JP6046648B2 - Silent chain and continuously variable transmission mechanism using the same - Google Patents

Description

  The present invention relates to a silent chain used for power transmission and a continuously variable transmission mechanism that transmits power using the silent chain.

  Conventionally, a belt type continuously variable transmission in which a driving belt is wound around a primary pulley and a secondary pulley, and power is transmitted using a frictional force generated between each pulley and the driving belt by a thrust applied to the movable sheave of each pulley. However, it has been put to practical use as a vehicle transmission, for example.

In such a continuously variable transmission, when transmitting a large amount of power, it is necessary to increase the thrust to ensure a frictional force. At this time, the load on the drive source (engine or electric motor) that drives the oil pump for generating thrust increases, which may lead to an increase in fuel consumption or power consumption, and each pulley. And the durability of the drive belt may be impaired.
Therefore, a continuously variable transmission mechanism has been developed that transmits power by using a plurality of pinion sprockets and a chain wound around the pinion sprocket without using the above thrust and frictional force.

As such a continuously variable transmission mechanism, a plurality of pinion sprockets which are supported so as to rotate in a radial direction and integrally rotate while maintaining an equal distance from the rotating shaft and revolve around the rotating shaft are polygonal. Apparent large sprockets (herein referred to as “composite sprockets”) formed so as to form the vertices are provided on the input side and the output side, respectively, and are wound around these composite sprockets. The one that transmits power by a chain. Under such a configuration, each pinion sprocket moves synchronously in the radial direction while maintaining an equal distance with respect to the rotating shaft, and the size of the polygon changes in a similar manner. Change.
Such continuously variable transmission mechanisms are disclosed in Patent Documents 1 and 2, for example.

U.S. Pat. No. 7,713,154 JP 2002-250420 A

  By the way, a roller chain is mentioned as a chain which transmits motive power. The roller chain has an inner link and an outer link in which a pair of pin holes are formed along the power transmission direction, and power transmission in one pin hole and outer link on the upstream side and the downstream side in the power transmission direction in the inner link. A common link pin is passed through and connected to the other pin hole on the upstream side and the downstream side in the direction to form an annular shape. A roller is provided on the outer periphery of each link pin, and this roller engages with the sprocket. However, when the power is transmitted from the roller chain, there is a possibility that the silence cannot be ensured due to a collision when the roller and the sprocket are engaged.

Therefore, a silent chain with improved silence has been developed.
In the silent chain, a large number of link plates arranged in series in the power transmission direction are connected by connecting pins. Each link plate is formed with a pair of teeth along the power transmission direction, and the sprocket engages with a groove formed between these teeth. That is, since the silent chain is engaged so that the sprocket and the tooth portion of the link plate slide, the collision at the time of engagement between the chain and the sprocket is buffered to improve the quietness.

  When such a silent chain is applied to a continuously variable transmission mechanism as exemplified in Patent Documents 1 and 2, the silent chain between the pinion sprockets is brought into contact with the guide rod in order to make the winding track of the chain as close to a circle as possible. It is possible to guide them in contact.

  Specifically, as shown in FIG. 8, auxiliary link plates 163 are disposed at both ends in the thickness direction of the link plate 61 connected by the connecting pins 62 and having a pair of teeth 61 a, and the auxiliary link plate 163. It is conceivable that the guide rod 29 is brought into contact with the guide rod 29. Each auxiliary link plate 163 needs to be spaced apart in the power transmission direction so as to correspond to the expansion / contraction diameter of the chain winding radius. However, when the auxiliary link plate 163 is spaced apart in the power transmission direction, the inner peripheral surface 163a of the auxiliary link plate 163 becomes discontinuous, and the guide rod 29 is located at a location 166 where the auxiliary link plate 163 is separated. There is a risk of getting caught or stuck. As a result, it may be difficult to generate vibrations and ensure quietness.

One of the objects of the present invention was created in view of the above-described problems, and is to provide a silent chain and a continuously variable transmission mechanism using the silent chain that can ensure quietness. .
Note that the present invention is not limited to this purpose, and other effects of the present invention can also be achieved by the functions and effects derived from the respective configurations shown in the embodiments for carrying out the invention which will be described later. Can be positioned as

(1) In order to achieve the above object, the silent chain of the present invention has a plurality of link plates formed in the inner peripheral side with a pair of tooth portions and having a pair of pin holes in series in the power transmission direction and in the thickness direction. Ri Na are connected by the inserted connecting pin into the pin bore are arranged on a plurality parallel, a silent chain winding radius is enlarged or reduced, straight or on the inner circumferential side not provided with the teeth A plurality of auxiliary link plates each having an arcuate guide surface and a pair of pin holes through which the connecting pins are inserted are arranged at the outermost side in the thickness direction of the link plates arranged in the plurality and in the power transmission direction. Arranged in series, the inner circumferential side of each of the auxiliary link plates overlaps with the inner circumferential side of the adjacent auxiliary link plate in the thickness direction, and the guide surface is placed in the power transmission direction. It is characterized in that the polymerization unit for connection is formed.

(2) The overlapping portion is formed of a thin portion that is thinned by a notch portion that is notched in the thickness direction, and the thickness of the thin portion and the thickness of the notch portion are set to be equal or approximately equal. preferable.
(3) It is preferable that the overlapping portion is set to overlap without interference at a minimum winding radius.

(4) It is preferable that the overlapping portion is set at a maximum winding radius and the overlapping region is set so that the guide surface is continuous in the power transmission direction.
(5) It is preferable that the guide surface is formed according to an arc shape having a maximum winding radius.
(6) The auxiliary link plate is preferably made of resin.

(7) A continuously variable transmission mechanism according to the present invention is a continuously variable transmission mechanism including two sets of composite sprockets around which the above-described silent chain is wound, and the composite sprocket is a rotation to which power is input or output. A shaft, a plurality of pinion sprockets and guide rods supported movably in a radial direction with respect to the rotation shaft, and the pinion sprockets and the guide rods in a radial direction while maintaining an equal distance from the axis of the rotation shaft A transmission mechanism that moves in synchronization with each other, and changes a gear ratio by changing a contact circle radius that surrounds all of the plurality of pinion sprockets and is in contact with any of the plurality of pinion sprockets. It is characterized by.
(8) Moreover, it is preferable that the silent chain is wound around a plurality of phases with a phase shift in the power transmission direction.

  According to the silent chain and the continuously variable transmission mechanism using the same according to the present invention, the guide surface is powered by overlapping the inner peripheral side of each auxiliary link plate with the inner peripheral side of the adjacent auxiliary link plate in the thickness direction. Since the overlapping part that is continuous in the transmission direction is formed, for example, when the silent chain is guided with the guide rod in contact with the guide surface, the guide surface can be smoothly contacted to ensure quietness can do.

