JP2015178872A - Continuously variable transmission mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the difference between a centrifugal force acting on pinion sprockets in one composite sprocket and a centrifugal force acting on pinion sprockets in the other composite sprocket.SOLUTION: Provided is a continuously variable transmission including two composite sprockets and a chain wound on these composite sprockets. A sprocket moving mechanism includes: a fixed disc 10 that includes sprocket fixed radial grooves 11 formed so that support shafts 20a of a plurality of pinion sprockets 20 are interpolated into the respective grooves 11 and that rotates integrally with a rotary shaft; and movable discs each of which includes sprocket movable radial grooves crossing the sprocket fixed radial grooves 11, the support shafts 20a being located in respective crossing portions The sprocket fixed radial grooves 11 are each formed to be offset to an advance position as being closer to a radially intermediate portion 112 from each of an inner circumferential end portion 111 and an outer circumferential end portion 113 with respect to a rotation direction of the fixed disc 10.

Description

  The present invention provides a plurality of revolving with respect to the axis of the rotating shaft, supported so as to be movable in the radial direction and integrally rotated (revolve around the rotating shaft) while maintaining an equal distance from the axis of the rotating shaft. The present invention relates to a continuously variable transmission mechanism that transmits power by using a pinion sprocket and a chain wound around the pinion sprocket.

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. In addition, since excessive thrust is applied to the drive belt, a large friction loss occurs in a portion where the structure slips.

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 revolving with respect to the shaft center of the rotating shaft supported by being movable in the radial direction and integrally rotating while maintaining an equal distance from the shaft center of the rotating shaft. Apparent large sprockets (herein referred to as “composite sprockets”) formed so that pinion sprockets each have a polygonal apex are provided on each of the input side and the output side. One that transmits power by a chain wound around a composite sprocket.

  For example, two disks (spindles) are juxtaposed on one side of a plurality of pinion sprockets, and each disk is provided with a radial groove, and a radial groove (hereinafter referred to as a “fixed radial groove”) of the fixed disk that rotates integrally with the rotating shaft. And a radial groove (hereinafter referred to as a “movable radial groove”) of a movable disk that can rotate with respect to the rotation axis, are arranged so as to intersect each other, and the fixed radial groove and the movable radial groove intersect each other. Proposals have been made in which the shaft of each pinion sprocket is supported.

  The fixed radial grooves are formed in a straight line along the radial direction of the fixed disk. This means that when torque is transmitted by the composite sprocket, the reaction force (herein referred to as “torque reaction force”) that acts through the support shaft of each pinion sprocket in the fixed disk that inputs and outputs the rotational shaft and rotational power This is to act on the wall portion of the fixed radial groove along. Thereby, the movement to the radial direction of the pinion sprocket by torque reaction force is suppressed.

When the relative angle (phase) between the fixed disk and the movable disk is changed, the intersection of the fixed radial groove and the movable radial groove moves in the radial direction, so each pinion sprocket pivotally supported at the intersection is It is moved in the radial direction by the relative rotation of both disks. In this way, each pinion sprocket moves synchronously in the radial direction while maintaining an equal distance with respect to the rotation axis, so that the size of the polygon changes in a similar manner and the composite sprocket expands and contracts. The gear ratio changes.
Such a continuously variable transmission mechanism is disclosed in Patent Document 1, for example.

U.S. Pat. No. 7,713,154

  By the way, when the composite sprocket rotates, a centrifugal force acts on each pinion sprocket. Such centrifugal force is proportional to the radial position of the pinion sprocket (distance to the axis of the rotating shaft) r and the square of the angular velocity ω at which the pinion sprocket revolves around the axis of the rotating shaft. In addition, a chain is wound around the composite sprockets provided on the input and output sides, respectively, and the peripheral speed (corresponding to rω) is equal in either one or the other composite sprocket. Accordingly, the centrifugal force acting on the pinion sprocket in each composite sprocket has a magnitude corresponding to the angular velocity ω of the pinion sprocket.

For example, when one composite sprocket has a reduced diameter and the other composite sprocket has an increased diameter, the radial position r ₁ of each pinion sprocket (herein referred to as “one pinion sprocket”) in one composite sprocket. Is smaller than the radial position r ₂ (<r ₁ ) of each pinion sprocket (herein referred to as “the other pinion sprocket”) in the other composite sprocket, and the angular velocity ω ₁ of _one pinion sprocket is It becomes faster than the angular velocity ω ₂ (> ω ₁ ) of the pinion sprocket. Further, the peripheral speeds of all the composite sprockets are equal (r ₁ ω ₁ = r ₂ ω ₂ ). Therefore, the centrifugal force (∝ω ₁ ) acting on one pinion sprocket is larger than the centrifugal force (∝ω ₂ ) acting on the other pinion sprocket. That is, a force that increases the diameter of one composite sprocket acts on one pinion sprocket, and a force that reduces the diameter of the other composite sprocket acts on the other pinion sprocket.

  Thus, if the radial position of one pinion sprocket and the radial position of the other pinion sprocket are different, a difference in centrifugal force occurs between the one composite sprocket and the other composite sprocket. As a result, the shift controllability may be reduced.

One of the objects of the present invention was devised in view of the above problems, and the difference between the centrifugal force acting on the pinion sprocket in one composite sprocket and the centrifugal force acting on the pinion sprocket in the other composite sprocket. It is an object to provide a continuously variable transmission mechanism that can suppress the above.
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, a continuously variable transmission mechanism according to the present invention includes a rotating shaft to which power is input or output, and a plurality of pinion sprockets supported so as to be movable in a radial direction with respect to the rotating shaft. And two sets of composite sprockets having a plurality of pinion sprockets that move in synchronism with the radial direction while maintaining the same distance from the axis of the rotating shaft, and two sets of composite sprockets. A continuously variable transmission mechanism that changes a gear ratio by changing a contact circle radius that is a radius of a circle that surrounds all of the plurality of pinion sprockets and that is in contact with any of the plurality of pinion sprockets The sprocket moving mechanism is formed with a fixed radial groove for a sprocket into which each support shaft of the plurality of pinion sprockets is inserted. A fixed disk that rotates integrally with the rotating shaft, and a movable radial groove for the sprocket in which the support shaft is located at an intersection where the fixed radial groove for the sprocket intersects, and is disposed concentrically with the fixed disk. And the fixed radial groove for the sprocket is directed from each of the inner peripheral end and the outer peripheral end toward the radial intermediate portion with reference to the rotational direction of the fixed disc. It is characterized by being formed so as to be biased toward the advance side.

(2) It is preferable that the fixed radial groove for the sprocket is formed in an arc shape.
(3) Moreover, it is preferable that the said fixed radial groove | channel for sprockets is linearly formed between each of the said inner peripheral side edge part and the said outer peripheral side edge part, and the said radial direction intermediate part.

(4) It is preferable that the fixed radial grooves for the sprocket are arranged so that the radial distances between the inner peripheral end and the outer peripheral end are equal to the radial intermediate portion.
(5) It is preferable that the sprocket moving mechanism includes a relative rotation driving mechanism that drives the movable disk to rotate relative to the fixed disk and moves the intersection in the radial direction.

