JP2016109262A - Transmission mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To apply restriction force for restricting rotation while permitting smooth movement in a radial direction of pinion sprockets, in a transmission mechanism composed of composite sprockets formed by a plurality of pinion sprockets.SOLUTION: A transmission mechanism includes two sets of composite sprockets having a plurality of pinion sprockets and moving mechanisms for moving them in a radial direction, and a chain wound on the composite sprockets, and further has a pair of guide wall portions 56 opposed to each other to guide the radial movement of the pinion sprockets, slide members 59 disposed on the pinion sprockets and having opposite wall portions 59a opposed to the guide walls 56 in parallel, and bearings 55b respectively held between the guide wall portion 56 and the opposite wall portion 59a opposed thereto by a holding member 55a and kept into contact with the guide wall portion 56 and the opposite wall portion 59a in a rolling manner. Rolling supporting members 55 are disposed to guide the parallel movement of the opposite wall portions 59a while rolling the bearings 55b in accompany with the radial movement of the pinion sprockets.SELECTED DRAWING: Figure 1

Description

  The present invention includes a plurality of pinion sprockets that are supported movably in the radial direction while maintaining an equal distance from the rotation shaft and revolve with respect to the rotation shaft so as to rotate integrally, and a chain wound around these. The present invention relates to a transmission mechanism for transmitting power.

  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 them without using the above thrust and frictional force.

  As such a continuously variable transmission mechanism, a plurality of pinion sprockets that are movably supported in the radial direction while maintaining an equal distance from the rotation shaft and that revolve with respect to the rotation shaft so as to rotate integrally are polygonal. An apparent large sprocket (herein referred to as a “composite sprocket”) formed in a composite so as to form the apex of each is provided on each of the input side and the output side. For example, Patent Literature 1 and Patent Literature 2 disclose power transmission using a wound 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.

  In Patent Document 1, two disks (spindles) are arranged in parallel on one side of a plurality of pinion sprockets, radial grooves are provided in each disk, and radial grooves (hereinafter referred to as a fixed disk) that rotate integrally with a rotating shaft. The first radial groove and the second radial groove are arranged so as to intersect with each other (referred to as “second radial groove”) and a radial groove (hereinafter referred to as “second radial groove”) of the movable disk that can rotate with respect to the rotation axis. The sprocket shaft is supported at the location where the radial grooves intersect. When the relative angle (phase) between the fixed disk and the movable disk is changed, the intersection of the first radial groove and the second radial groove moves in the radial direction, so that each pinion sprocket pivotally supported at the intersection Is moved in the radial direction by the relative rotation of both disks.

  Further, in Patent Document 1, grooves along the circumferential direction are formed at respective positions corresponding to each other of the fixed disk and the movable disk, and the grooves are urged so that the rotational phases of the fixed disk and the movable disk are matched. It is shown that a spring is provided, and the spring expands and contracts according to the magnitude of the input and the load on the output side, and the movable disk rotates relative to the fixed disk.

  In Patent Document 2, a female frame is provided on a slide frame to which each pinion sprocket is attached, and a power distribution device that rotates each male screw attached to the female screw is a polygonal center formed by a plurality of pinion sprockets. Is provided. By rotating the same number of male screws simultaneously by this power distribution device, each sprocket is moved in the radial direction.

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

  By the way, when the transmission mechanism is constituted by the “composite sprocket”, it is necessary to restrain the rotation of the pinion sprocket because the power cannot be transmitted if the pinion sprocket automatically rotates. This restriction is not limited to the case where the rotation of the pinion sprocket is completely restricted regardless of the radial position (hereinafter referred to as rotation restriction), but is restricted so that the phase is in accordance with the radial position of the pinion sprocket. Including the case of rotating.

  Since the pinion sprocket moves in the radial direction when changing the transmission gear ratio, when the pinion sprocket is restricted to rotate, it is necessary to restrict the rotation while smoothly allowing the pinion sprocket to move in the radial direction. However, since the pinion sprocket has a small diameter and, naturally, the shaft of the pinion sprocket has a smaller diameter, it is not easy to apply a restraining force that restricts rotation while allowing the pinion sprocket to move smoothly in the radial direction.