It is radial direction sectional drawing which shows typically the principal part which paid its attention to the composite sprocket and chain of the continuously variable transmission mechanism concerning one Embodiment of this invention. FIG. 3 is an axial cross-sectional view schematically showing a main part focusing on a radial rotation relative rotational drive mechanism such as a pinion sprocket of a continuously variable transmission mechanism according to an embodiment of the present invention. In the continuously variable transmission mechanism according to one embodiment of the present invention, a stationary disk and a movable disk for radial movement such as a pinion sprocket and the support shafts of the pinion sprocket and guide rod moved by these are shown. It is a figure explaining a rod moving mechanism, and the tangent radius becomes large in order of (a), (b), and (c). In addition, the thing with the smallest diameter is shown in (a), and the thing with the largest diameter is shown in (c). It is a perspective view showing typically the principal part of the continuously variable transmission mechanism concerning one embodiment of the present invention. 1 is a perspective view schematically showing a part of a continuously variable transmission mechanism chain to which a silent chain according to an embodiment of the present invention is applied and a guide rod for guiding the chain. FIG. The auxiliary | assistant link plate is shown alone among the chains of the continuously variable transmission mechanism to which the silent chain concerning one Embodiment of this invention is applied, (a) is a front view, (b) is a bottom view. It is a perspective view showing a link plate (drive link) alone among chains of a continuously variable transmission mechanism to which a silent chain according to an embodiment of the present invention is applied. It is a perspective view which shows the silent chain devised in the creation process of this invention.

  Embodiments of the continuously variable transmission mechanism of the present invention will be described below with reference to the drawings. The continuously variable transmission mechanism of the present embodiment is suitable for use in a vehicle transmission. In the present embodiment, the side (revolution shaft side) close to the axis of the rotation shaft in the continuously variable transmission mechanism will be described as the inside, and the opposite side as the outside.

[1. One Embodiment]
Hereinafter, a continuously variable transmission mechanism according to an embodiment will be described.
[1-1. Configuration of continuously variable transmission mechanism]
As shown in FIG. 1, the continuously variable transmission mechanism includes two sets of composite sprockets 5, 5 and a chain 6 wound around these composite sprockets 5, 5. The composite sprocket 5 means an apparent large sprocket in which a plurality of pinion sprockets 20 and a plurality of guide rods 29 whose details will be described later are formed so as to form the apexes of a polygon (here, an octagon). To do.

  One of the two sets of composite sprockets 5 and 5 is a pair of composite sprockets 5 (shown on the left in FIG. 1) that rotate integrally with the input-side rotary shaft 1 (input shaft). , A composite sprocket 5 (shown on the right side in FIG. 1) that rotates integrally with the output-side rotary shaft 1 (output shaft). Since these composite sprockets 5 and 5 are configured in the same manner, the following description will be focused on the composite sprocket 5 on the input side.

The composite sprocket 5 includes a rotating shaft 1, a plurality (three in this case) of pinion sprockets 20 and a plurality of (here, fifteen) guide rods (first here) supported so as to be movable in the radial direction relative to the rotating shaft 1. 1 guide rod) 29. The three pinion sprockets 20 are arranged at equal intervals along the circumferential direction on the circumference around the axis C ₁ of the rotating shaft 1, and five guide rods 29 are interposed between the pinion sprockets 20. Is arranged.

  Although not shown in FIG. 1, the composite sprocket 5 rotates a sprocket moving mechanism 40A that moves a plurality of pinion sprockets 20 and the rotation pinion sprockets 22 and 23 included in the pinion sprocket 20 in conjunction with the sprocket moving mechanism 40A. And a rod moving mechanism 40B that moves the plurality of guide rods 29 (see FIGS. 2 to 5). Details of these will be described later.

This continuously variable transmission mechanism has an outer diameter of an apparent large sprocket formed by the pinion sprocket 20 and the guide rod 29 forming the apex of a polygon (here, an octagon), that is, outside the composite sprocket 5. The gear ratio is changed by changing the diameter (expanded / reduced diameter).
The outer diameter of the composite sprocket 5 is a radius of a circle (tangent circle) that surrounds all of the plurality of pinion sprockets 20 and is in contact with any of the plurality of pinion sprockets 20 (hereinafter referred to as “tangent circle radius”). Corresponding. Further, since the chain 6 is wound around the composite sprocket 5, it can be said that the outer diameter of the composite sprocket 5 corresponds to the contact radius between the plurality of pinion sprockets 20 and the chain 6. Therefore, when the tangent radius or the contact radius is the minimum diameter, the outer diameter of the composite sprocket 5 is the minimum diameter. When the tangent radius or the contact radius is the maximum diameter, the outer diameter of the composite sprocket 5 is the maximum. Is the diameter.

For this reason, it can be said that the continuously variable transmission mechanism changes the gear ratio by changing the tangent radius.
FIG. 1 shows the case where the input side tangent radius is the minimum diameter and the output side tangent radius is the maximum diameter.
Hereinafter, the configuration of the continuously variable transmission mechanism will be described in the order of the composite sprocket 5 and the chain 6 wound around this.

[1-1-1. (Composite sprocket)
In the following description of the configuration of the composite sprocket 5, the pinion sprocket 20, the guide rod 29, the sprocket moving mechanism 40A, the rod moving mechanism 40B, the mechanical rotation driving mechanism 50, and the rotating shaft 1 will be described in this order.
[1-1-1-1. (Pinion sprocket)
Each of the three pinion sprockets 20 is configured as a gear that meshes with the chain 6 and transmits power, and revolves around the axis C ₁ of the rotating shaft 1. Here, “revolution” means that each pinion sprocket 20 rotates around the axis C ₁ of the rotating shaft 1. When the rotating shaft 1 rotates, each pinion sprocket 20 revolves in conjunction with this rotation. That is, the rotation speed of the rotating shaft 1 and the rotation speed of the pinion sprocket 20 are equal. In FIG. 1, a white arrow indicates the counterclockwise revolution direction.

  These pinion sprockets 20 are arranged in one pinion sprocket (hereinafter referred to as “fixed pinion sprocket”) 21 that does not rotate, and the rotational phase of revolution with respect to the fixed pinion sprocket 21 on the advance side and the retard side, respectively. The two rotation pinion sprockets 22 and 23 are capable of rotating. In the following description, the pinion sprocket (advanced side rotation pinion sprocket) provided on the advance side with respect to the fixed pinion sprocket 21 is referred to as a first rotation pinion sprocket 22, and the pinion sprocket provided on the retard side. The (retarded-side rotation pinion sprocket) is called a second rotation pinion sprocket 23 for distinction.

Each of the pinion sprockets 21, 22, and 23 is coupled to support shafts (pinion sprocket shafts) 21a, 22a, and 23a provided at the center thereof. This means that the pinion sprockets 22 and 23 rotate around the axes C ₃ and C _{4 of} the support shafts 22a and 23a. The shaft centers C ₂ , C ₃ , C _{4 of the} support shafts 21 a, 22 a, 23 a and the shaft center C 1 of the rotary shaft ₁ are all parallel to each other.

  The fixed pinion sprocket 21 has a main body portion 21b and teeth 21c partially formed on the outer peripheral portion of the main body portion 21b. In other words, the fixed pinion sprocket 21 is formed with teeth 21c partially protruding in the outer peripheral region that can mesh with the chain 6. In other words, the fixed pinion sprocket 21 has no teeth formed in the outer peripheral region that does not engage with the chain 6.

