JP6063433B2 - Speed change mechanism - Google Patents

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 continuously variable 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. Apparent large sprockets (herein referred to as “composite sprockets”) formed so as to form the vertices are provided on the input side and the output side, respectively, and are wound around these composite sprockets. For example, Patent Literature 1 and Patent Literature 2 disclose power transmission by a chain. Under such a configuration, each pinion sprocket moves synchronously in the radial direction while maintaining an equal distance with respect to the rotating shaft, and the size of the polygon changes in a similar manner. Change.

  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, in the case of a meshing sprocket chain that transmits power by meshing between the sprocket and the chain, the chain is loosened when a large torque is transmitted, and tooth skipping is likely to occur. With a normal fixed drive radius meshing sprocket chain, the initial tension can be adjusted by adjusting the length between the shafts during setting, and since the sprocket itself is single, sufficient rigidity can be secured, so there is a risk of flying. Can be suppressed.

  However, when a composite sprocket is applied, in order to equip a mechanism for moving the pinion sprocket in the radial direction, it is necessary to make the length between the shafts constant, and it is impossible to adjust the length between the shafts. Also, since the pinion sprocket is structured to move in the radial direction, it is difficult to ensure the rigidity on the procket side, so the procket side is elastically deformed, the chain is loosened, and tooth skipping is likely to occur. Further, even if an operation error occurs in the radial movement of each pinion sprocket, the chain is loosened, causing tooth skipping.

  In the case of compound sprockets, the thickness (axial length) of the speed change mechanism tends to increase due to the fact that there is an incidental mechanism such as a structure for moving the pinion sprocket in the radial direction. It is necessary to make the width as small as possible, and it is difficult to ensure the rigidity of the chain. When the rigidity of the chain is lowered, the chain is likely to be stretched. When the chain is stretched, the chain is loosened, which also causes tooth skipping.

  Furthermore, in general, small-diameter pinion sprockets are more prone to tooth skipping than large-diameter sprockets. In particular, pinion sprockets with small diameters relative to the turning radius of the chain, such as composite sprockets, can also generate tooth skipping. Cause increased sex. Further, as the pinion sprocket moves radially outward and the diameter of the composite sprocket increases, the amount of winding of the chain around the pinion sprocket decreases, and tooth skipping easily occurs.

  In the techniques of Patent Documents 1 and 2, a tensioner is provided outside the chain, and the chain is prevented from being loosened by pressing the chain with the tensioner. However, if a tensioner is installed, the chain resistance will increase, resulting in an increase in power transmission loss and a tendency for the chain to rebound. In addition, it may be difficult to secure an installation space, resulting in an increase in cost.

  Therefore, we want to be able to prevent the chain from loosening without relying on length adjustments or tensioners. Although it is conceivable to reduce the length of the chain to suppress the occurrence of looseness, the chain is composed of an even number of links, so it can only be adjusted in units of at least two links. It is also difficult to prevent the chain from loosening by adjusting the length.

The present invention was devised in view of the problems as described above, and constitutes a speed change mechanism from two sets of composite sprockets and a chain wound around them, without causing an increase in power transmission loss, It is a first object of the present invention to provide a speed change mechanism capable of reliably transmitting a large torque by preventing the chain from loosening and avoiding tooth skipping of the chain.
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) The speed change mechanism of the present invention includes a rotating shaft to which power (driving torque) is input or output, a plurality of pinion sprockets and a plurality of guide rods supported so as to be movable in a radial direction with respect to the rotating shaft, Two sets of composite sprockets having 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, and the two sets of the two sets A chain wound around a composite sprocket, the radius of a circle surrounding 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 speed change ratio by changing a tangent radius, wherein the moving mechanism includes the plurality of pinion sprockets. And a plurality of fixed radial grooves into which the support shafts of the plurality of guide rods are inserted, a fixed disk that rotates integrally with the rotary shaft, and the support shaft at a first intersection that intersects each of the fixed radial grooves. A plurality of movable radial grooves in which the movable disk is located, a movable disk disposed concentrically with respect to the fixed disk, and rotatable relative to the fixed disk; And a relative rotation drive mechanism for moving the first disk in the radial direction, and an initial phase adjusting mechanism for changing the initial phase of the movable disk relative to the fixed disk and displacing the first intersection in the radial direction. It is characterized by.