The present invention was devised in view of the above-described problems, and in a structure in which a speed change mechanism is configured by a composite sprocket formed by combining a plurality of pinion sprockets, the diameter of the pinion sprocket that restricts rotation is determined. It is a first object of the present invention to provide a speed change mechanism that can apply a restraining force that restricts rotation while allowing direction movement smoothly.
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 speed change mechanism according to the present invention includes a rotating shaft to which power is input or output, a plurality of pinion sprockets supported in a radial direction with respect to the rotating shaft, and a plurality of pinion sprockets. Two sets of composite sprockets, each having a plurality of pinion sprockets and a moving mechanism that moves the plurality of pinion sprockets and the plurality of guide rods synchronously in the radial direction while maintaining an equal distance from the axis of the rotating shaft. , A chain wound around the two sets of composite sprockets, enclosing both of the plurality of pinion sprockets and the plurality of guide rods and in contact with any of the plurality of pinion sprockets and the plurality of guide rods. A speed change mechanism that changes a gear ratio by changing a tangent radius that is a radius of a circle, the radial direction of the pinion sprocket A pair of opposing guide walls for guiding the movement, a slide member provided on the pinion sprocket and provided with opposing walls arranged in parallel with the respective guide walls, and the guide walls opposed to the guide wall Between the opposing wall portion, there is a bearing that is held by a holding member and is in rolling contact with the guide wall portion and the opposing wall portion, while rolling the bearing as the pinion sprocket moves in the radial direction. The rolling support member which guides the parallel movement of the said opposing wall part is interposed, It is characterized by the above-mentioned.
The bearing is a needle bearing having a rotational axis that is orthogonal to the radial direction in which the pinion sprocket moves, and it is preferable that all the opposing wall portions always make line contact with at least two needle bearings.

  (2) The plurality of pinion sprockets include a rotation pinion sprocket that rotates in a phase corresponding to a radial position, a fixed pinion sprocket that is restricted in rotation so as to always have a constant phase state regardless of the radial position, And a mechanical rotation drive mechanism that rotates the rotation pinion sprocket according to a radial position, and the stationary pinion sprocket is guided by the rolling support member in the radial direction.

  (3) The moving mechanism is formed with a fixed radial groove for sprocket in which a support shaft provided in each of the plurality of pinion sprockets is inserted, and the radial moving fixed disk that rotates integrally with the rotating shaft; A movable radial groove for a sprocket that intersects with a fixed radial groove for a sprocket and at which the support shaft is located is formed, is disposed concentrically with the fixed disk for a radial movement, and is capable of relative rotation. A pair of guides, comprising: a movable disk; and a relative rotation drive mechanism for moving the movable disk for radial movement relative to the fixed disk for radial movement to move the intersection in the radial direction. The wall portion is provided on the radial movement fixed disk, and the mechanical rotation driving mechanism includes a radial movement fixed disk that rotates integrally with the rotary shaft. A rack which is fixedly provided along the radial direction, preferably has a pinion which the rack meshing is fixed to rotate integrally with the support shaft of the rotation pinion sprocket.

  (4) It is preferable that a bearing is interposed between the support shaft of the pinion sprocket and at least one of the radial radial groove for the sprocket and the radial radial groove for the sprocket.

  According to the speed change mechanism of the present invention, there is provided a bearing that is in rolling contact with the wall portion between the guide wall portion that guides the radial movement of the pinion sprocket and the opposing wall portion that is disposed to face and parallel to the guide wall portion. Since the rolling support member is interposed, the bearing rolls as the pinion sprocket moves in the radial direction, and it is possible to give a restraining force that reliably restricts rotation while allowing the radial movement smoothly. become able to.