In FIG. 1, the shape of the portion of the fixed pinion sprocket 21 where the teeth are not formed is illustrated as an arc shape, but the shape is not limited to the arc shape, and various shapes such as a rectangular shape and a triangular shape are illustrated. The shape can be adopted.
Each of the rotation pinion sprockets 22 and 23 has main body portions 22b and 23b and teeth 22c and 23c that are formed so as to protrude from the entire outer periphery of the main body portions 22b and 23b.
As a matter of course, the shape and pitch of the teeth formed on each pinion sprocket 21, 22, 23 are of the same standard.

  As will be described in detail later, the first rotation pinion sprocket 22 rotates clockwise when the tangent radius is expanded, and rotates counterclockwise when the tangent radius is reduced. On the other hand, the second rotation pinion sprocket 23 rotates counterclockwise when the tangent radius is increased, and rotates clockwise when the tangent radius is reduced.

  In the present embodiment, as shown in FIG. 2, each of the rotation pinion sprockets 22 and 23 includes three rows of gears in the axial direction and is not shown, but the fixed pinion sprocket 21 also has three rows of gears in the axial direction. In addition, three chains 6 are also wound around the gears in each row. Thus, each pinion sprocket 21, 22, 23 has three rows of gears in the axial direction. Here, the three rows of gears of each pinion sprocket 20 are provided at a distance from each other via a spacer.

  The number of gear rows of each pinion sprocket 21, 22, 23 depends on the magnitude of the transmission torque of the continuously variable transmission mechanism, but may be two rows, four rows or more, or one row. FIG. 2 schematically shows the first rotation pinion sprocket 22, the second rotation pinion sprocket 23, and a relative rotation drive mechanism 30 described later in the same cross section for easy understanding.

[1-1-1-2. Guide rod)
As shown in FIG. 1, the plurality of guide rods 29 are capable of reducing the variation in the distance between the chain 6 and the axis C ₁ of the rotating shaft 1, that is, allowing the path of the chain 6 around the rotating shaft 1. The chain 6 is guided as close as possible to the circular orbit. The guide rod 29 guides the track of the chain 6 that is in contact with the outer peripheral surface thereof. Since the pinion sprockets 21, 22, 23 and the guide rods 29 are polygonal (substantially regular polygons), the chain 6 abuts on the pinion sprockets 21, 22, 23, and the guide rods 29 on the inside and guides them. While rolling, it rolls along the polygonal shape.

  Each guide rod 29 is obtained by inserting a cylindrical guide member 29b on the outer periphery of a rod support shaft 29a (shown by a broken line in FIG. 1 at only one position), and is supported by the rod support shaft 29a. The chain 6 is guided by the outer peripheral surface of the shaft.

The number of guide rods 29 is not limited to fifteen and may be more or less. In this case, the number of guide rods 29 is preferably a multiple of the number of pinion sprockets 20 (three here). Further, the more the guide rods 29 are provided, the closer the composite sprocket 5 becomes to a perfect circle and the variation in the distance between the chain 6 and the axis C ₁ of the rotary shaft 1 can be reduced. Therefore, it is preferable to set the number of guide rods 29 in consideration of these. Furthermore, the guide rod 29 may be omitted for a simple configuration.

[1-1-1-3. Sprocket moving mechanism, rod moving mechanism and mechanical rotation drive mechanism]
Next, the sprocket moving mechanism 40A, the rod moving mechanism 40B, and the mechanical rotation driving mechanism 50 will be described.
The sprocket moving mechanism 40A has a plurality of pinion sprockets 20 as moving objects, and the rod moving mechanism 40B has a plurality of guide rods 29 as moving objects.

These movement mechanisms 40A, 40B, each moving object (s pinion sprocket 20, a plurality of guide rods 29) for moving in synchronization with the axis C ₁ of the rotary shaft 1 radially while maintaining equidistant It is.
The mechanical rotation drive mechanism 50 causes the rotation of the pinion sprockets 22 and 23 to sprocket so as to eliminate the phase shift of the plurality of pinion sprockets 20 with respect to the chain 6 with the radial movement of the plurality of pinion sprockets 20 by the sprocket moving mechanism 40A. It rotates in conjunction with the moving mechanism 40A.

[1-1-3-1-1. (Prerequisite configuration)
First, with reference to FIG. 2, the premise structure of said mechanism 40A, 40B, 50 is demonstrated. Here, as such a precondition, a fixed disk group 10 that rotates integrally with the rotary shaft 1, a movable disk 19 that is concentrically arranged with respect to the fixed disk group 10 and that can rotate relative to the fixed disk group 10, and the movable disk 19 is fixed to the fixed disk. Each of the relative rotation driving mechanism 30 that rotates relative to the group 10 will be described.

The fixed disk group 10 and the movable disk 19 are provided on both sides of the plurality of pinion sprockets 20 (one side and the other side in the direction along the axis C ₁ of the rotary shaft 1). For this reason, here, the configuration will be described by paying attention to the fixed disk group 10 and the movable disk 19 provided on one side (the upper side in FIG. 2).

[1-1-1-3-1-1. (Fixed disk)
The fixed disk group 10 includes a first fixed disk (radial movement fixed disk) 11 and a second fixed disk (rotation fixed disk) 12 in order from the plurality of pinion sprockets 20 side. These fixed disks 11 and 12 are both formed integrally with the rotary shaft 1 or are coupled so as to rotate integrally with the rotary shaft 1. In FIG. 2, the first fixed disk 11, the movable disk 19 (to be described later), and the second fixed disk 12 are arranged in this order from the plurality of pinion sprockets 20 side.

As shown in FIG. 3, the first fixed disk 11 is formed with two types of radial grooves, a fixed radial groove 11a for a sprocket and a fixed radial groove 11b for a rod (both are provided with a reference numeral only at one location). Yes.
The fixed radial grooves 11a for the sprocket are provided with the number of grooves corresponding to the number of pinion sprockets 20 (here, three), and the fixed radial grooves 11b for the rod are the number of guide rods 29 (here, fifteen). The number of grooves corresponding to is provided.

  Support shafts 21a, 22a, and 23a of pinion sprockets 21, 22, and 23 are inserted into the fixed radial groove 11a for the sprocket, and rod support shafts 29a of the guide rods 29 are inserted into the fixed radial groove 11b for the rod. (Only one place is marked) is interpolated.

As shown in FIGS. 2 and 4, the second fixed disk 12 is formed with guide grooves 12a, 12b, and 12c corresponding to the pinion sprockets 21, 22, and 23, respectively. Specifically, a first guide groove (fixed pinion sprocket guide groove) 12a for guiding the radial movement of the fixed pinion sprocket 21; a second guide groove 12b for guiding the radial movement of the first rotation pinion sprocket 22; A third guide groove 12c that guides the radial movement of the second rotation pinion sprocket 23 is formed. Each of these guide grooves 12a, 12b, 12c is formed along the radial movement path of the corresponding pinion sprocket 21, 22, 23.
In FIG. 4, a counterclockwise revolution direction is indicated by a white arrow.