According to the continuously variable transmission mechanism of the present invention, the fixed radial groove for the sprocket advances from each of the inner peripheral end and the outer peripheral end toward the radial intermediate portion with respect to the rotation direction of the fixed disk. Since it is formed to be biased to the corner side, the component force of the torque reaction force input from the fixed radial groove for the sprocket through the support shaft of each pinion sprocket during torque transmission by the composite sprocket and chain is supported by each pinion sprocket. When the shaft is positioned closer to the inner peripheral side than the radial intermediate portion, it can act as a force to move the support shaft of each pinion sprocket along the fixed radial groove for the sprocket to the inner peripheral side, When the support shaft of each pinion sprocket is positioned on the outer peripheral side end side with respect to the radially intermediate portion, the support shaft of each pinion sprocket is It can act as a force for moving toward the outer periphery along the socket fixed radial grooves.
For this reason, for example, when one composite sprocket is reduced in diameter and the other composite sprocket is expanded in diameter, a component of torque reaction force can be applied in a direction opposite to the direction of centrifugal force action in one composite sprocket. In addition, a component of torque reaction force can be applied in the same direction as the centrifugal force in the other composite sprocket.
Thus, the centrifugal force acting on the pinion sprocket in one composite sprocket by causing the component of the torque reaction force to act in the opposite direction to the larger centrifugal force and in the same direction as the smaller centrifugal force. And the centrifugal force acting on the pinion sprocket in the other composite sprocket can be suppressed. As a result, the shift controllability can be improved.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a radial cross-sectional view (transverse cross-sectional view) schematically showing a main part focused on a composite sprocket and a chain of a continuously variable transmission mechanism according to an embodiment of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an axial cross-sectional view (longitudinal 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. It is a side view which pays attention to the fixed disk of the continuously variable transmission mechanism concerning one embodiment of the present invention. FIG. 3 corresponds to the arrow AA in FIG. It is a principal part enlarged view explaining the fixed radial groove | channel for sprockets in the fixed disk of the continuously variable transmission mechanism concerning one Embodiment of this invention. FIG. 4 corresponds to a region E in FIG. 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 radial direction sectional drawing of the continuously variable transmission mechanism concerning one Embodiment of this invention. 6 is a cross-sectional view taken along the line BB in FIG. It is radial direction sectional drawing of the continuously variable transmission mechanism concerning one Embodiment of this invention. 7 is a cross-sectional view taken along the line CC in FIG. It is a principal part enlarged view which expands and shows the 1st cam groove and 2nd cam groove of the continuously variable transmission mechanism concerning one Embodiment of this invention. This FIG. 8 is a DD arrow view of FIG. FIG. 3 is a perspective view schematically showing a part of a continuously variable transmission mechanism chain according to an embodiment of the present invention and a part of a guide rod that guides the chain. It is a principal part enlarged view which shows the modification of the fixed radial groove | channel for sprockets of the continuously variable transmission mechanism concerning one Embodiment of this invention. FIG. 10 corresponds to FIG.

  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 will be described as the outside.

[One Embodiment]
Hereinafter, a continuously variable transmission mechanism according to an embodiment will be described.
[1. Constitution〕
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, which will be described later in detail, are formed so as to form a vertex of a polygon (here, a pentagon). .

  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 rotary shaft 1 (output shaft) on the output side. 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 that are movably supported in the radial direction with respect to the rotating shaft 1, and a plurality of (here, twelve) guide rods (first number). 1 guide rod) 29. The three pinion sprockets 20 are arranged at equal intervals along the circumferential direction on the circumference centered on the axis C ₁ of the rotating shaft 1, and four guide rods 29 are provided 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, 5 to 7). Details of these will be described later.

  This continuously variable transmission mechanism changes the outer diameter of an apparent large sprocket formed such that the pinion sprocket 20 and the guide rod 29 form a vertex of a polygon, that is, the outer diameter of the composite sprocket 5 (expansion / reduction diameter). By doing so, the gear ratio is changed.

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, the outer diameter of the composite sprocket 5 corresponds to the contact radius between the plurality of pinion sprockets 20 and the chain 6, that is, the radius of the pitch circle of the composite sprocket 5. It can be said.
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.

Thus, the continuously variable transmission mechanism changes the gear ratio by changing the tangent radius. For example, if the tangent radii of the composite sprockets 5 and 5 are equal, the continuously variable transmission mechanism has a transmission ratio of 1 (the power transmission ratio between one composite sprocket 5 and the other composite sprocket 5 is 1: 1).
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. (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, and the mechanical rotation driving mechanism 50 will be described in this order.

[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 is equal to the rotation speed at which the pinion sprocket 20 revolves. 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. Here, “spinning” means that the rotating 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 formed on the entire outer periphery of the main body portion 21b. Similarly, each of the rotation pinion sprockets 22 and 23 includes main body portions 22b and 23b and teeth 22c and 23c 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.
Note that the first rotation pinion sprocket 22 and the second rotation pinion sprocket 23 are configured in the same manner except that the arrangement location and the rotation direction are different. Therefore, here, the first rotation pinion sprocket 22 will be described by focusing on the first rotation pinion sprocket 22. To do.

  In the present embodiment, as shown in FIG. 2, the first rotation pinion sprocket 22 includes three rows of gears in the axial direction and is not shown, but the fixed pinion sprocket 21 and the second rotation pinion sprocket 23 are also in the axial direction. Are provided with three rows of gears, and three chains 6 are also wound around these rows of gears. 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 and a relative rotation drive mechanism 30 described later in the same cross section.

  Although not shown in the drawings, the pinion sprockets 21, 22 and 23 allow power to be transmitted by allowing a minute rotation (rotation within a certain range) while restricting rotation of the support shafts 21a, 22a and 23a. A phase shift allowable power transmission mechanism to be realized may be provided. As such a phase shift allowable power transmission mechanism, a key member equipped to rotate integrally with the inner peripheral side of the pinion sprockets 21, 22, 23, and the support shafts 21 a, 22 a, 23 a of the pinion sprockets 21, 22, 23 are provided. A key groove formed on the outer peripheral side and engaged with play in the rotational direction with the key member engaged, and the key member in the forward direction and the reverse direction in the rotational direction so that the key member is located at a neutral position in the rotational direction of the key groove. And an urging member that urges from both sides, and that urges to a neutral position in the rotational direction and elastically restricts rotation can be used. In this case, the main body portions 21b, 22b, and 23b of the pinion sprockets 21, 22, and 23 can transmit power to the support shafts 21a, 22a, and 23a while allowing slight rotation.

[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. These guide rods 29 guide the track of the chain 6 that is in contact with the circumferential surface on the radially outer side. Since the pinion sprockets 21, 22, 23 and the guide rods 29 are polygonal (substantially regular polygonal) shapes, the chain 6 contacts the pinion sprockets 21, 22, 23 and the guide rods 29 on the radially inner side. Roll along a polygonal shape while touching.

  As shown in FIGS. 1 and 2, the 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). The chain 6 (see FIGS. 1 and 2) is guided by the outer peripheral surface of the guide member 29b.

The number of guide rods 29 is not limited to twelve and may be more or less than this. 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.

[1-1-3. 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. (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 10 (radial direction moving fixed disk, rotating fixed disk) that rotates integrally with the rotating shaft 1 and a concentric arrangement with the fixed disk 10 and capable of relative rotation are provided. A movable disk 19, a first rotating part 15 that rotates integrally with the fixed disk 10, a second rotating part 16 that rotates integrally with the movable disk 19, and a relative drive that rotates the movable disk 19 relative to the fixed disk 10. Each will be described in the order of the rotation drive mechanism 30.

The fixed disk 10, the movable disk 19, the first rotating part 15, and the second rotating part 16 are disposed concentrically with the axis C ₁ of the rotating shaft 1, and the radial direction of the disks 10, 19 is that of the rotating shaft 1. It coincides with the radial direction.
The fixed disk 10 and the movable disk 19 are respectively 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). Focusing on the fixed disk 10 and the movable disk 19 provided on the upper side of FIG. 2, the configuration will be described.