FIG. 2 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 speed change mechanism according to an embodiment of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an axial sectional view (longitudinal sectional view) schematically showing a main part focused on a radial rotation relative rotational drive mechanism such as a pinion sprocket of a speed change mechanism according to an embodiment of the present invention. 1 shows a fixed disk and a movable disk for radial movement such as a pinion sprocket in a speed change mechanism according to an embodiment of the present invention, and pinion sprockets and guide rod support shafts moved by these disks, and a sprocket moving mechanism and rod movement It is a figure explaining a 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 transmission mechanism concerning one Embodiment of this invention. 4 is a cross-sectional view taken along arrow AA in FIG. It is radial direction sectional drawing of the transmission mechanism concerning one Embodiment of this invention. FIG. 5 is a cross-sectional view taken along line BB in FIG. It is a principal part enlarged view which expands and shows the 1st cam groove and 2nd cam groove of the transmission mechanism concerning one Embodiment of this invention. This FIG. 6 is a CC arrow view of FIG. FIG. 3 is a perspective view schematically showing a part of a chain of a speed change mechanism according to an embodiment of the present invention and a guide rod that guides the chain. It is a figure which shows the rolling support member with which the fixed disk of the transmission mechanism concerning one Embodiment of this invention was equipped, (a), (b) is a front view of the half part of a fixed disk, (c) is It is an enlarged view of the EE arrow cross section of Fig.8 (a). It is a figure which shows the structure around the support shaft of the transmission mechanism concerning one Embodiment of this invention, and is equivalent to the D section enlarged view of FIG.

  Hereinafter, an embodiment according to a transmission mechanism of the present invention will be described with reference to the drawings. The speed change mechanism of this embodiment is suitable for use in a vehicle transmission. In the present embodiment, the side near the axis of the rotation shaft (revolution shaft side) in the speed change mechanism will be described as the radially inner side, and the opposite side will be described as the radially outer side. In addition, the side that is separated from the plurality of pinion sprockets along the axis of the rotation shaft is referred to as the axially outer side, and the opposite side is described as the axially inner side.

Hereinafter, a transmission mechanism according to an embodiment will be described.
[1-1. (Configuration of transmission mechanism)
As shown in FIG. 1, the speed change 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 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 and a plurality of (here, fifteen) guide rods 29 supported so as to be movable in the radial direction with respect to the rotating shaft 1. have. 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.

  In this speed change mechanism, 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 is changed (expanded / reduced diameter). The gear ratio is changed by. Since the gear ratio can be continuously changed, it can be configured as a continuously variable transmission mechanism, but can also be changed in stages to be configured as a multi-stage stepped transmission mechanism.

  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 speed change mechanism changes the speed 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 structure of the speed change mechanism will be described in the order of the composite sprocket 5 and the chain 6 wound around the composite sprocket 5.

[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, and the mechanical rotation driving mechanism 50 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 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.

  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.

  Note that the number of gear rows of each pinion sprocket 21, 22, 23 depends on the magnitude of the transmission torque of the speed change 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 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.

  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 10 that rotates integrally with the rotary shaft 1, a movable disk 19 that is arranged concentrically with the fixed disk 10 and that can rotate relative to the fixed disk 10, and a first disk that rotates integrally with the fixed disk 10. Each of the rotation unit 15, the second rotation unit 16 that rotates integrally with the movable disk 19, and the relative rotation drive mechanism 30 that drives the movable disk 19 to rotate relative to the fixed disk 10 will be described in this order.

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 the drawing in FIG. 2, the configuration will be described.

[1-1-1-3-1-1. (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 has fixed radial grooves 11a, 11b, 11c for the sprockets and fixed radial grooves 12 for the rods provided for the pinion sprockets 21, 22, 23 (see FIG. 1). Two types of radial grooves are formed (only one place is given a reference numeral).
The fixed radial grooves for sprockets 11 a, 11 b, and 11 c are provided corresponding to each of the pinion sprockets 20, and the fixed radial grooves for rod 12 are provided corresponding to each of the guide rods 29.

The support shafts 21a, 22a, and 23a of the 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 is 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 rotation pinion sprocket 22 is used. The fixed radial groove 11b is a groove that 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 is the radial direction of the second rotation pinion sprocket 23. It is a groove that 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.
In addition, rod support shafts 29a of each guide rod 29 (indicated by reference numerals only at one place) are inserted into the fixed radial grooves 12 for rods.