A helical gear 12 </ b> A is provided on the outer peripheral portion of the second fixed disk 12. The outer peripheral portion of the second fixed disk 12 the helical gear 12A is provided is protruded to have a predetermined length in a direction along the axis C _1, helical gear 12A is provided over a predetermined length .
Here, the “predetermined length” refers to a length corresponding to the advance / retreat amount of the input member 33 in the relative rotation drive mechanism 30 corresponding to the phase difference between the second fixed disk 12 and the movable disk 19 described later. .

[1-1-1-3-1-2. (Movable disc)
As shown in FIG. 3, the movable disk 19 (shown by a broken line) has two types of movable radial grooves, a movable radial groove 19a for a sprocket and a movable radial groove 19b for a rod (each of which is provided with a reference numeral only). Is formed. Although the outer shape of the movable disk 19 is circular and overlaps with the outer shape of the first fixed disk 11 that is circular, the outer circle of the movable disk 19 is shown in a reduced form in FIG. 3 for convenience.

The sprocket movable radial groove 19a intersects the sprocket fixed radial groove 11a, and the support shafts 21a, 22a, and 23a of the pinion sprockets 21, 22, and 23 are located at the intersections. Similarly, the rod movable radial groove 19b intersects the rod fixed radial groove 11b, and the rod support shafts 29a at the intersecting positions are located.
Further, as shown in FIGS. 2 and 4, the movable disk 19 has teeth (hereinafter referred to as “outer peripheral teeth”) 19 </ b> A formed on the entire outer periphery thereof.

[1-1-1-3-1-3. (Relative rotation drive mechanism)
The relative rotation drive mechanism 30 drives the movable disk 19 to rotate relative to the fixed disk group 10. Here, as shown in FIG. 2, the relative rotation drive mechanism 30 meshes with outer peripheral teeth 19 </ b> A formed on the outer periphery of the movable disk 19. The output member 34 having the rotation drive teeth 34 a is rotated to drive the movable disk 19 relative to the fixed disk group 10.

  The relative rotation drive mechanism 30 is driven forward and backward in the axial direction by a linear motion switched by the motion conversion mechanism 32A and a motion conversion mechanism 32A that switches the rotational motion of the output shaft 31a of the motor 31 to a linear motion. Driven fork 32, input member 33 driven to advance and retreat in the axial direction by fork 32, interlocking rotation mechanism 34A for interlocking rotation of input member 33 as input member 33 advances and retracts in the axial direction, and input member 33 and an output member 34 that rotates integrally therewith.

For example, a stepping motor can be used as the motor 31.
The input member 33 is attached to the output member 34 so as to be movable in the axial direction and to rotate integrally. For example, the input member 33 and the output member 34 are attached by spline fitting.

  The input member 33 includes a helical gear 33a that is always meshed with the helical gear 12A provided on the outer peripheral portion of the second fixed disk 12, and a fork groove 33b that sandwiches and slides the fork 32. Further, the output member 34 has output teeth 34 a that always mesh with the outer peripheral teeth 19 </ b> A of the movable disk 19.

  The motion conversion mechanism 32A includes a male screw part 31b formed on the output shaft 31a, a support 32b having a female screw part 32a screwed to the male screw part 31b, to which the fork 32 is coupled, and an outer periphery of the input member 33. And a fork outer peripheral portion 32c that engages in a fork groove 33b formed in the inner surface to restrict the rotation of the fork 32. When the output shaft 31a rotates, the fork 32 whose rotation is regulated moves in the axial direction with respect to the output shaft 31a by screwing the male screw portion 31b and the female screw portion 32a, and the input member 33 is pivoted. Drive in the direction.

  The interlocking rotation mechanism 34A prevents the helical gear 12A provided on the outer periphery of the second fixed disk 12, the helical gear 33a formed on the outer periphery of the input member 33 and meshing with the helical gear 12A, and the output member 34 from moving in the axial direction. The second fixed disk 12 rotationally drives the input member 33 through meshing of the helical gears 12A and 33a as the input member 33 moves in the axial direction.

  According to this relative rotational drive mechanism 30, when the fork 32 is driven forward and backward by the motor 31, the rotational phase of the movable disk 19 is changed with respect to each fixed disk group 10. Thus, the rotational phase difference between the fixed disk group 10 and the movable disk 19 is adjusted in accordance with the amount of advancement and retreat of the fork 32.

[1-1-1-3-2. Sprocket moving mechanism and rod moving mechanism]
Next, the sprocket moving mechanism 40A and the rod moving mechanism 40B will be described with reference to FIGS.
The sprocket moving mechanism 40A includes a first fixed disk 11 formed with fixed radial grooves 11a for sprockets in which support shafts 21a, 22a, and 23a provided in pinion sprockets 21, 22, and 23 are inserted, and a movable sprocket. The movable disk 19 is formed with a radial groove 19 a and a relative rotation drive mechanism 30.

Further, the rod moving mechanism 40B has a relative rotation between the first fixed disk 11 in which the rod fixed radial groove 11b in which the rod support shaft 29a is inserted is formed, the movable disk 19 in which the rod movable radial groove 19b is formed, and relative rotation. And a drive mechanism 30.
As described above, the configurations of the moving mechanisms 40A and 40B are the same except for the support shafts of the respective moving objects.

Next, movement by the moving mechanisms 40A and 40B will be described with reference to FIGS.
FIG. 3 (a) shows that the support shafts 21a, 22a, and 23a of the pinion sprockets 21, 22, and 23 (see FIG. 2 and the like) in the radial grooves 11a and 19a and the rod support shaft 29a in the radial grooves 11b and 19b are the rotation shaft 1. The _one located closest to the axis C1 is shown. In this case, if the rotational phase of the movable disk 19 is changed with respect to the first fixed disk 11 by the relative rotation drive mechanism 30 (see FIG. 2), the fixed radial groove 11a for the sprocket is sequentially changed in the order of FIGS. and the intersection of the sprocket movable radial grooves 19a, and intersection of the rod fixed radial grooves 11b and rod movable radial grooves 19b is away from the axis C ₁ of the rotary shaft 1. That is, the support shaft 21a in these intersections, 22a, 23a, pinions sprocket 20 and the guide rod 29 which is supported to 29a in synchronism from the axis C ₁ of the rotary shaft 1 in a radial direction while maintaining equidistant Moved.

On the other hand, if the direction of change of the rotational phase of the movable disk 19 is reversed by the relative rotational drive mechanism 30 from the above direction, the pinion sprocket 20 and the guide rod 29 approach the axis C ₁ of the rotary shaft 1.
When the input side moving mechanisms 40A and 40B increase the diameter of the contact circle, the output side movement mechanisms 40A and 40B reduce the diameter of the contact circle so that the chain 6 is not loosened or tensioned.

  When the pinion sprocket 20 is moved by the sprocket moving mechanism 40 </ b> A, the distance between the pinion sprockets 20 changes, so that the phase shift of the pinion sprocket 20 with respect to the chain 6 occurs. Therefore, in order to eliminate such a phase shift, a mechanical rotation driving mechanism 50 is provided.