[1-1-3-1-1. (Fixed disk)
The fixed disk 10 is formed integrally with the rotating shaft 1 or is coupled so as to rotate together with the rotating shaft 1. FIG. 2 illustrates an example in which the movable disk 19 and the fixed disk 10 are arranged in this order from the plurality of pinion sprockets 20 toward the outside in the axial direction.

As shown in FIG. 3, the fixed disk 10 is provided corresponding to the sprocket fixed radial grooves 11 a, 11 b, 11 c and the respective guide rods 29 provided corresponding to the pinion sprockets 21, 22, and 23. Two types of radial grooves are formed: a fixed radial groove 12 for a rod (a reference numeral is attached to only one location). In FIG. 3, the revolution direction in the counterclockwise direction is indicated by a white arrow.
Hereinafter, the fixed radial grooves 11a, 11b, 11c for the sprocket and the fixed radial grooves 12 for the rod will be described in this order.

[1-1-3-1-1-1. (Fixed radial groove for sprocket)
Support shafts 21a, 22a, and 23a of pinion sprockets 21, 22, and 23 are inserted into the fixed radial grooves 11a, 11b, and 11c for the sprocket. The fixed radial groove 11a for the sprocket corresponding to the fixed pinion sprocket 21 can be said to be a groove (fixed pinion sprocket guide groove) for guiding the radial movement of the fixed pinion sprocket 21. Similarly, the sprocket corresponding to the first rotating pinion sprocket 22 is used. The fixed radial groove 11b for use as a groove guides the radial movement of the first rotation pinion sprocket 22, and the fixed radial groove 11c for the sprocket corresponding to the second rotation pinion sprocket 23 corresponds to the radial direction of the second rotation pinion sprocket 23. It can be said that the groove guides movement. For this reason, these fixed radial grooves 11a, 11b, 11c for sprockets are along the radial movement path of the corresponding pinion sprockets 21, 22, 23.

Here, the radial positions of the support shafts 21a, 22a, and 23a of the pinion sprockets 21, 22, and 23 will be described in order to explain the locations of the sprocket fixed radial grooves 11a, 11b, and 11c.
The distance between the shaft centers C ₂ , C ₃ , C ₄ of the support shafts 21 a, 22 a, 23 a in the pinion sprockets 21, 22, 23 and the shaft center C ₁ of the rotary shaft 1 is determined when the tangent radius is the minimum diameter. The minimum distance (hereinafter referred to as “minimum diameter”) r ₁ , and the maximum distance (hereinafter referred to as “maximum diameter”) r ₃ when the tangent radius is the maximum diameter, each composite sprocket 5 (FIGS. 1 and 2). (See) is equal to each other, an intermediate distance between the minimum diameter r ₁ and the maximum diameter r ₃ (hereinafter referred to as “intermediate diameter”) r ₂ .

The radial positions of the sprocket fixed radial grooves 11a, 11b, and 11c in the fixed disk 10 are set to a minimum diameter r ₁ and an intermediate diameter r according to the movement range of the support shafts 21a, 22a, and 23a of the pinion sprockets 21, 22, and 23. ₂ and the maximum diameter r ₃ .
These sprocket fixed radial grooves 11a, 11b, and 11c are configured in the same manner except that they are disposed at different locations.

In the following description, when these fixed radial grooves 11a, 11b, and 11c for sprockets are shown without distinction, they are simply referred to as fixed radial grooves 11 for sprockets, and pinion sprockets 21 corresponding to the fixed radial grooves 11 for sprockets, 22 and 23 and the support shafts 21a, 22a, and 23a are also simply referred to as the pinion sprocket 20 and the support shaft 20a.
As shown in FIG. 4, the fixed radial groove 11 for the sprocket is formed from the inner peripheral end 111 and the outer peripheral end 113 to the radial intermediate portion 112 on the basis of the rotation direction (revolution direction) of the fixed disk 10. It is formed to deviate toward the advance side as it goes. In FIG. 4, a counterclockwise revolution direction is indicated by a white arrow.

In other words, in the fixed radial groove 11 for sprocket, the phase θ ₂ of the radial intermediate portion 112 is located on the most advanced side with respect to the rotation direction of the fixed disk 10, and is retarded from the radial intermediate portion 112. phase theta ₁ and the phase theta ₃ of outer end portion 113 of the inner peripheral end 111 is located. In Figure 4, but illustrates what phase theta ₁ of the inner peripheral end 111 is disposed on the retard side of the phase theta ₃ of outer end portion 113, the phase theta ₁ of the inner peripheral end 111 May be the same phase as the phase θ ₃ of the outer peripheral side end portion 113, or may be disposed on the advance side with respect to the phase θ ₃ of the outer peripheral side end portion 113.

The fixed radial grooves 11 for the sprocket are arranged so that the radial distances between the radial intermediate portion 112 and the inner peripheral end 111 and the outer peripheral end 113 are equal. Specifically, the radial distance L ₁₂ between the intermediate diameter r ₂ corresponding to the radial intermediate portion 112 and the minimum diameter r ₁ corresponding to the inner peripheral side end 111, and the intermediate diameter corresponding to the radial intermediate portion 112. The radial distance L ₂₃ between r ₂ and the minimum diameter r ₃ corresponding to the outer end 113 is equal.

  A support shaft 20a (indicated by a two-dot chain line) of the pinion sprocket 20 when the tangent radii of the composite sprockets 5 are equal to each other is located in the radial intermediate portion 112. On the other hand, the support shaft 20a of the pinion sprocket 20 is located at the inner peripheral side end portion 111 when the tangent radius is the minimum diameter, and the outer peripheral side end portion 113 is located at the tangential radius is the maximum diameter. The support shaft 20a (indicated by a two-dot chain line) of the pinion sprocket 20 is located.

  Here, the case where the fixed radial groove 11 for sprocket is formed in an arc shape will be described as an example. The fixed radial groove 11 for the sprocket has a constant curvature between the inner peripheral end 111 and the outer peripheral end 113. In other words, the sprocket fixed radial groove 11 is formed in a smoothly continuous curved shape. Further, in FIG. 4, in order to clearly indicate that the fixed radial groove 11 for the sprocket has an arc shape, an example having a relatively large arc curvature is illustrated, but the arc curvature is not limited thereto.

The sprocket fixed radial groove 11 is formed in an arc shape because the teeth of racks 53 and 54 (details will be described later) provided along the shape of the sprocket fixed radial groove 11 are evenly arranged. This is because the engagement of the pinions 51 and 52 with the racks 53 and 54 can be made smooth.
The fixed radial groove 11 for sprockets is roughly divided into an inner peripheral portion 11i on the inner peripheral side end portion 111 side with respect to the radial intermediate portion 112 and an outer peripheral portion 11o on the outer peripheral side end portion 113 side with respect to the radial intermediate portion 112. can do.

The inner peripheral portion 11i is provided to be inclined by the first angle α with respect to the radial direction, and the outer peripheral portion 11o is provided to be inclined by the second angle β with respect to the radial direction. The radial direction here corresponds to the phase θ ₂ of the radial intermediate portion 112.
Specifically, the inner peripheral portion 11i is inclined toward the retarded side by the first angle α, and the outer peripheral portion 11o is inclined toward the retarded side by the second angle β. Since the fixed radial groove 11 for the sprocket is formed in an arc shape, the first angle α applied to the inner peripheral portion 11i increases as it approaches the inner peripheral end 111, and the first angle α applied to the outer peripheral portion 11o. The two angles β become larger as the outer end 113 is approached.