[1-1-1-3-1-2. (Movable disc)
The movable disk 19 (shown by a broken line) is formed with two types of movable radial grooves, a movable radial groove 19a for a sprocket and a movable radial groove 19b for a rod (both are shown by a broken line with only one reference numeral). Has been. 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.

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. 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.

  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.

[1-1-1-3-1-3. (First rotating part)
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, as shown in FIG. 2, 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, 4 and 5, the first rotating portion 15 is provided with a first cam groove 15 a. 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. 5 illustrates an example in which the first cam groove 15a (only one place is given 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.

[1-1-1-3-1-4. (Second rotating part)
As shown in FIGS. 2, 4, and 5, the second rotating unit 16 is connected to the movable disk 19 via the connection unit 17. In FIGS. 4 and 5, a counterclockwise revolution direction is indicated by a white arrow.
First, the connection part 17 is demonstrated.

The connection portion 17 is disposed so as to cover the fixed disk 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 this connection portion 17, of the connection between the movable disk 19 and the second rotation portion 16, the axial component 17 a is connected to the axial component separation, and the radial separation is connected. 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, 4, and 5, 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 FIGS. 4 and 5, the radial connection portion 17b is provided with a lightening portion 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. 4 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, 4, and 5, 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 6, 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 axial direction of the rotary shaft 1 while intersecting the first cam groove 15a.
FIG. 5 shows an example in which the second cam groove 16a (a reference numeral is attached to only one place) is provided at three places at intervals in the circumferential direction. The number of formations is set according to the formation location and the number of formations of the first cam grooves 15a.

[1-1-1-3-1-5. (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 second intersection CP ₂ cam roller 90 disposed to the second cam groove 16a intersects, speed change gear shift fork for transmitting the axial force against the cam roller 90 (axial force transmission member) 35 and The shift fork 35 is provided with an axial movement mechanism 31 for moving in the axial direction.

Hereinafter, the cam roller 90, the speed change fork 35, and the axial movement mechanism 31 will be described in this order.
As shown in FIGS. 2 and 5, 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. On the outer periphery of the cam roller 90, a bearing 91a is externally fitted at a location corresponding to the first cam groove 15a, and a bearing 91b is externally fitted at a location corresponding to 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 transmission fork 35 is provided across the two composite sprockets 5 and 5. The speed change fork 35 includes an annular cam roller support portion 35a (referenced only on one side) provided corresponding to each of the composite sprockets 5, 5, and a bridge portion 35b for connecting the cam roller support portions 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 speed change 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.

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 portion 35 c forms 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 5 illustrate a needle bearing as the rolling element 35d, but a ball bearing may be used instead.

  The axial movement mechanism 31 supports the motor 32, the motion conversion mechanism 33 that switches the rotational motion of the output shaft 32 a of the motor 32 to linear motion, and the speed change fork 35 in order to move the speed change fork 35 in the axial direction. In addition, a fork support portion 34 that is linearly moved by the motion conversion mechanism 33 is provided. As the motor 32, a stepping motor can be used.

Hereinafter, with reference to FIGS. 2 and 5, 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.

The fork support portion 34 is provided with a female screw portion 34 a that is screwed into an inner periphery of a male screw portion 32 b formed on the output shaft 32 a of the motor 32, and is engaged with a bridge portion 35 b of the speed change fork 35 on the outer periphery. A fork groove 34b is recessed.
The fork groove 34b is formed to have a width (axial direction length) corresponding to the thickness (axial direction length) of the bridge portion 35b of the speed change 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 transmission 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 through the speed change fork 35 that engages the fork support 34, and the cam roller 90 is also a shaft. Moved in the direction.

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

[1-1-1-3-2. 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 5).