  (2) The movable disk is connected to the relative rotation drive mechanism via a connection disk portion, and the initial phase adjustment mechanism displaces the relative position of the movable disk and the connection disk portion in the relative rotation direction. It is preferable that the mechanism be fixed.

  (3) The movable disk includes a superposition plate portion that overlaps with the connection disk portion, and the initial phase adjusting mechanism is formed along one of the superposition plate portion and the connection disk portion along the relative rotation direction. An arc-shaped elongated hole, a screw hole formed on the other of the overlapping plate portion and the connecting disk portion, and an insertion into the arc-shaped elongated hole and screwed into the screw hole to connect the movable disk and the connection It is preferable to have a fastening member that fastens the disk part.

  (4) The relative rotation drive mechanism is provided along the axial direction of the rotation shaft, and intersects the first cam groove and a first cam groove provided in a first rotation portion that rotates integrally with the fixed disk. A second cam groove provided in a second rotating portion provided along the axial direction and rotating integrally with the movable disk, and a second intersection where the first cam groove and the second cam groove intersect. An axial force transmission that is disposed at a location and is provided with a cam roller having one end projecting in the radial direction and a groove that accommodates the one end of the cam roller, and transmits the axial force to the cam roller. A member, and an axial movement mechanism that moves the axial force transmission member in the axial direction. The axial force transmission member is connected to the first member provided with the groove and the axial movement mechanism. Divided into a second member, Serial initial phase adjustment mechanism is preferably a mechanism for fixing by displacing the axial direction of the relative position between the second member and the first member.

(5) The axial force transmission member has a plate shape arranged in parallel with the movable disk, and the first member and the second member are divided in the thickness direction of the plate shape and overlap each other. Preferably, the initial phase adjusting mechanism is a mechanism that fixes the overlapping portion of the first member and the overlapping portion of the second member by displacing relative positions in the thickness direction. .
(6) The initial phase adjusting mechanism includes a spacer having a selectable thickness, and a fastening member that is fastened with the spacer interposed between the overlapping portion of the first member and the overlapping portion of the second member. It is preferable to have.

Further, when the power is transmitted, the component force of the torque acting on the fixed disk and the movable disk via the support shaft of the pinion sprocket changes the phase of the both disks, thereby causing the first intersecting portion to move in the radial direction. It is also preferable to provide a torque response phase adjustment mechanism that allows the displacement outward.
In this case, when the power is transmitted, the torque response phase adjusting mechanism changes the phase of both the disks by the component force of the torque acting on the fixed disk and the movable disk via the support shaft of the pinion sprocket. It is preferable to restrict displacement of the first intersecting portion radially inward.
Further, the phase of the two disks is changed by the component force of the torque acting on the fixed disk and the movable disk via the support shaft of the pinion sprocket to allow the first intersection to be displaced radially outward. It is preferable to do.
Of the two sets of composite sprockets, the inclination angle of the fixed radial groove formed on the fixed disk of the input side composite sprocket to which power (driving torque) is input is maximized at the position of the minimum diameter. Of the two sets of composite sprockets formed, the inclination angle of the fixed radial groove formed in the fixed disk of the output side composite sprocket from which power (drive torque) is output is the largest at the position of the maximum diameter. It is preferable to be formed as follows.
Of the two sets of composite sprockets, the inclination angle of the fixed radial groove formed on the fixed disk of the input-side composite sprocket to which power (drive torque) is input is set to increase toward the inner side in the radial direction. Of the two sets of composite sprockets formed, the inclination angle of the fixed radial groove formed on the fixed disk of the output-side composite sprocket from which power (drive torque) is output increases as it goes radially outward. It is preferable to be formed as follows.
The relative rotational drive mechanism is provided along the axial direction of the rotary shaft, intersects the first cam groove and a first cam groove provided in a first rotary portion that rotates integrally with the fixed disk, and A second cam groove provided along the axial direction and provided in a second rotating portion that rotates integrally with the movable disk, and a second intersection where the first cam groove and the second cam groove intersect. An axial force transmission member provided with a cam roller having one end projecting in the radial direction, a groove portion for accommodating the one end portion of the cam roller, and transmitting the axial force to the cam roller; An axial movement mechanism for moving the axial force transmission member in the axial direction, wherein the axial force transmission member is provided with a first member connected to the axial movement mechanism and a groove portion. Divided into two parts, Mechanism preferably is interposed between the second member and the first member.