First, as a premise for explaining the angles α and β, the force acting on the support shaft 20a of the pinion sprocket 20 at the time of torque transmission in the composite sprocket 5 and the chain 6 will be described, and then the centrifugal force in the composite sprockets 5 and 5 is explained. Will be described.
When torque is transmitted by the composite sprockets 5, 5 and the chain 6, for example, in one composite sprocket 5, torque is transmitted from the rotary shaft 1 on the input side to the support shaft 20 a of the pinion sprocket 20 through the fixed disk 10. . At this time, a force opposite to the torque transmission direction (hereinafter referred to as “torque reaction force”) acts through the support shaft 20 a of the pinion sprocket 20. This torque reaction force acts along the circumferential direction (direction perpendicular to the radial direction).

Similarly, the torque reaction force acts on the other composite sprocket 5 when torque is transmitted from the support shaft 20 a of the pinion sprocket 20 to the fixed disk 10.
The torque reaction force mainly acts on the fixed disk 10. This is because the fixed disk 10 rotates integrally with the rotary shaft 1 and bears power transmission, whereas the movable disk 19 (see FIG. 2) does not bear power transmission.

The torque reaction force F _i when the support shaft 20a of the pinion sprocket 20 is positioned at the inner peripheral portion 11i is a first component force F _i1 that is input perpendicularly to the wall portion 11w that defines the fixed radial groove 11 for the sprocket, It can be decomposed into a second component force F _i2 orthogonal to the first component force F _i1 . The second component force F _i2 has a direction toward the inner peripheral end 111 along the inner peripheral part 11i.
The torque reaction force F _i and the first component force F _i1 have the relationship of the following formula (1).
F _i1 = F _i · cos α (1)
Further, the torque reaction force F _i and the second component force F _i2 have the relationship of the following formula (2).
F _i2 = F _i · sin α (2)

Similarly, the torque reaction force F _o when the support shaft 20a of the pinion sprocket 20 is positioned at the outer peripheral portion 11o is divided into a first component force F _o1 and a second component force F _o2 that are input perpendicularly to the wall portion 11w. Can be disassembled. The second component force F _o2 has a direction toward the outer peripheral end 113 along the outer peripheral part 11o.
The torque reaction force F _o and the first component force F _o1 have the relationship of the following formula (3).
F _o1 = F _o · cos β (3)
Further, the torque reaction force F _o and the second component force F _o2 have the relationship of the following formula (4).
F _o2 = F _o · sin β (4)

Next, the centrifugal force in the composite sprockets 5 and 5 will be described.
In one composite sprocket 5, when the support shaft 20 a is positioned on the inner peripheral portion 11 i of the sprocket fixed radial groove 11 a, in the other composite sprocket 5, the support shaft 20 a is positioned on the outer peripheral portion 11 o of the sprocket fixed radial groove 11. To do. At this time, since the peripheral speeds of any of the composite sprockets 5 and 5 are equal, the centrifugal force F ₁ (indicated by a white arrow) in one composite sprocket 5 is the centrifugal force F ₂ acting on the other composite sprocket 5 ( (Indicated by a white arrow). As described above, centrifugal forces F ₁ and F ₂ that are different from each other act on the composite sprockets 5 and 5, whereby a force directed toward the outer peripheral side acts on the support shaft 20 a located on the inner peripheral part 11 i, and is positioned on the outer peripheral part 11 o. A force directed toward the inner periphery acts on the supporting shaft 20a.

  When the contact radii of the composite sprockets 5 and 5 are equal, that is, when the gear ratio of the continuously variable transmission mechanism is 1, the centrifugal force is balanced.

On the other hand, the second component force F _i2 applied to the support shaft 20a of the inner peripheral portion 11i acts in a direction to cancel the centrifugal force F _1, and the second component force F _o2 applied to the support shaft 20a of the outer peripheral portion 11o is a centrifugal force. Acts in the direction of increasing F ₂ . That is, the second component forces F _i2 and F _o2 act in the direction of increasing the smaller centrifugal force F ₂ and decreasing the larger centrifugal force F ₁ , so that different centrifugal forces are generated in the composite sprockets 5 and 5. It works in the direction of reducing the difference.

The angles α and β applied to the second component forces F _i2 and F _o2 are set so that the difference between the centrifugal forces F ₁ and F _{2 that} are different between the composite sprockets 5 and 5 can be efficiently reduced. Setting the angles α and β in the fixed radial groove 11 for the sprocket can be regarded as setting the curvature and orientation of the groove shape.

[1-1-3-1-1-2. Fixed radial groove for rod)
As shown in FIG. 3, the rod support shaft 29a (only one place is attached | subjected) of the corresponding guide rod 29 is inserted in the fixed radial groove | channel 12 for rod (only one place is attached | subjected). . The fixed radial grooves 12 for rods are configured in the same manner except that the arrangement locations are different.

  FIG. 3 shows an example in which the fixed radial groove 12 for a rod is formed in a straight line. However, the fixed radial groove for rod 12 is not limited to a linear shape, and may have various shapes. For example, the pinion sprocket 20 (see FIG. 1) is aligned with the sprocket fixed radial grooves 11a, 11b, and 11c so that the guide rods 29 are positioned at equal intervals between the pinion sprockets 20 at any radial position. You may employ | adopt the fixed radial groove | channel 12 for rods of a shape.

[1-1-3-1-2. (Movable disc)
As shown in FIG. 2, the movable disk 19 is provided on each of one side and the other side with the pinion sprocket 20 interposed therebetween. These movable disks 19 are connected to each other by a connecting shaft 19A. Here, as shown in FIG. 1, a connecting shaft 19 </ b> A (a reference numeral is attached only to one place) is provided between the pinion sprockets 21, 22, and 23. As a result, the movable disk 19 on one side and the movable disk 19 on the other side rotate together.

  As shown in FIG. 5, the movable disk 19 (shown by a broken line) includes a sprocket movable radial groove 19a and a rod movable radial groove 19b. A kind of movable radial groove is formed. Note that the outer shape of the movable disk 19 is circular and overlaps with the outer shape of the fixed disk 10 that is circular, but in FIG.

[1-1-3-1-2-1. (Movable radial groove for sprocket)
Each of the sprocket movable radial grooves 19a is provided so as to intersect with each of the above-described sprocket fixed radial grooves 11a, 11b, and 11c. Each of the pinion sprockets 21, 22, and 23 is provided at a first intersecting point CP ₁ where the sprocket movable radial groove 19 a and the sprocket fixed radial grooves 11 a, 11 b, and 11 c intersect (all of which are given a reference numeral only). Support shafts 21a, 22a, and 23a are located.
Each sprocket movable radial groove 19a is provided in a shape corresponding to each of the fixed radial grooves 11a, 11b, 11c for sprockets.

[1-1-3-1-2-2. (Moveable radial groove for rod)
Similarly, the rod movable radial groove 19b is provided so as to intersect with the above-mentioned rod fixed radial groove 12, and each rod support shaft 29a is disposed at the intersection.
Each of the rod movable radial grooves 19b is provided in a shape corresponding to each of the fixed radial grooves 12 for the rod.

[1-1-3-1-3. (First rotating part)
As shown in FIG. 2, the first rotating portion 15 is a portion that rotates integrally with the fixed disk 10, that is, a portion that rotates integrally with the rotating shaft 1. Here, the first rotating portion 15 is provided on a part of the rotating shaft 1. The first rotating portion 15 is disposed on the outer side in the axial direction than the fixed disk 10 and the movable disk 19.