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.
FIG. 3A shows the support shafts 21a, 22a, 23a of the pinion sprockets 21, 22, 23 (see FIG. 2 etc.) in the radial grooves 11a, 11b, 11c, 19a and the rod support shaft 29a in the radial grooves 12, 19b. There show those located closest to 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 and 11b for the sprocket are sequentially displayed in the order of FIGS. , a first intersection CP ₁ to 11c and the sprocket movable radial grooves 19a intersect, the intersection of the rod fixed radial grooves 12 and the rod movable radial grooves 19b is from the axis C ₁ of the rotary shaft 1 Move away. 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. Here, since the mechanical rotation drive mechanism 50 is configured symmetrically with the pinion sprocket 20 in between, the description will be given 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, 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. 4, 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 slide member 59 is integrally coupled to the support shaft 21a.

  As shown in FIGS. 8A to 8C, one end of the support shaft 21a of the fixed pinion sprocket 21 protrudes toward one surface of the fixed disk 10 (the outward surface facing the radial connection portion 17b). The slide member 59 is fixed to the protruding end portion of the support shaft 21a. On one surface of the fixed disk 10, a pair of opposing guide wall portions 56 for guiding the radial movement of the pinion sprocket 21 are arranged in parallel to each other along the fixed radial groove 11a for the sprocket and fixed by bolts 58. ing.

  The slide member 59 is located between the pair of guide wall portions 56 and has opposing wall portions 59 a that are arranged to face each other in parallel with the guide wall portions 56. And the rolling support member 55 is interposed between each guide wall part 56 and the opposing wall part 59a facing this. The rolling support member 55 includes a holding member 55a and a plurality of bearings 55b that are rotatably held by the holding member 55a and are in rolling contact with the guide wall portion 56 and the opposing wall portion 59a.

This rolling support member 55 is known as a linear flat roller (registered trademark), and is locked inside each guide wall portion 56 (on the slide member 59 side) by a flange portion 56a of the guide wall portion 56, and is sprocketed. It moves along the fixed radial groove 11a. The plurality of bearings 55b are needle bearings that are arranged at equal intervals in the sliding direction and whose rotation axis is arranged in a direction orthogonal to the sliding direction and are held by the holding member 55a, and the opposing wall portion 59a is always two or more bearings 55b. The size and arrangement of the bearing 55b are set so as to be in line contact with each other.
The slide member 59 is in contact with the bearings 55b of the rolling support members 55 at both opposing wall portions 59a. When the slide member 59 moves along the sprocket fixed radial groove 11a, the both rolling support members 55 are in contact with each other. Slides while rolling the bearing 55b. At this time, the rolling support member 55 moves in the same direction as the slide member 59 at half the speed of the slide member 59, and each of the rolling support members 55 holds the slide member 59 with at least two bearings 55b. Support from both sides. Accordingly, the rotation of the slide member 59 is also completely restricted.

  As shown in FIG. 8 (c), in the support shaft 21a of the fixed pinion sprocket 21, the portions of the fixed disk 10 that are in contact with the fixed radial groove 11a for the sprocket and the movable radial groove 19a for the sprocket of the movable disk 19 are A needle bearin 57 is interposed around the periphery. The needle bearers 57 are arranged in parallel with the support shaft 21a, and a plurality of needle bearers 57 are arranged in a ring around the support shaft 21a. 9 illustrates the rotation pinion sprocket 22, the fixed radial grooves 11 b and 11 c for the fixed disk 10 and the movable radial pattern for the sprocket of the movable disk 19 are also provided on the support shafts 22 a and 23 a of the rotation pinion sprockets 22 and 23. Similarly, a needle bearin 57 is interposed around the portion in contact with the groove 19a.

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 fixed disk 10 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 appropriately adjust the chain length, when the first pinion 51 rotates by the distance x, the first rotation pinion sprocket 22 needs to rotate by 2πx / 3 in the circumferential length. That is, the first rotation pinion sprocket 22 needs to rotate by 2π / 3 times 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.

[1-1-2. chain〕
Next, the chain 6 will be described with reference to FIG.
The number of the chains 6 guided by the guide rods 29 is provided corresponding to the number of gear rows (three rows here) of the pinion sprockets 21, 22, and 23. Here, three chains of a first chain 6A, a second chain 6B, and a third chain 6C are provided.
FIG. 7 shows what uses a so-called silent chain for the chains 6A, 6B, 6C, but other types of chains such as roller chains and bush chains may be used instead.

