking Moving end, 20 ... leverage crank mechanism.

Claims (3)

An input shaft to which the driving force from the driving source is transmitted;
An output shaft arranged parallel to the input shaft;
A lever crank mechanism connected to the input shaft and the output shaft, and converting the rotational motion of the input shaft into a swing motion on the output shaft side;
A pinion shaft disposed concentrically with the input shaft,
The lever crank mechanism
An eccentric mechanism having a cam disk provided eccentrically with respect to the input shaft, and a rotating disk provided eccentrically with respect to the cam disk and rotatable;
A swing link pivotally supported by the output shaft;
A connecting rod having an input-side annular portion rotatably fitted to the eccentric mechanism at one end, and the other end connected to the swing end of the swing link;
With
When the swing link is fixed to the output shaft and is relatively rotated to the other side when attempting to rotate relative to the output shaft between the swing link and the output shaft. Is provided with a one-way rotation prevention mechanism that idles the swing link with respect to the output shaft,
A camshaft is constituted by the input shaft and the cam disk,
The camshaft is hollow, and the pinion shaft is inserted therein,
The camshaft is formed with a notch hole at a location facing the eccentric direction of the cam disk, and the pinion shaft is exposed from the notch hole,
The rotating disk is provided with a receiving hole for receiving the input shaft and the cam disk,
Inner teeth are formed on the inner peripheral surface of the rotating disk that forms the receiving hole,
The inner teeth mesh with the pinion shaft exposed from the notch hole of the input shaft,
The eccentric amount of the eccentric mechanism is maintained by rotating the input shaft and the pinion shaft at the same speed, and the eccentric amount of the eccentric mechanism is changed by changing the rotational speeds of the input shaft and the pinion shaft. Control the gear ratio,
The camshaft is provided with a cylindrical portion at the end in the axial direction of the portion where the cutout hole is formed,
The cylindrical portion receives a load from the connecting rod through the rotating disk ,
A plurality of the lever crank mechanisms are provided,
The plurality of cam disks are splined to the input shaft, respectively.
The spline teeth formed at a plurality of positions for fixing the plurality of cam disks provided on the input shaft are set to have the same phase, and the number of teeth is a multiple of the number of the lever crank mechanisms. set four-bar linkage mechanism type continuously variable transmission according to claim Rukoto. A four-bar linkage type continuously variable transmission according to claim 1,
4. The four-bar linkage mechanism continuously variable transmission, wherein the cam disk is separate from the input shaft and is supported by the input shaft. A four-bar linkage type continuously variable transmission according to claim 1 or 2 ,
Before SL cam disc, the eccentric direction of the phase respectively made different, the four-bar linkage type continuously variable transmission, characterized in that to vary also the notch holes phase.