As shown in FIGS. 2, 7 and 8, the first rotating portion 15 is provided with a first cam groove 15a. The first cam groove 15 a is provided so as to be recessed along the axial direction of the rotary shaft 1. Here, the first cam groove 15 a is formed in parallel with the axis C ₁ of the rotary shaft 1. FIG. 7 illustrates an example in which the first cam groove 15a (only one place is provided with a reference numeral) is provided at three places at intervals in the circumferential direction. May be set according to the surrounding configuration, required specifications, and the like, and various shapes and numbers can be employed.

[1-1-3-1-4. (Second rotating part)
As shown in FIGS. 2, 6, and 7, the second rotating portion 16 is connected to the movable disk 19 via the connecting portion 17. In FIGS. 6 and 7, counterclockwise revolution directions are indicated by white arrows.

First, the connection part 17 is demonstrated.
The connecting portion 17 is disposed so as to rotate integrally with the movable disc 19 and the second rotating portion 16 and cover the fixed disc 10. The connection portion 17 includes an axial connection portion 17 a that covers the outer periphery (radially outer side) of the fixed disk 10, and a radial connection portion 17 b that covers the axial outer side of the fixed disk 10.

In the connection part 17, among the connections between the movable disk 19 and the second rotation part 16, the axial direction connection part 17 a connects the axial component separations, and connects the radial separations. It is the radial direction connection part 17b.
Axial connection portion 17a has a cylindrical shape extending in the axial direction together provided the axis C ₁ and concentric rotary shaft 1. As shown in FIG. 2, the axial direction connecting portion 17a is connected to the outer peripheral end portion (outer peripheral portion) 19t of the movable disk 19, and the axially outer side is connected to a radial connecting portion 17b described below. Has been.

As shown in FIGS. 2, 6, and 7, the radial connection portion 17 b is connected to the axial connection portion 17 a on the radial outer side and is connected to the second rotation portion 16 on the radial inner side. The radial connection portion 17b is formed in a lightening shape by lightening portion 17c which will be described from the disc which extends radially with provided the axis C ₁ and concentric rotary shaft 1.

  As shown in FIG.6 and FIG.7, the radial direction connection part 17b is provided with the thinning part 17c. The lightening portion 17c is formed at a position corresponding to the racks 53 and 54 and the pinions 51 and 52 of the mechanical rotation driving mechanism 50, which will be described in detail later. FIG. 6 shows an example in which fan-shaped thinned portions 17c provided at three locations are provided at equal intervals with the radial connecting portion 17b interposed therebetween. However, the shape and number of the thinned portions 17c may be set according to the surrounding configuration, required specifications, and the like, and various shapes and numbers can be employed.

Next, the second rotating unit 16 will be described.
As shown in FIGS. 2, 6, and 7, the second rotating portion 16 is provided so as to cover the outer periphery (radially outer side) of the first rotating portion 15, and is concentric with the axis C ₁ of the rotating shaft 1. It is formed in a cylindrical shape. Here, as shown in FIG. 2, the second rotating portion 16 is shifted from the outer peripheral end portion 19 t of the movable disk 19 to the inner peripheral side and provided along the axial direction.

As shown in FIGS. 2 and 8, the second rotating portion 16 is provided with a second cam groove 16 a. The second cam groove 16a is provided adjacent to the outer periphery of the first cam groove 15a, and is provided along the rotary shaft 1 while intersecting the first cam groove 15a. The second cam groove 16 a is provided so as to intersect the axial direction of the rotary shaft 1.
FIG. 7 illustrates an example in which the second cam groove 16a (only one place is given a reference numeral) is provided at three places at intervals in the circumferential direction. Is set according to the formation location and the number of formation of the first cam groove 15a.

[1-1-3-1-5. (Relative rotation drive mechanism)
In addition to the first cam groove 15a provided in the first rotating part 15 and the second cam groove 16a provided in the second rotating part 16, the relative rotation drive mechanism 30 includes the first cam groove 15a and the first cam groove 15a. A cam roller 90 disposed at the second intersection CP ₂ where the two cam grooves 16a intersect, a glasses fork (axial force transmission member) 35 for transmitting axial force to the cam roller 90, and the glasses An axial movement mechanism 31 that moves the fork 35 in the axial direction is provided.
Hereinafter, the cam roller 90, the glasses fork 35, and the axial movement mechanism 31 will be described in this order.

As shown in FIGS. 2 and 7, the cam roller 90 is formed in a cylindrical shape. This cam roller 90 has an axial center along a direction orthogonal to the axial center C ₁ of the rotating shaft 1, and a second intersecting point CP ₂ (both of which the first cam groove 15 a and the second cam groove 16 a intersect each other). It is inserted through only one place. For this reason, the cam roller 90 rotates around the axis C ₁ of the rotating shaft 1 in conjunction with the rotation of the rotating shaft 1. A bearing is fitted on the outer periphery of the cam roller 90 at locations corresponding to the first cam groove 15a and the second cam groove 16a.

One end portion 90a of the cam roller 90 is provided to be protruded from the second intersection CP ₂ in the radial direction.
Although not shown in the drawing, the cam roller 90 is appropriately removed so as not to fall off the cam grooves 15a and 16a. Examples of the retaining process include providing a head at the other end of the cam roller 90 and adding a retaining pin so that the cam roller 90 can move in the axial direction but not in the radial direction. It is done.

The glasses fork 35 is provided across the two composite sprockets 5 and 5. The spectacles fork 35 includes an annular cam roller support part 35a (corresponding only to one side) provided corresponding to each of the composite sprockets 5 and 5, and a bridge part 35b for connecting the cam roller support parts 35a. Have. The first rotating portion 15 and the second rotating portion 16 are disposed on the inner peripheral side of the cam roller support portion 35a.
The glasses fork 35 is parallel to the disks 10 and 19 and is arranged in a plate shape on the outer side in the axial direction with respect to the disks 10 and 19 when the chain 6 is used as a reference.

A groove portion 35c is recessed in the cam roller support portion 35a over the entire inner periphery.
The groove portion 35 c has a depth corresponding to the protruding length of the cam roller 90 and accommodates one end portion 90 a of the cam roller 90. That is, it can be said that the groove 35c has an annular space whose radial length is the protruding length of the cam roller 90.

The groove 35c is provided with a rolling element 35d (a reference numeral is given only at one place) that can be in rolling contact with the cam roller 90. The rolling element 35d is cam roller 90 is provided to prevent the rotation around the axis when the cam roller 90 that rotates about the axis C ₁ of the rotary shaft 1 is brought into contact with the side wall of the groove 35c . That is, the rolling element 35d is disposed on the cam roller support portion 35a that forms the side wall of the groove portion 35c. Here, a plurality of rolling elements 35d are arranged over the entire circumference of the groove 35c. 2 and 7 illustrate a needle bearing as the rolling element 35d, but a ball bearing may be used instead.

  The axial direction moving mechanism 31 supports the spectacles fork 35 and the motor 32, the motion conversion mechanism 33 that switches the rotational motion of the output shaft 32 a of the motor 32 to a linear motion, and the spectacles fork 35. And a fork support portion 34 that is linearly moved by the motion conversion mechanism 33. As the motor 32, a stepping motor can be used.