These chains 6A, 6B, 6C are provided with a pitch shifted from each other. Here, the pitch of each other is shifted by 1/3 pitch. Correspondingly, the phase of each gear of the pinion sprocket 20 meshing with each chain 6A, 6B, 6C is also shifted.
The chains 6A, 6B, and 6C are similarly configured except for the arrangement pitch.
Further, depending on the transmission torque of the speed change mechanism, two or four or more chains 6 are used. In this case, it is preferable that the pitches of the respective chains are shifted by a “1 / number of chains” pitch.

[1-2. Action and effect)
Since the speed change mechanism according to the embodiment of the present invention is configured as described above, the following operations and effects can be obtained.
First, paying attention to the relative rotational driving of the movable disk with respect to the fixed disk 10, the operation and effect will be described.

When the axial movement mechanism 31 moves the transmission fork 35 in the axial direction, the cam roller 90 in which the one end 90a is accommodated in the groove 35c of the transmission fork 35 is moved in the axial direction. The cam roller 90, since the first cam groove 15a and the second cam groove 16a is disposed in the second intersection CP ₂ crossing, when the cam roller 90 is moved in the axial direction, the in accordance with this movement two intersections CP ₂ also moves in the axial direction. When the second intersection CP ₂ is moved in the axial direction, the first cam groove 15a provided in the first rotating portion 15 and the second cam groove 16a provided in the second rotating portion 16 The two-rotation unit 16 is driven to rotate relative to the first rotation unit 15. Since the first rotating unit 15 rotates integrally with the fixed disk 10 and the second rotating unit 16 rotates integrally with the movable disk 19, the movable disk 19 is driven to rotate relative to the fixed disk 10. When the movable disk 19 is driven rotates relative to the fixed disk 10, the support shaft 21a of the first intersection CP ₁ and the sprocket 21, 22, 23 arranged in this position, 22a, 23a is moved in the radial direction The

Thus, the gear ratio can be freely changed by driving the movable disk 19 relative to the fixed disk 10 by moving the cam roller 90 in the axial direction.
Further, the relative rotation drive mechanism 30 provided with the speed change fork 35, the axial movement mechanism 31 and the like is provided by being shifted in the axial direction from the pinion sprockets 21, 22, 23, so that each pinion sprocket 21, 22, is provided. Thus, the most contracted diameter position of 23 can be made inward (closer to the rotating shaft 1), and ratio coverage can be ensured.

Since the first cam groove 15a is provided so as to be recessed along the axial direction of the rotary shaft 1, it is not necessary to add another member to provide the first cam groove 15a, and the configuration is simple. can do.
Second cam grooves 16a, since provided adjacent to the outer periphery of the first cam groove 15a which is recessed in the rotary shaft 1, these cam grooves 15a, 16a is disposed in the second intersection CP ₂ crossing The rotation speed of the cam roller 90 rotating around its own axis can be suppressed. Therefore, it can contribute to the improvement of durability. Furthermore, since the rolling part 35d which can be in rolling contact with the cam roller 90 is provided in the groove part 35c, it is possible to further suppress the cam roller 90 from rotating about its own axis.

  Since the connecting portion 17 that connects the second rotating portion 16 and the outer peripheral end portion 19t of the movable disk 19 is provided with the lightening portion 17c, the weight can be reduced. Further, since the thinned 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, the axial length of the axial connection portion 17a in the connection portion 17 is determined. Can be suppressed, and further weight saving can be achieved.

Next, focusing on the rotation of the pinion sprockets 21, 22, and 23, the operation and effect will be described.
By changing the rotational phase of the drive disc 19 against the fixed disk 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 rod relative to the axis C ₁ of the rotary shaft 1 The 29 radial positions are changed synchronously while maintaining the same 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.