[1-1-1-3-3. Mechanical rotation drive mechanism)
Next, the mechanical rotation driving mechanism 50 will be described with reference to FIGS. 2 and 4. Since the mechanical rotation drive mechanism 50 is configured symmetrically with the pinion sprocket 20 in between, description will be given here focusing on the configuration on one side (the upper side in the drawing of FIG. 2).

As described above, the mechanical rotation drive mechanism 50 rotates the rotation pinion sprockets 22 and 23 so that the phase shift between the pinion sprockets 20 with respect to the chain 6 is eliminated from the sprocket moving mechanism 40A. It is mechanically driven to rotate in conjunction with it.
On the other hand, the mechanical rotation drive mechanism 50 is also for preventing the fixed pinion sprocket 21 from rotating when moving in the radial direction.

First, the structure for preventing the fixed pinion sprocket 21 from rotating about the mechanical rotation drive mechanism 50 will be described.
As shown in FIG. 4, the support shaft 21 a of the fixed pinion sprocket 21 is inserted into the first guide groove 12 a of the second fixed disk 12. A guide member 59 is integrally coupled to the support shaft 21 a of the fixed pinion sprocket 21.

  The guide member 59 is inserted into the first guide groove 12a and guided in the radial direction. The guide member 59 is formed in a corresponding shape so as to contact the first guide groove 12a over a predetermined length in the radial direction. For this reason, when a rotational force that rotates the fixed pinion sprocket 21 is applied, the guide member 59 transmits the rotational force to the first guide groove 12a, and the reaction (resistance force) of the rotational force causes the fixed pinion. It can be said that the sprocket 21 is fixed. That is, the guide member 59 is formed in a shape capable of sliding in the radial direction in the first guide groove 12a and having a rotation preventing function. Here, the predetermined length is a length that can secure a drag force of a rotational force that causes the fixed pinion sprocket 21 to rotate.

In FIG. 4, the first guide groove 12a is formed in a rectangular shape having a longitudinal direction in the radial direction, and a guide member 59 formed in a rectangular shape smaller than the rectangular shape is illustrated.
In addition, if bearings are attached to the side wall of the guide member 59 in contact with the inner wall of the first guide groove 12a, particularly the four corners of the guide member 59, smoother sliding of the guide member 59 can be ensured.
Next, the structure for rotationally driving the rotation pinion sprockets 22 and 23 in the mechanical rotation drive mechanism 50 will be described.

The mechanical rotation drive mechanism 50 meshes with the pinions 51 and 52 fixed so as to rotate integrally with the support shafts 22a and 23a of the rotation pinion sprockets 22 and 23, respectively, corresponding to the pinions 51 and 52, respectively. Racks 53 and 54 provided as described above.
The pinions 51 and 52 are provided at axial ends of the support shafts 22a and 23a of the rotation pinion sprockets 22 and 23, respectively. Racks 53 and 54 corresponding to the pinions 51 and 52 are fixed to the second fixed disk 12 along the radial direction.

  In the following description, the pinion (advance side pinion) 51 of the first rotation pinion sprocket 22 is referred to as a first pinion 51, and a rack (advance side rack) 53 that meshes with the first pinion 51 is a first rack. 53 to distinguish. Similarly, the pinion (retard side pinion) 52 of the second pinion sprocket 23 is called a second pinion 52, and the rack (retard side rack) 54 that meshes with the second pinion 52 is called a second rack 54.

  As shown in FIG. 4, the first rack 53 is arranged on the retard side with respect to the first pinion 51 on the basis of the revolution direction. Conversely, the second rack 54 is disposed on the advance side with respect to the second pinion 52 on the basis of the revolution direction. For this reason, the pinions 51 and 52 and the racks 53 and 54 are opposite to each other by the racks 53 and 54 meshing with the pinions 51 and 52 when the pinions 51 and 52 are moved in the diameter increasing direction or the diameter reducing direction. It is arranged to be rotated.

  That is, the mechanical rotation drive mechanism 50 sets the rotation phase for rotation of the rotation pinion sprockets 22 and 23 according to the radial position of the pinion sprocket 20 moved by the sprocket moving mechanism 40A. That is, the mechanical rotation driving mechanism 50 has a one-to-one correspondence between the radial position of the pinion sprocket 20 and the rotation phase applied to the rotation of the rotation pinion sprockets 22 and 23.

In this way, the mechanical rotation drive mechanism 50 guides the fixed pinion sprocket 21 so as not to rotate, and guides the rotation pinion sprockets 22 and 23 to rotate.
The first pinion 51 and the second pinion 52 are configured in the same manner except that the positional relationship of the racks 53 and 54 with respect to the pinions 51 and 52 is different, and the first rack 53 and the second rack 54 are also configured. Are structured similarly. For this reason, in the following description, it demonstrates paying attention to the 1st pinion 51 and the 1st rack 53. FIG.

The outer diameter (pitch circle diameter) of the first pinion 51 is formed to be approximately half of the outer diameter (pitch circle diameter) of the first rotation pinion sprocket 22. In other words, the outer diameter of the first rotation pinion sprocket 22 is formed approximately twice the outer diameter of the first pinion 51. The reason is as follows.
Since the three pinion sprockets 20 are arranged at equal intervals in the circumferential direction, the chain length between the first pinion sprocket 22 and the fixed pinion sprocket 20 is such that the first rotation pinion sprocket 22 is a distance x in the radial direction. When moved, it changes by “2πx / 3”.

Therefore, if the first rotation pinion sprocket 22 rotates (rotates) so that the chain 6 having a length of “2πx / 3” is fed or pulled out between the first rotation pinion sprocket 22 and the fixed pinion sprocket 21, The chain length is adjusted appropriately.
Therefore, in order to adjust the chain length appropriately, when the first pinion 51 rotates by the distance x, the first rotation pinion sprocket 22 needs to rotate by 2πx / 3. That is, the first rotation pinion sprocket 22 needs to rotate by 2π / 3 times in the circumferential length with respect to the first pinion 51. In other words, the ratio between the outer diameter of the first rotation pinion sprocket 22 and the outer diameter of the first pinion 51 needs to be “2π / 3: 1”.

Therefore, the outer diameter of the first rotation pinion sprocket 22 is formed to be “2π / 3” times (substantially twice) the outer diameter of the first pinion 51.
Although not shown in the drawings, a disc spring is interposed between the support shaft 22a and the rotation pins 22b and 22c in the first rotation pinion sprocket 22. This is to absorb a shock (impact) at the time of meshing between the first rotation pinion sprocket 22 and the chain 6 that may occur during the change of the gear ratio. This disc spring is also provided in each of the fixed pinion sprocket 21 and the second rotation pinion sprocket 23.