Hereinafter, with reference to FIGS. 2 and 7, the axial movement mechanism 31 will be described in the order of the fork support portion 34 and the motion conversion mechanism 33.
The fork support portion 34 is formed in a cylindrical shape having a cylindrical shaft concentric with the output shaft 32 a of the motor 32. An output shaft 32 a of the motor 32 is inserted into the fork support portion 34.
Further, the fork support portion 34 has a female screw portion 34a threadedly engaged with a male screw portion 32b formed on the output shaft 32a of the motor 32 on the inner periphery, and is engaged with the bridge portion 35b of the glasses fork 35 on the outer periphery. A fork groove 34b is recessed.

  The fork groove 34b is formed to have a width (axial length) corresponding to the thickness (axial length) of the bridge portion 35b of the glasses fork 35. An intermediate portion (between the two composite sprockets 5 and 5) of the bridge portion 35b is engaged with the fork groove 34b.

The motion conversion mechanism 33 includes a male screw portion 32b of the output shaft 32a and a female screw portion 34a of the fork support portion 34. When the output shaft 32a rotates, the fork support portion 34 in which the female screw portion 34a is formed is moved in the axial direction by screwing the male screw portion 32b and the female screw portion 34a. That is, the axial direction moving mechanism 31 converts the rotational motion of the motor 31 into a linear motion by the motion converting mechanism 33 and causes the fork support portion 34 to linearly move in the axial direction by this linear motion.
The relative rotation drive mechanism 30 including the glasses fork 35 and the axial movement mechanism 31 is provided so as to be shifted in the axial direction from the pinion sprockets 21, 22, and 23.

Hereinafter, the relative rotation drive of the movable disk 19 with respect to the fixed disk 10 by the relative rotation drive mechanism 30 will be described.
When the fork support 34 is linearly moved in the axial direction by the axial movement mechanism 31, an axial force is transmitted to the cam roller 90 via the glasses fork 35 that engages the fork support 34, and the cam roller 90 is also axially moved. Moved to.

When the cam roller 90 of the first cam groove 15a and the second cam groove 16a is disposed in the second intersection CP ₂ crossing is moved in the axial direction, also moves in the second axial intersection CP _2. Since the first rotating portion 15 first cam groove 15a is provided to rotate integrally with the rotary shaft 1 and the fixed disk 10, when the second intersection CP ₂ is moved in the axial direction, first with respect to the first rotating portion 15 The second rotating portion 16 provided with the two cam grooves 16a is relatively rotated.

  Since the second rotating unit 16 rotates integrally with the movable disk 19 and the first rotating unit 10 rotates integrally with the fixed disk 10, the second rotating unit 16 is fixed when the second rotating unit 16 is rotated relative to the first rotating unit 15. The movable disk 19 is rotated relative to the disk 10.

When the movable disk 19 is driven to rotate relative to the fixed disk 10, the movable radial movement of the sprocket fixed radial grooves 11a, 11b, and 11c provided in the fixed disk 10 is possible as will be described later with reference to the moving mechanisms 40A and 40B. first intersection CP ₁ of the sprocket movable radial grooves 19a provided on the disk 19 intersect is moved in the radial direction.
Thus, relative rotation drive mechanism 30 drives rotates relative to the fixed disk 10 the movable disk 19 by the axial movement mechanism 31 moves the first intersection CP ₁ in the radial direction.

[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 fixed disk 10 formed with fixed radial grooves 11a, 11b, and 11c for sprockets in which support shafts 21a, 22a, and 23a provided in pinion sprockets 21, 22, and 23 are inserted, and a sprocket. The movable disk 19 is provided with a movable radial groove 19a and a relative rotation drive mechanism 30 (see FIGS. 2 and 7).

The rod moving mechanism 40B includes a fixed disk 10 in which the rod fixed radial groove 12 into which the rod support shaft 29a is inserted, a movable disk 19 in which the rod movable radial groove 19b is formed, and a relative rotation 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. 5 (a) to 5 (c).
FIG. 5A shows the support shafts 21a, 22a, 23a of the pinion sprockets 21, 22, 23 (see FIGS. 1 and 2, etc.) in the radial grooves 11a, 11b, 11c, 19a and the rod support in the radial grooves 12, 19b. It shows what the shaft 29a is located at the closest position from the axis C ₁ of the rotary shaft 1. In this case, when the rotational phase of the movable disk 19 is changed with respect to the fixed disk 10 by the relative rotation drive mechanism 30 (see FIG. 2), the fixed radial grooves 11a for the sprocket are sequentially displayed in the order of FIGS. , 11b, 11c and the first intersection CP ₁ of the sprocket movable radial grooves 19a intersect, the intersection of the rod fixed radial grooves 12 and the rod movable radial grooves 19b are of the rotary shaft 1 axis C Move away from 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.

[1-1-3-3. Mechanical rotation drive mechanism)
Next, the mechanical rotation driving mechanism 50 will be described with reference to FIGS. 2 and 6. Here, since the mechanical rotation driving mechanism 50 is configured symmetrically with the pinion sprocket 20 in between, the description will be made focusing on the configuration on one side (the upper side in 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.
However, the mechanical rotation drive mechanism 50 also has a configuration that does not rotate the fixed pinion sprocket 21 when moving in the radial direction.

First, a configuration for preventing the fixed pinion sprocket 21 (see FIG. 1) from rotating in the mechanical rotation driving mechanism 50 will be described.
As shown in FIG. 6, the support shaft 21 a of the fixed pinion sprocket 21 is inserted through the fixed radial groove 11 a for the sprocket of the fixed disk 10. A guide member 59 is integrally coupled to the support shaft 21a.

  The guide member 59 is inserted into the sprocket fixed radial groove 11a and guided in the radial direction. The guide member 59 is formed in a corresponding shape (arc shape) so as to contact the sprocket fixed radial groove 11a over a predetermined length in the radial direction. Therefore, when a rotational force that rotates the fixed pinion sprocket 21 is applied, the guide member 59 transmits the rotational force to the fixed radial groove 11a for the sprocket and is fixed by a reaction (resistance force) of this rotational force. It can be said that the pinion sprocket 21 is fixed. That is, the guide member 59 is formed in a shape that is slidable in the radial direction in the fixed radial groove 11a for the sprocket and has a function of preventing rotation. 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. 6, the guide member 59 which has the shape along the circular arc shape of the fixed radial groove 11a for sprockets is shown.
Further, if bearings are attached to the side walls of the guide member 59 in contact with the inner wall of the fixed radial groove 11a for the sprocket, 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. The racks 53 and 54 respectively corresponding to the pinions 51 and 52 are fixed along the arc formed by the fixed radial grooves 11b and 11c for the sprocket.
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. 6, the first rack 53 is disposed 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.
Although not shown in detail, the pinions 51 and 52 and the racks 53 and 54 are formed so that the rotational phase of the first pinion 51 and the rotational phase of the second pinion 52 are the same. That is, the rotation amounts of the pinions 51 and 52 when the rotation pinion sprockets 22 and 23 move in the radial direction are set to be the same rotation amount.

  In addition, a disc spring may be interposed between the support shaft 22 a and the first pinion 51 in the first rotation pinion sprocket 22 instead of the above-described phase shift allowable power transmission mechanism. According to this disc spring, the first rotation pinion sprocket 22 and the chain 6 that can be generated during the change of the gear ratio are controlled by restricting the relative rotation while allowing the minute rotation between the support shaft 22a and the first pinion 51. Absorbs the shock (shock) at the time of meshing. This disc spring can be similarly applied to each of the fixed pinion sprocket 21 and the second rotation pinion sprocket 23.