  Then, the slide member 59 fixed to the support shaft 21a of the fixed pinion sprocket 21 has its opposing wall portions 59a in the reduced-diameter position shown in FIG. 8A and the FIG. It is supported so as to be able to move in the axial direction smoothly between the expanded diameter positions shown, and the opposing wall portions 59a are always in line contact with the two or more bearings 55b. The rotation of the slide member 59 is also completely restricted by the force. The pinion sprocket 21 is smoothly controlled in its radial direction while being smoothly moved in the radial direction, and the fixed pinion sprocket 21 is smoothly and appropriately operated to smoothly expand and contract the composite sprocket 5 and suppress the torque cross. Is done. Since the rolling support member 55 can be configured to be relatively small, even a compact and small-sized device can be installed.

  Further, the support shaft 21 a of the fixed pinion sprocket 21 and the support shafts 22 a and 23 a of the rotating pinion sprockets 22 and 23 are fixed radial grooves 11 a, 11 b, 11 c for the fixed disk 10 and movable radial grooves 19 a for the sprocket of the movable disk 19. Since the needle bearerin 57 is interposed in the portion in contact with the support shaft 21a, the support shafts 21a, 22a, 23a smoothly move in the radial grooves 11a, 11b, 11c, 19a.

[3. 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 embodiment mentioned above and 2nd embodiment can be selected as needed, and may be combined suitably.
In the above-described embodiment, the rolling element 35d is provided in the groove 35c, but the rolling element 35d may be omitted. In this case, a simple configuration can be obtained.

  Moreover, although the above-mentioned embodiment demonstrated what provided the thinning part 17c in the connection part 17, you may abbreviate | omit the thinning part 17c. In this case, the mechanical rotation drive mechanism 50 can be accommodated by extending the axial connection portion 17a beyond the axial length (thickness) of the racks 51, 52 and the pinions 53, 54 of the mechanical rotation drive mechanism 50. Can do.

  In the above-described embodiment, the movable disk 19 and the fixed disk 10 are arranged in this order from the plurality of pinion sprockets 20 side. However, the arrangement and number of disks are not limited to this, and various arrangements and numbers are employed. Can do. For example, a first fixed disk and a second fixed disk may be arranged on the inner side and the outer side of the movable disk 19 as the disk corresponding to the fixed disk 10. 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.

  In addition, although three pinion sprockets 20 are shown, the number of pinion sprockets 20 is not limited to this, and may be four or more, and any pinion sprocket 20 may always mesh with the chain 6. For example, the number may be two. In any case, at least one of the adjacent pinion sprockets 20 is configured as a rotating pinion sprocket 20, and radial grooves 11a, 11a, 11b, 11c, and 19a corresponding to the number of pinion sprockets 20 are provided.

  Further, in the above embodiment, the bearing 55b is a needle bearing that is arranged at equal intervals in the sliding direction and whose rotation axis is arranged in a direction perpendicular to the sliding direction and is held by the holding member 55a. Although it is set so as to be in line contact with two or more bearings 55b at all times and the rotation of the slide member 59 is completely restricted, the bearing 55b is not limited to a needle bearing. However, from the viewpoint of regulating the rotation of the slide member 59, it is preferable that the opposing wall portions 59a come into contact at at least two different locations in the slide direction.

  For example, when a ball bearing is used as the bearing 55b, the ball bearings are arranged at equal intervals in the sliding direction, and the opposing wall portion 59a is always set to be in contact with two or more ball bearings adjacent in the sliding direction. However, the rotation of the slide member 59 can be restricted. In this case, since the contact is a point contact, two rows of ball bearing rows arranged at equal intervals in the slide direction are arranged in parallel with each opposing wall portion 59a, and the slide direction is also orthogonal to the slide direction. If it is configured to always contact two or more ball bearings in the direction, the rotation of the slide member 59 can be stably regulated.