[1-1-1-4. Axis of rotation〕
Next, the rotating shaft 1 will be described with reference to FIG. In the description of the rotary shaft 1, the configuration will be described with attention paid to the composite sprocket 5 on the output side. In FIG. 1, the output side tangent radius that is expanded or contracted by driving of the relative rotation drive mechanism 30 is indicated by a solid line with a maximum diameter, and a dotted line with a minimum diameter.
The rotary shaft 1 is formed with a recess 2 in which a plurality of pinion sprockets 20 can be accommodated. In the recess 2, the plurality of pinion sprockets 20 are housed most deeply when the tangent radius becomes the minimum diameter. As the radial position of the plurality of pinion sprockets 20 moves outward (expanded side) from this state, the degree of accommodation (accommodation depth) of the plurality of pinion sprockets 20 in the recess 2 decreases, and the radial position further increases. As a result, the plurality of pinion sprockets 20 are not accommodated in the recess 2.

The recess 2 has a first recess 2 a corresponding to the fixed pinion sprocket 21 and two second recesses 2 b and 2 b corresponding to the rotation pinion sprockets 22 and 23. One second recess 2b and the other second recess 2b are configured similarly.
The first recess 2 a is formed in a shape corresponding to the outer peripheral shape of the fixed pinion sprocket 21. Specifically, the outer peripheral shape of the main body portion 21b of the fixed pinion sprocket 21 is formed in an arc shape, and the first recess 2a forms a thinner cylinder than the outer peripheral surface side of the cylindrical rotating shaft. The main body portion 21b of the fixed pinion sprocket 21 is removed.

The main body portion 21b of the fixed pinion sprocket 21 is brought into contact with the first recess 2a when the tangent radius becomes the minimum diameter. At this time, the main body portion 21 b of the fixed pinion sprocket 21 is accommodated so as to bite into the rotary shaft 1.
The second recess 2b is formed in a cross-sectional shape corresponding to the outer peripheral shape of the rotation pinion sprockets 22,23. More specifically, the second recess 2b is a cylinder having a bottom surface or an upper surface formed by connecting the tips of the teeth of the rotation pinion sprockets 22 and 23 from the outer peripheral surface side of the cylindrical rotating shaft. The shape is formed by removing the portion.

  When the tangent radius becomes the minimum diameter, the tips of the rotation pinion sprockets 22 and 23 abut against the second recess 2b. At this time, the rotation pinion sprockets 22 and 23 are accommodated so as to bite into the rotary shaft 1.

Thus, when the tangent radius becomes the minimum diameter, the fixed pinion sprocket 21 comes into contact with the rotating shaft 1 that defines the first recess 2a, and rotates to the rotating shaft 1 that defines the second recess 2b. Pinion sprockets 22 and 23 abut.
Further, the guide rod 29 abuts on the outer peripheral surface 1a of the rotating shaft 1 positioned between the recesses 2a and 2b when the radius of contact is the minimum.

[1-1-2. chain〕
Next, the chain 6 will be described.
As shown in FIG. 5, the number of the chains 6 guided by the guide rod 29 is provided corresponding to the number of gear rows (three rows here) of each pinion sprocket 21, 22, 23. Here, three chains of a first chain 6A, a second chain 6B, and a third chain 6C are provided.

These chains 6A, 6B, and 6C are wound with a phase shifted in the power transmission direction, and are provided with a pitch shifted from each other. Here, the pitch of each other is shifted by 1/3 pitch. Correspondingly, the phases of the teeth 21c, 22c and 23c of the pinion sprocket 20 meshing with the chains 6A, 6B and 6C (hereinafter referred to as “teeth 20c” when they are not distinguished from each other) are also shifted. Has been.
The chains 6A, 6B, and 6C are similarly configured except for the arrangement pitch.
In addition, two or four or more chains 6 are used depending on the transmission torque of the continuously variable transmission mechanism. In this case, it is preferable that the pitch of each chain is shifted by “1 / number of chains”. .

Here, each chain 6A, 6B, 6C using a silent chain will be further described.
In each of the chains 6A, 6B, 6C, a plurality of link plate rows 61S in which a large number of link plates (drive links) 61 are arranged in series in the power transmission direction are arranged in parallel in the thickness direction of the link plate 61, thereby connecting pins 62 Concatenated by. In other words, a plurality of link plates 61 are arranged in parallel in the thickness direction.

  As shown in FIG. 7, the link plate 61 is formed with a pair of tooth portions 61a projecting toward the inner peripheral side of the chains 6A, 6B, 6C so as to be separated in the direction of power transmission, and the locations where the pair of tooth portions 61a, 61a are formed. A pair of pin holes 61b, 61b are formed at a predetermined interval corresponding to (corresponding to the power transmission direction). Further, a groove (link groove) 61c that engages with the teeth 20c of the pinion sprocket 20 is formed between the pair of tooth portions 61a and 61a.

  As shown in FIG. 5, the link plates 61 are adjacent to each other in the power transmission direction, but adjacent pin holes 61b, 61b in the link plates 61, 61 have a predetermined interval (the length between the pin holes 61b, 61b). As a result, the link plate row 61S is formed. The link plate rows 61S adjacent to each other in the thickness direction are arranged with the tooth portions 61a shifted from each other by one tooth, and are connected in an annular shape by connecting pins 62 that simultaneously penetrate the pin holes 61b aligned in the thickness direction.

In the present embodiment, an auxiliary link plate row 63S in which a large number of auxiliary link plates 63 are arranged in series in the power transmission direction is provided at both ends in the thickness direction of the chains 6A, 6B, 6C. In other words, a plurality of auxiliary link plates 63 are arranged on the outermost side in the thickness direction of the link plates 61 arranged in parallel and in the power transmission direction.
The auxiliary link plate row 63 </ b> S is guided by a guide surface 63 a formed on the inner peripheral side of the auxiliary link plate 63 being in contact with the outer peripheral surface of the guide rod 29. The auxiliary link plate row 63S is composed of auxiliary link plates 63 arranged in a row along the power transmission direction.

  The auxiliary link plate 63 can be made of resin. In this case, it is preferable to use a resin having strength and rigidity capable of withstanding contact with a guide rod 29 such as so-called engineering plastic such as polyamide or polyester.

  When the gear ratio is changed, the large number of guide rods 29 move in the radial direction in the same manner as the pinion sprockets 21, 22 and 23 so as to form a polygon together with the pinion sprockets 21, 22 and 23. The outer diameter of the composite sprocket 5 is changed. Each of the chains 6A, 6B, 6C changes the rolling path following the change in the outer diameter of the composite sprocket 5, and abuts against the guide rod 29 between the portions engaged with the pinion sprockets 21, 22, 23. Guided by rolling route.

For this reason, each chain 6A, 6B, 6C is equipped with an auxiliary link plate row 63S that contacts the guide rod 29. That is, a guide surface 63 a formed in a linear shape or an arc shape on the inner peripheral side of each auxiliary link plate 63 constituting the auxiliary link plate row 63 </ b> S is brought into contact with the guide rod 29.
The auxiliary link plate 63 is connected to the link plate 61 through the pair of pin holes 63b and 63b as shown in FIG.