[1-2. chain〕
Next, the chain 6 will be described.
As shown in FIG. 9, the number of 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 around the pinion sprocket 20 with the pitch shifted from each other so as to shift the phase in the power transmission direction. 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”. .

[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.

[2-1. Action)
Here, the case where one composite sprocket 5 is reduced in diameter and the other composite sprocket 5 is increased in diameter is taken as an example, and the operation will be described with reference to FIG.
In one composite sprocket 5, the support shaft 20 a of the pinion sprocket 20 is positioned on the inner peripheral portion 11 i of the fixed radial groove 11 for the sprocket of the fixed disk 10. Torque reaction force F _i and centrifugal force F ₁ act on the support shaft 20a.

The torque reaction force F _i acts at a magnitude corresponding to the transmission torque of the one and other composite sprockets 5, 5 and the chain 6. Further, the torque reaction force F _i is orthogonal to the radial direction of the fixed disk 10 and acts toward the retard side with reference to the revolution direction (the rotation direction of the fixed disk 10).
The torque reaction force F _i includes a first component force F _i1 that is input perpendicularly to the wall portion 11w that defines the sprocket fixed radial groove 11, and a second component force F _i2 that is orthogonal to the first component force F _i1. Can be broken down into This second component force F _i2 acts in a direction toward the inner peripheral end 111 along the inner peripheral part 11i.

The centrifugal force F ₁ is the product of the square of the angular velocity ω ₁ corresponding to the rotational speed of the rotating shaft 1 (the rotating speed of the fixed disk 10) and the radial position r _i (the distance from the axis C ₁ of the rotating shaft 1). Acts according to the size. Further, the centrifugal force F ₁ (∝r _i ω ₁ ² ) acts in the radial direction of the fixed disk 10 toward the outer peripheral side.
The centrifugal force F ₁ is applied to a first component force F ₁₁ that is input perpendicularly to the wall portion 11 w that partitions the sprocket fixed radial groove 11 and a second component force F ₁₂ that is orthogonal to the first component force F _11. Can be disassembled. The second component force F ₁₂ acts in a direction toward the radial intermediate portion 112 along the inner peripheral portion 11i.

In the other composite sprocket 5, the support shaft 20 a of the pinion sprocket 20 is positioned on the outer peripheral portion 11 o of the sprocket fixed radial groove 11 of the fixed disk 10. A torque reaction force F _o and a centrifugal force F ₂ act on the support shaft 20a.

The torque reaction force F _o acts with a magnitude corresponding to the transmission torque according to the transmission torque of the one and other composite sprockets 5, 5 and the chain 6. Further, the torque reaction force F _o is orthogonal to the radial direction of the fixed disk 10 and acts toward the retard side with reference to the revolution direction (the rotation direction of the fixed disk 10).
The torque reaction force F _o includes a first component force F _o1 that is input perpendicularly to the wall portion 11w that defines the sprocket fixed radial groove 11, and a second component force F _o2 that is orthogonal to the first component force F _o1. Can be broken down into This second component force F _o2 acts in the direction toward the outer peripheral end 113 along the outer peripheral part 11o.

The centrifugal force F ₂ is the product of the square of the angular velocity ω ₂ corresponding to the rotational speed of the rotating shaft 1 (the rotating speed of the fixed disk 10) and the radial position _ro (the distance from the axis C ₁ of the rotating shaft 1). Acts according to the size. Further, the centrifugal force ^{_{F 2 (αr o ω 2 2}} ) acts toward a radial direction of the fixed disk 10 to the outer peripheral side.
The centrifugal force F ₂ is applied to a first component force F ₂₁ that is input perpendicularly to the wall 11 w that defines the sprocket fixed radial groove 11 a and a second component force F ₂₂ that is orthogonal to the first component force F _21. Can be disassembled. The second component force F ₂₂ acts in a direction toward the radial intermediate portion 112 along the outer peripheral portion 11o.

Thus, the torque reaction forces F _i and F _o and the centrifugal forces F ₁ and F ₂ act in directions orthogonal to each other.
The speed of the chain 6 (peripheral speed of the composite sprocket 5,5), since equal to one circumferential speed of the composite sprocket 5 (αr _i ω ₁₎ and the other circumferential speed of the composite sprocket 5 (αr _o ω ₂₎ One centrifugal force F ₁ (∝r _i ω ₁ ² ) is larger than the other centrifugal force F ₂ (∝r _o ω ₂ ² ). In addition, as one composite sprocket 5 is reduced in diameter (as the other composite sprocket 5 is expanded in diameter), the difference between _one centrifugal force F ₁ and the other centrifugal force F ₂ increases.

At this time, the second component force F ₁₂ of the larger centrifugal force F ₁ and the second component force F _i2 of the torque reaction force F _i act in opposite directions, and the _{second component} of the smaller centrifugal force F ₂ . The component force F ₂₂ and the second component force F _o2 of the torque reaction force F _o act in the same direction.

[2-2. effect〕
Therefore, according to the continuously variable transmission mechanism of the present embodiment, the fixed radial groove 11 for the sprocket is radially intermediate from each of the inner peripheral end 111 and the outer peripheral end 113 with reference to the rotational direction of the fixed disk 10. The pinion sprocket 20 is formed so as to deviate toward the advance side as it goes to the portion 112, so that when the support shaft 20 a of the pinion sprocket 20 is positioned closer to the inner peripheral side end 111 than the radial intermediate portion 112, the pinion sprocket The support shaft 20a of the pinion sprocket 20 can be acted as a force for moving the support shaft 20a of the pinion sprocket 20 toward the inner peripheral side along the fixed radial groove 11 for the sprocket. When positioned on the 113 side, the support shaft 20a of the pinion sprocket 20 is moved to the outer peripheral side along the fixed radial groove 11 for the sprocket. It can act as a force that.

Specifically, as described above in the operation, in the fixed radial groove 11 for sprocket, the second component F ₁₂ of the larger centrifugal force F ₁ acting on the inner peripheral portion 11 _i and the second of the torque reaction force F _i are applied. The component force F _i2 is applied in the opposite direction, and the second component force F ₂₂ of the smaller centrifugal force F ₂ acting on the outer peripheral portion 11o and the second component force F _o2 of the torque reaction force F _o are the same. Can act in the direction.
In this way, the torque reaction forces F _i and F _o are applied in the opposite direction to the larger centrifugal force F ₁ and in the same direction as the smaller centrifugal force F ₂ . The difference between the centrifugal force F ₁ acting on the pinion sprocket 20 and the centrifugal force F ₂ acting on the pinion sprocket 20 in the other composite sprocket 5 can be suppressed. As a result, the shift controllability can be improved.

The fixed radial groove 11 for the sprocket is formed in an arc shape, and the first angle α applied to the inner peripheral portion 11i increases as it approaches the inner peripheral end 111, and the second angle applied to the outer peripheral portion 11o. Since β increases as it approaches the outer peripheral side end portion 113, the second component with respect to the torque reaction forces F _i and F _o increases as the difference between _one centrifugal force F ₁ and the other centrifugal force F ₂ increases. The ratio of the forces F _i2 and F _o2 can be increased, and the difference between the centrifugal forces F ₁ and F ₂ can be appropriately suppressed.

The fixed radial grooves 11 for sprockets are arranged so that the radial distances between the inner peripheral side end portion 111 and the outer peripheral side end portion 113 and the radial intermediate portion 112 are equal to each other. When the tangent radii are equal to each other, that is, when one centrifugal force F ₁ and the other centrifugal force F ₂ are equal, all components of the torque reaction forces F _i and F _o act on the wall portion 11w, and the centrifugal force The state where the forces F ₁ and F ₂ are balanced can be maintained. As a result, the shift controllability can be improved.