According to the speed change mechanism of the present invention, the initial phase adjustment mechanism changes the initial phase of the movable disk with respect to the fixed disk, and the first intersection where the fixed radial groove and the movable radial groove intersect is displaced radially outward. Since it can be fixed, each support shaft of the pinion sprocket and the guide rod located at this first intersection is displaced in the radial direction, and the radius of the circle that touches both the pinion sprocket and the guide rod The initial tension of the chain can be easily adjusted by expanding and contracting the diameter.
Accordingly, the occurrence of tooth skipping of the chain can be avoided even when a large torque is transmitted, and the large torque can be reliably transmitted.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an axial sectional view (longitudinal sectional view) schematically showing a main part focusing on a radial rotation relative rotational drive mechanism such as a pinion sprocket of a speed change mechanism according to a first embodiment of the present invention. FIG. 3 is a radial cross-sectional view (transverse cross-sectional view) schematically showing a main part focused on the composite sprocket and the chain of the speed change mechanism according to the first embodiment of the present invention. It is a side view paying attention to the fixed disk of the speed change mechanism concerning a 1st embodiment of the present invention. FIG. 3 corresponds to an arrow AA in FIG. It is a side view paying attention to the movable disk of the speed change mechanism concerning a 1st embodiment of the present invention. 4 corresponds to the arrow BB in FIG. FIG. 1 shows a fixed disk and a movable disk for radial movement such as a pinion sprocket in the speed change mechanism according to the first embodiment of the present invention, and pinion sprockets and guide rod support shafts that are moved by these disks. It is a figure explaining a 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 transmission mechanism concerning 1st Embodiment of this invention. 6 is a cross-sectional view taken along the line CC in FIG. It is radial direction sectional drawing of the transmission mechanism concerning 1st Embodiment of this invention. 7 is a cross-sectional view taken along the line DD 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 1st Embodiment of this invention. FIG. 8 is a view taken in the direction of arrows EE in FIG. FIG. 3 is a perspective view schematically showing a part of the chain of the speed change mechanism according to the first embodiment of the present invention and a guide rod that guides the chain. It is a schematic diagram explaining the phase adjustment mechanism of the speed change mechanism concerning 1st Embodiment of this invention, (a) shows this embodiment, (b) shows this embodiment. It 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 a second embodiment of the present invention. It is radial direction sectional drawing of the speed change mechanism concerning 2nd Embodiment of this invention. 6 is a cross-sectional view taken along the line CC in FIG. It 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 a third embodiment of the present invention. It is a side view which pays attention to the fixed disk of the compound sprocket of the input side of the speed change mechanism concerning a 3rd embodiment of the present invention. This corresponds to the view AA in FIG. It is a side view which pays attention to the fixed disk of the compound sprocket of the output side of the speed change mechanism concerning a 3rd embodiment of the present invention. This corresponds to the view A2-A2 in 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 axial direction is the axis of the rotating shaft in the speed change mechanism or the direction parallel to the axis, and the radial direction and the circumferential direction are determined based on the axis of the rotating shaft. Further, a description will be given assuming that the side (revolution shaft side) close to the axis of the rotation shaft in the transmission mechanism is the inside and the opposite side is the outside.