Here, a description will be given focusing on the guide surface 63a formed in an arc shape. The guide surface 63a is formed according to an arc having the maximum winding radius (corresponding to the maximum tangent radius) of the chains 6A, 6B, 6C.
On the inner peripheral side of each auxiliary link plate 63, there are overlapping portions 64A and 64B that overlap in the thickness direction with the inner peripheral side of the auxiliary link plate 63 adjacent in the power transmission direction and continue the guide surface 63a in the power transmission direction. Is formed. These overlapping portions 64A and 64B are formed on the side of another auxiliary link plate 63 adjacent to the auxiliary link plate 63 (that is, on the upstream side and the downstream side in the power transmission direction).

In the following description, in the auxiliary link plate 63, the overlapping portion provided on one side in the power transmission direction is referred to as a first overlapping portion 64A, and the overlapping portion provided on the other side in the power transmission direction is referred to as a second overlapping portion 64B. To do.
The first overlapping portion 64A is adjacent to the second overlapping portion 64B of the other adjacent auxiliary link plate 63. The first polymerization part 64A and the second polymerization part 64B are polymerized.

  As shown in FIGS. 6A and 6B, each of the overlapping portions 64A and 64B is formed in a corresponding shape. Specifically, each of the overlapping portions 64A and 64B is formed of a thin portion 65a in which the auxiliary link plate 63 is thinned by a cutout portion 65b cut out in the thickness direction. The notch portion 65b of the first overlapping portion 64A corresponds to the thin portion 65a of the second overlapping portion 64B, and the notch portion 65b of the second overlapping portion 64B is configured to correspond to the thin portion 65a of the first overlapping portion 64A. ing.

Here, as shown in FIG.6 (b), the thickness of the thin part 65a and the thickness of the notch part 65b of each superimposition part 64A, 64B are provided equally or substantially equal. However, each thickness of the thin part 65 and the notch part 65b can be set arbitrarily.
Various shapes can be adopted as the shapes of the overlapping portions 64A and 64B. For example, as shown by a two-dot chain line in FIG. 6B, a shape is adopted in which the length in the thickness direction of the cutout portion 65b increases as each overlapping portion 64A, 64B moves toward the end of the power transmission direction. May be.

Further, the overlapping portions 64A and 64b are set so as to overlap without interfering with each other when the chains 6A, 6B, and 6C have the minimum winding radius (tangent circle radius).
On the other hand, the overlapping portions 64A and 64b are overlapped even when having the maximum winding radius, and the overlapping region is set so that the guide surface 63a is continuous in the power transmission direction. The overlap region corresponds to the overlap area when viewed from the direction orthogonal to the power transmission direction (pin axis direction).
Specifically, as the wrapping radius (tangent circle radius) of the chains 6A, 6B, and 6C decreases, the thin portion 65a of the second overlapping portion 65B enters the notched portion 65b of the first overlapping portion 65A. The thin portion 65a of the first overlapping portion 65A enters the cutout portion 65b of the second overlapping portion 65B, and the region where both thin portions 65a overlap is increased.

[1-2. Action and effect)
Since the continuously variable transmission mechanism according to one embodiment of the present invention is configured as described above, the following operations and effects can be obtained.
First, the chain 6A, 6B, 6C guided by the guide rod 29 will be described.

The chains 6A, 6B and 6C, to which the silent chain is applied, are wound around the composite sprockets 5 and 5 and engage with a plurality of pinion sprockets 20 to transmit power. At this time, the chains 6A, 6B, and 6C are guided by the guide rod 29 coming into contact with the guide surface 63a of the auxiliary link plate 63.
The guide surface 63a is formed on the inner peripheral side of each auxiliary link plate 63 and is continuous in the power transmission direction by overlapping portions 64A and 64B that overlap in the thickness direction with the inner peripheral side of another adjacent auxiliary link plate 63. Therefore, the guide surface 63a and the guide rod 29 can be smoothly brought into contact with each other, and quietness can be ensured. Furthermore, vibration can be suppressed, which can contribute to improvement of durability.

  Adjacent overlapping portions 64A and 64B are formed in shapes corresponding to each other, and overlap without interference when the chains 6A, 6B, and 6C have the minimum winding radius, and overlap at the maximum winding radius. Since the overlapping region is set so that the guide surface 63a is continuous in the power transmission direction, it is possible to ensure quietness and to suppress vibration when the winding radius is increased or decreased.

  Specifically, since the overlapping portions 64A and 64B are formed of the thin portion 65a thinned by the notch portion 65b cut out in the thickness direction, the overlapping portions 64A. When the 64Bs are superposed, the other thin part 65a is located in one notch part 65b and the one thin part 65a is located in the other notch part 65b. Since the thickness of the notch portion 65b and the thickness of the thin portion 65a are equal or substantially equal, each overlapping portion 64A. The load on 64B can be leveled. This contributes to improved durability.

The overlapping portions 64A and 64B can cope with various winding radii because the overlapping region increases as the winding radius of the chains 6A, 6B, and 6C decreases.
Furthermore, when the wrapping radius of the chains 6A, 6B, and 6C is small, the load per link increases, but the overlapping region increases as the wrapping radius decreases. Sex can be secured.

  If the auxiliary link plate 63 is made of resin, the weight can be reduced as compared with a generally used steel plate. Furthermore, the vibration and impact applied to the contact with the guide rod 29 can be buffered to contribute to the reduction of vibration and noise.

  For example, when the guide surface 63a is formed to have a diameter smaller than the maximum winding radius of the chains 6A, 6B, 6C, when the winding radius is the maximum, the guide rod 29 contacts the guide surface 63a. Contact may not be stable and vibration and noise may occur. On the other hand, according to the chains 6A, 6B, and 6C of the present embodiment, the guide surface 63a of the auxiliary link plate 63 is formed according to the arc shape of the maximum winding radius. The guide rod 29 can be satisfactorily brought into contact, and generation of vibration and noise can be suppressed.

In this way, vibration and noise can be suppressed by using the chains 6A, 6B, and 6C guided in contact with the plurality of pinion sprockets 20 and the guide member 29 in the continuously variable transmission mechanism of this embodiment. Wear can be reduced. For this reason, the chains 6A, 6B, and 6C of this embodiment are suitable for use in such a continuously variable transmission mechanism.
Since the chains 6A, 6B, and 6C are provided at different pitches, the noise can be further reduced by dispersing the noise caused by the contact between the chains 6A, 6B, and 6C and the guide rod 29.

  Since the auxiliary link plate row 63S is composed of the auxiliary link plates 63 arranged in a line along the power transmission direction, the length in the direction (thickness direction) orthogonal to the power transmission direction in the chains 6A, 6B, and 6C. Can be suppressed.

Next, the rotation of the pinion sprocket 20 will be described.
By changing the rotational phase of the drive disc 19 against the fixed disk unit 10 by the relative rotation drive mechanism 30, sprocket moving mechanism 40A and the rod moving mechanism 40B is running, the pinion sprocket 20 and the guide for the axis C ₁ of the rotary shaft 1 The radial position of the rod 29 is changed synchronously while maintaining an equal distance. Thereby, the tangent circle radius is changed. In this case, if the pinion sprocket does not rotate, a phase shift of the pinion sprocket with respect to the chain occurs. This phase shift is eliminated by the rotation of the rotation pinion sprockets 22 and 23 by the mechanical rotation drive mechanism 50.