Thus, by suppressing the difference between the centrifugal forces F ₁ and F ₂ , it is possible to suppress energy applied to the relative rotation drive of the movable disk 19 relative to the fixed disk 10 by the relative rotation drive mechanism 30.

[Modification]
Next, a modification according to an embodiment of the present invention will be described.
The continuously variable transmission mechanism of this modification is different from the above in the shape of the fixed radial groove for the sprocket. In the following description, the different points will be described. Except for the differences described here, the configuration is the same as the configuration of the above-described embodiment, and these are denoted by the same reference numerals and will not be described in detail.

As shown in FIG. 10, the fixed radial groove 11 ′ for sprockets of this modification is linearly formed between the inner peripheral end 111 ′ and the outer peripheral end 113 ′ and the radial intermediate portion 112 ′. Has been. That is, both the inner peripheral part 11i ′ and the outer peripheral part 11o ′ are formed in a straight line.
In other words, the fixed radial groove 11 ′ for the sprocket is formed in a “<” shape. In the fixed radial groove 11 'for sprockets, the upper and lower ends of the "<" character correspond to the inner peripheral end 111' and the outer peripheral end 113 ', and the "<" corners are fixed disks. 10 points in the rotational direction (revolution direction) and corresponds to the radial intermediate portion 112 ′. Further, the angle of the angle of the “<” character, that is, the angle corresponding to the first angle α and the second angle β in the above-described embodiment can be appropriately set according to the assumed centrifugal force. .

  According to the continuously variable transmission mechanism of this modification, the fixed radial groove 11 ′ for the sprocket is linear between the inner peripheral end 111 ′ and the outer peripheral end 113 ′ and the radial intermediate portion 112 ′. Since it is formed, formation is easy and manufacturing cost can be suppressed. Moreover, the linear racks 53 and 54 can be used, and component cost can also be suppressed.

[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 composition of one embodiment and a modification mentioned above can be chosen as needed, and may be combined suitably.
The radial distances L ₁₂ and L ₂₃ between the inner peripheral end portions 111 and 111 ′ and the outer peripheral end portions 113 and 113 ′ and the radial intermediate portions 112 and 112 ′ of the fixed radial grooves 11 and 11 ′ for the sprocket are respectively It can be freely set according to the surrounding configuration, required specifications, etc., and may not be equal to each other (L ₁₂ ≠ L ₂₃ ).

  Moreover, although the thing arrange | positioned in order of the movable disk 19 and the fixed disk 10 from the several pinion sprocket 20 side was illustrated, arrangement | positioning and the number of disks are not restricted to this, Various arrangement | positioning and number can be employ | adopted. For example, as a disk corresponding to the fixed disk 10, a first fixed disk and a second fixed disk may be disposed on the inner side and the outer side of the movable disk 19 in the axial direction. In this case, the fixed radial grooves 11a, 11b, 11c for the sprocket and the fixed radial grooves 12 for the rod can be formed on the first fixed disk, and the fixed radial grooves 11a, 11b, 11c for the sprocket can be formed on the second fixed disk. The grooves 53 can be formed and the racks 53 and 54 can be fixed. Thus, the first fixed disk (radial movement fixed disk) for moving the pinion sprocket in the radial direction and the second fixed disk (rotation fixed disk) for rotating the pinion sprocket may be provided. In the above-described embodiment, it can be said that the fixed disk 10 serves as both the first fixed disk and the second fixed disk described above.

1 Rotating shaft 5 Composite sprocket 6 Chain 10 Fixed disk (fixed disk for radial movement, fixed disk for rotation)
10p plate 11, 11 ', 11a, 11b, 11c Fixed radial groove for sprocket (fixed pinion sprocket guide groove)
111, 111 'Inner peripheral end 112, 112' Radial intermediate portion 113, 113 'Outer peripheral end 11i, 11i' Inner peripheral portion 11o, 11o 'Outer peripheral portion 12 Rod fixed radial groove 15 First rotating portion 15a 1st cam groove 16 2nd rotation part 16a 2nd cam groove 17 Connection part 17a Axial connection part 17b Radial direction connection part 17c Thickening part 19 Movable disk (movable disk for radial direction movement)
19a Movable radial groove for sprocket 19b Movable radial groove for rod 19A Connecting shaft 20 Pinion sprocket 21 Fixed pinion sprocket 22 First rotation pinion sprocket (advanced side rotation pinion sprocket)
23 Second-rotation pinion sprocket (retarded-side rotation pinion sprocket)
21a, 22a, 23a Support shaft 29 Guide rod 29a Rod support shaft 29b Guide member 30 Relative rotation drive mechanism 31 Axial movement mechanism 32 Motor 33 Motion conversion mechanism 34 Fork support part 35 Glasses fork (Axial force transmission member)
40A Sprocket moving mechanism 40B Rod moving 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 90 Cam roller 90a One end C ₁ , C ₂ , C ₃ , C ₄ axis CP ₁ 1st intersection location CP ₂ 2nd intersection location F _i , F _o torque reaction force F _i1 , F _o1 first component force F _i2 , F _o2 second component force F ₁ , F ₂ centrifugal force F ₁₁ , F ₂₁ first component force F ₁₂ , F ₂₂ second component force r ₁ minimum diameter r ₂ intermediate diameter r ₃ maximum diameter L ₁₂ , L ₂₃ Radial distances θ ₁ , θ ₂ , θ ₃ Phase α First angle β Second angle

Claims (5)

A rotating shaft to which power is input or output, a plurality of pinion sprockets supported movably in the radial direction with respect to the rotating shaft, and the plurality of pinion sprockets while maintaining an equal distance from the axis of the rotating shaft Two sets of composite sprockets having a sprocket moving mechanism that moves in synchronization with the radial direction, and a chain wound around the two sets of composite sprockets, surrounding each of the plurality of pinion sprockets, and A continuously variable transmission mechanism that changes a gear ratio by changing a tangent radius that is a radius of a circle that contacts any of a plurality of pinion sprockets,
The sprocket moving mechanism is
A fixed radial groove for sprocket into which each support shaft of the plurality of pinion sprockets is inserted, and a fixed disk that rotates integrally with the rotary shaft;
A movable radial groove for a sprocket in which the support shaft is located is formed at an intersection where the fixed radial groove for the sprocket intersects, and a movable disk that is concentrically arranged with respect to the fixed disk and is relatively rotatable.
The fixed radial groove for the sprocket is
Based on the rotation direction of the fixed disk, it is formed so as to deviate toward the advance side from each of the inner peripheral end and the outer peripheral end toward the radial intermediate portion. Step shifting mechanism. The continuously variable transmission mechanism according to claim 1, wherein the fixed radial groove for the sprocket is formed in an arc shape. The fixed radial groove for the sprocket is
2. The continuously variable transmission mechanism according to claim 1, wherein a space between each of the inner peripheral side end and the outer peripheral side end and the radial intermediate portion is linearly formed. The fixed radial groove for the sprocket is
4. The apparatus according to claim 1, wherein the radial distance between each of the inner peripheral end and the outer peripheral end and the radial intermediate portion is equal. The continuously variable transmission mechanism according to the item. The sprocket moving mechanism is
5. The rotary drive mechanism according to claim 1, further comprising a relative rotary drive mechanism that drives the movable disk to rotate relative to the fixed disk and moves the intersection in the radial direction. 6. The continuously variable transmission mechanism described.

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