[1. First Embodiment]
Hereinafter, the speed change mechanism according to the first embodiment will be described.
[1-1. Constitution〕
As shown in FIGS. 1 and 2, 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 FIGS. 1 and 2) that rotate integrally with the input-side rotary shaft 1 (input shaft). The other is a composite sprocket 5 (shown on the right side in FIGS. 1 and 2) 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. 2, the composite sprocket 5 rotates a sprocket moving mechanism 40A that moves the 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. 1 and 5 to 7). 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, 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. For this reason, it can be said that the speed change mechanism changes the speed ratio by changing the tangent radius. 1 and 2 show a case where the input side tangent radius is the minimum diameter and the output side tangent radius is the maximum diameter.

As described above, the speed change mechanism changes the speed ratio by changing the tangent circle radius. For example, if the tangent radii of the composite sprockets 5 and 5 are equal, the speed change mechanism has a gear ratio of 1 (the power transmission ratio between one composite sprocket 5 and the other composite sprocket 5 is 1: 1).
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. (Composite sprocket)
In the following description of the configuration of the composite sprocket 5, the pinion sprocket 20, the guide rod 29, the sprocket moving mechanism 40A, the rod moving mechanism 40B, the mechanical rotation driving mechanism 50, and the initial phase adjusting mechanism 80 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. 2, 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. 1, 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 speed change mechanism, but may be two rows, four rows or more, or one row. FIG. 1 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, each pinion sprocket 21, 22, 23 is equipped with a phase shift allowable power transmission mechanism that realizes power transmission by allowing a relative rotation of a minute angle with respect to each support shaft 21 a, 22 a, 23 a May be. 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. 2, 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. 2). 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 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.

[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. 1, 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 rotates integrally with the fixed disk 10. Each of the first 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, 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. 1, the configuration will be described.

[1-1-3-2. (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. 1 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 FIGS. 3 and 4, the fixed disk 10 includes fixed radial grooves 11a, 11b, 11c for the sprockets and fixed radial grooves 12 for the rods (corresponding to the pinion sprockets 21, 22, 23). Two types of radial grooves are formed.
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 the 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.

[1-1-3-3. (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. Note that 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, but in FIG. 5, the outer circle of the movable disk 19 is shown in a reduced scale 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. 1, 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.

[1-1-3-4. (First rotating part)
As shown in FIG. 1, 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. 1, 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.

[1-1-3-9. (Second rotating part)
As shown in FIGS. 1, 6, and 7, the second rotating unit 16 is connected to the movable disk 19 via the connection unit 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 configured differently in the two composite sprockets 5.
The connecting portion 17B equipped on one composite sprocket 5 (here, the right output-side composite sprocket 5 in FIGS. 1 and 2) rotates integrally with the movable disk 19 and the second rotating section 16, and the fixed disk 10 It is arrange | positioned so that it may cover. The connection portion 17B includes an axial connection portion 17a that covers the outer circumference (radially outer side) of the fixed disk 10, and a radial connection portion (connection disk portion) 17b that covers the outer side of the fixed disk 10 in the axial direction.

In the connecting portion 17B, the axial connection portion 17a connects the axial components of the connection between the movable disk 19 and the second rotating portion 16, and connects the radial separation. 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. 1, the axial direction connecting portion 17a is connected to the outer peripheral end portion (outer peripheral portion) 19t of the movable disk 19 on the inner side in the axial direction, and connected to the radial direction connecting portion 17b to be described next on the outer side in the axial direction. Has been.

As shown in FIGS. 1, 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.

  The connecting portion 17A provided on the other composite sprocket 5 (here, the left-side input composite sprocket 5 in FIGS. 1 and 2) also rotates integrally with the movable disk 19 and the second rotating section 16, and the fixed disk 10 It is arrange | positioned so that it may cover. The connecting portion 17A is fastened to an axial connecting member 119 that is fixed to the outer peripheral end portion (outer peripheral portion) 19t of the movable disc 19 and covers a part of the outer periphery (radially outer side) of the fixed disc 10. It has the radial direction connection part 17b which covers an axial direction outer side, and the cyclic | annular part 17a 'which connects each other of multiple (three) radial direction connection parts 17b in an outer peripheral part.