1 Rotating shaft 5 Composite sprocket 6 Chain 10 Fixed disk (fixed disk for radial movement, fixed disk for rotation)
10t outer periphery end (outer periphery)
11a, 11b, 11c Fixed radial groove for sprocket (fixed pinion sprocket guide groove)
12 Fixed radial grooves 15 and 15 ′ for rods First rotating portions 15a and 15a ′ First cam grooves 16 and 16 ′ Second rotating portions 16a and 16a ′ Second cam grooves 17 Connection portions 17a Axial connection portions 17b Radial connections Part 17c Meat removal part 19 Movable disk (movable disk for radial movement)
19a Movable radial groove for sprocket 19b Movable radial groove for rod 19t Outer peripheral end (outer peripheral part)
19A Connection shaft 20 Pinion sprocket 21 Fixed pinion sprocket 21a Sprocket 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 members 30, 30 'Relative rotation drive mechanism 31, 31' Axial movement mechanism 32 Motor 32a Output shaft 32b Male thread part 33 Motion conversion mechanism 34 Fork support part 34a Female thread part 34b Fork groove 35, 35 'Speed change fork (axial force transmission member)
35a, 35a 'Cam roller support portion 35b, 35b' Bridge portion 35c, 35c 'Groove portion 35d Rolling element 40A Sprocket moving mechanism 40B Rod moving mechanism 50 Mechanical rotation driving mechanism 51 First pinion (advanced side pinion)
52 Second pinion (retarding pinion)
53 First rack (advanced side rack)
54 Second rack (retard side rack)
55 rolling support member 55a holding member 55b bearing 56 guide wall 56a flange portion 57 the needle bare phosphorus 58 volts 59 slide members 59a facing wall 90 cam roller 90a at one end portion _{C 1, C 2, C 3} , C 4 axis CP ₁ second One intersection CP ₂ Second intersection

Claims (4)

A rotating shaft to which power is input or output, a plurality of pinion sprockets and a plurality of guide rods supported movably in a radial direction with respect to the rotating shaft, and the plurality of pinion sprockets and the plurality of guide rods are rotated. Two sets of composite sprockets having a moving mechanism that moves in synchronization with the radial direction while maintaining an equal distance from the shaft center of the shaft, and a chain wound around the two sets of composite sprockets, A transmission mechanism that changes a gear ratio by changing a contact circle radius that surrounds both the plurality of pinion sprockets and the plurality of guide rods and is in contact with the plurality of pinion sprockets and the plurality of guide rods. There,
A pair of opposing guide walls that guide the radial movement of the pinion sprocket;
A slide member provided on the pinion sprocket and having a facing wall portion disposed opposite to and parallel to each guide wall portion;
Between the guide wall part and the opposing wall part opposite to the guide wall part, there is a bearing that is held by a holding member and makes rolling contact with the guide wall part and the opposing wall part. A rolling support member that guides the parallel movement of the opposing wall portion while rolling the bearing is interposed. The plurality of pinion sprockets include a rotation pinion sprocket that rotates in a phase corresponding to a radial position, and a fixed pinion sprocket that is restricted in rotation so as to always have a constant phase state regardless of the radial position. ,
A mechanical rotation drive mechanism for rotating the rotation pinion sprocket according to the radial position;
The speed change mechanism according to claim 1, wherein the stationary pinion sprocket is guided in a radial movement by the rolling support member. The moving mechanism is
A radial radial fixed disk that is formed with a fixed radial groove for a sprocket into which a support shaft provided in each of the plurality of pinion sprockets is inserted, and rotates integrally with the rotary shaft;
A movable radial groove for the sprocket that intersects the fixed radial groove for the sprocket and at which the support shaft is located is formed, is disposed concentrically with the fixed disk for radial movement, and is capable of relative rotation. Movable disk for,
A relative rotation drive mechanism for driving the radial movement movable disk relative to the radial movement fixed disk to move the intersection in the radial direction; and
The pair of guide wall portions are provided on the radial movement fixed disk,
The mechanical rotation drive mechanism is fixedly installed so as to rotate integrally with a rack fixed in the radial direction on a fixed disk for radial movement that rotates integrally with the rotation shaft, and a support shaft of the rotation pinion sprocket. The speed change mechanism according to claim 2, further comprising a pinion that meshes with the rack. 4. The bearing according to claim 3, wherein a bearing is interposed between the support shaft of the pinion sprocket and at least one of the radial radial groove for the sprocket and the movable radial groove for the sprocket. Transmission mechanism.

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