  When the chain 6 is wound around the fixed pinion sprocket 21 and the first rotation pinion sprocket 22 or the second rotation pinion sprocket 23, when the contact radius increases, the fixed pinion sprocket 21 and the first rotation pinion sprocket 21 The optimum chain length between the sprocket 22 and the second rotation pinion sprocket 23 becomes long, and if the mechanical rotation drive mechanism 50 is not provided, the chain length is insufficient. At this time, the first rotation pinion sprocket 22 or the second rotation pinion sprocket 23 is rotated by the mechanical rotation drive mechanism 50, whereby the fixed pinion sprocket 21 and the first rotation pinion sprocket 22 or the second rotation pinion sprocket 23 are rotated. In the meantime, only the shortage of the chain length is sent.

  On the other hand, when the chain 6 is wound around the fixed pinion sprocket 21 and the first rotation pinion sprocket 22 or the second rotation pinion sprocket 23, when the contact circle radius is reduced, the fixed pinion sprocket 21 and the first rotation pinion sprocket 21 The optimum chain length between the rotation pinion sprocket 22 and the second rotation pinion sprocket 23 is shortened, and if the mechanical rotation drive mechanism 50 is not provided, the chain is slackened. At this time, the first rotation pinion sprocket 22 or the second rotation pinion sprocket 23 is rotated by the mechanical rotation drive mechanism 50, whereby the fixed pinion sprocket 21 and the first rotation pinion sprocket 22 or the second rotation pinion sprocket 23 are rotated. Only the remainder (sag) of the chain length is drawn from the gap.

  The rotation pinion sprockets 22 and 23 that rotate when the tangent radius is expanded or contracted have a one-to-one relationship between the radial position of the pinion sprocket 20 and the rotation phase of the rotation of the rotation pinion sprockets 22 and 23 by the mechanical rotation drive mechanism 50. It has become a correspondence relationship. That is, the rotation pinion sprockets 22 and 23 can transmit power while adjusting the excess or deficiency of the chain 6 when changing the gear ratio by the expansion / contraction diameter of the tangent radius.

  As described above, the rotation pinion sprocket 22 causes the mechanical rotation drive mechanism 50 to eliminate the phase shift of the plurality of pinion sprockets 20 with respect to the chain 6 in accordance with the radial movement of the plurality of pinion sprockets 20 by the sprocket moving mechanism 40A. , 23 are driven to rotate in conjunction with the sprocket moving mechanism 40, so that when the plurality of pinion sprockets 20 are moved in the radial direction, that is, when the gear ratio is changed, the chain length between the pinion sprockets is adjusted appropriately. The gear ratio can be changed while transmitting power.

[2. Others]
Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention. Each structure of one Embodiment mentioned above can be selected as needed, and may be combined suitably. Here, the silent chain is applied to the continuously variable transmission chain 6A, 6B, 6C, but the silent chain of the present invention can be applied to other mechanisms.

1 Rotating shaft 2 Recess 5 Composite sprocket 6 Chain 10 Fixed disk group 11 First fixed disk (fixed disk for radial movement)
11a Fixed radial groove for sprocket 11b Fixed radial groove for rod 12 Second fixed disk (fixed disk for rotation)
12a First guide groove (fixed pinion sprocket guide groove)
12b Second guide groove 12c Third guide groove 12A Helical gear 19 Movable disk (movable disk for radial movement)
19a Movable radial groove for sprocket 19b Movable radial groove for rod 19A Peripheral teeth 20 Pinion sprocket 21 Fixed pinion sprocket 21a Support shaft 22 First rotation pinion sprocket (advanced side rotation pinion sprocket)
22a Support shaft 23 Second rotation pinion sprocket (retarding side pinion sprocket)
23a Support shaft 29 Guide rod 29a Rod support shaft 29b Guide member 30 Relative rotation drive mechanism 31 Motor 31a Output shaft 31b Male screw portion 32 Fork 32a Female screw portion 32b Support body 32c Fork outer peripheral portion 32A Motion conversion mechanism 33 Input member 33a Helical gear 33b Fork groove 34A Interlocking rotation mechanism 34 Output member 34a Rotation drive tooth 40A Sprocket movement mechanism 40B Rod movement mechanism 50 Mechanical rotation drive mechanism 51 First pinion (advance side pinion)
52 Second pinion (retarding pinion)
53 First rack (advanced side rack)
54 Second rack (retard side rack)
59 Guide member 61 Link plate (drive link)
61S link plate row 61a teeth 61b the pin holes 61c link groove 62 connecting pin 63 auxiliary link plates 63S auxiliary link plate row 63a guide surface 63b pin holes 64A, 64B overlap portion 65a thin portions 65b notch C ₁ of the link plate 61, C _2, C _3, C ₄ axis

Claims (8)

A plurality of link plates having a pair of tooth portions formed on the inner peripheral side and having a pair of pin holes are arranged in series in the power transmission direction and in parallel in the thickness direction, and are connected by connecting pins inserted into the pin holes. has been Ri Na, a silent chain winding radius is enlarged or reduced,
The link plate in which a plurality of auxiliary link plates having a pair of pin holes into which linear or arcuate guide surfaces are formed on the inner peripheral side without teeth and through which the connecting pins are inserted are arranged. Are arranged in series in the outermost thickness direction and in the power transmission direction.
The inner peripheral side of each of the auxiliary link plates is formed with an overlapping portion that overlaps with the inner peripheral side of the adjacent auxiliary link plate in the thickness direction and continues the guide surface in the power transmission direction. Silent chain. The overlapping portion is formed of a thin portion that is thinned by a notch cut out in the thickness direction,
2. The silent chain according to claim 1, wherein a thickness of the thin portion and a thickness of the notch portion are set to be equal or substantially equal. The silent chain according to claim 1 or 2, wherein the overlapping portion is set so as to overlap without interference at a minimum winding radius. The superposition part is superposed at a maximum winding radius, and a superposition region is set so that the guide surface is continuous in a power transmission direction. Silent chain. The silent chain according to any one of claims 1 to 4, wherein the guide surface is formed according to an arc shape having a maximum winding radius. The silent chain according to any one of claims 1 to 5, wherein the auxiliary link plate is made of resin. A continuously variable transmission mechanism comprising two sets of composite sprockets around which the silent chain according to any one of claims 1 to 6 is wound,
The composite sprocket includes a rotation shaft to which power is input or output, a plurality of pinion sprockets and guide rods supported so as to be movable in a radial direction with respect to the rotation shaft, and the pinion sprockets and the guide rods to the rotation shaft. A movement mechanism that moves in synchronization with the radial direction while maintaining an equal distance from the axis of the
A continuously variable transmission mechanism characterized by changing a gear ratio by changing a contact circle radius that surrounds all of the plurality of pinion sprockets and is in contact with any of the plurality of pinion sprockets. The continuously variable transmission mechanism according to claim 7, wherein the plurality of silent chains are wound with a phase shifted in a power transmission direction.

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