  On the connection portion 17A side, the axial connection member 119 (in this case, for easy identification) is connected to the separation of the axial component of the connection between the movable disk 19 and the second rotating portion 16. The radial connection portion 17b connects the radial separations. A plurality (three in this case) of the axial connection members 119 are provided at equal intervals. The fastening between the axial connection member 119 and the radial connection portion 17b relates to the initial phase adjustment mechanism 80, and details thereof will be described later.

As shown in FIGS. 1, 6, and 7, the radially connecting portion 17 b of the connecting portion 17 </ b> A has a radially outer side fastened to the axial connecting member 119 and a radially inner side connected to the second rotating portion 16. Yes. 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. 1, 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. 1, the second rotating portion 16 is shifted from the outer peripheral end 19 t of the movable disk 19 to the inner peripheral side and provided along the axial direction.

As shown in FIGS. 1 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.
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.

[1-1-3-10. (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, a shift fork (axial force transmission member) 35 for transmitting the axial force against the cam roller 90, the An axial movement mechanism 31 for moving the shift fork 35 in the axial direction is provided.

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. 1 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. 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 transmission fork 35 is parallel to the disks 10 and 19 and is arranged in parallel 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. 1 and 7 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 FIG.1 and FIG.7, the axial direction moving mechanism 31 is demonstrated in order of the fork support part 34 and the motion conversion mechanism 33. FIG.
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.
In addition, the fork support portion 34 has a female screw portion 34a that is screwed into an inner periphery and is engaged with a male screw portion 32b formed on the output shaft 32a of the motor 32, and is engaged with the bridge portion 35b of the speed change fork 35 on the outer periphery. A mating 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.

[1-1-3-11. 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. 1 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. 1), the fixed radial grooves 11a for the sprocket are sequentially displayed in the order of FIGS. 5 (b) and 5 (c). , 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.

[1-1-3-12. Mechanical rotation drive mechanism)
Next, the mechanical rotation driving mechanism 50 will be described with reference to FIGS. 1 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. 1).
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, the structure for preventing the fixed pinion sprocket 21 (see FIG. 2) from rotating about the mechanical rotation drive 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 so as to come into contact with the fixed radial groove for sprocket 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. 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 sprocket fixed radial groove 11a is formed in a rectangular shape having a longitudinal direction in the radial direction, and a guide member 59 formed in a rectangular shape smaller than this rectangular shape is illustrated.
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. Racks 53 and 54 corresponding to the pinions 51 and 52, respectively, are fixed along the extending direction of the sprocket fixed radial grooves 11b and 11c.

  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.
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.

[1-1-4. (Initial phase adjustment mechanism)
Next, the initial phase adjusting mechanism 80 will be described with reference to FIGS. 1, 6, 7 and 10 (a). The initial phase adjustment mechanism 80 changes the initial phase of the movable disc 19 (relative phase) with respect to the fixed disc 10, the first intersection CP ₁ radial (mainly outside) is displaced in a loosening of the chain 6 After taking it into an appropriate tension state, it is fixed to the initial relative phase state. This initial phase adjustment mechanism 80 will be described with respect to one of the two composite sprockets 5, here, the one installed on the left input-side composite sprocket 5 in FIG. 5 may be equipped.

  In the present embodiment, an axial connection member 119 is fixed to the movable disk 19, and the radial connection portion (connection disk portion) of the axial connection member 119 and the connection portion 17 </ b> B connected to the relative rotation drive mechanism 30. 17b is fastened via a bolt (fastening member) 121. As a result, the movable disk 19 is driven to rotate relative to the fixed disk 10 by the relative rotation drive mechanism 30 through the radial connecting portion (connecting disk portion) 17b.

  The axial connection member 119 on the movable disk 19 side overlaps with the axial connection part 119a disposed in the notch 17d of the annular part 17a ′ and covering the outer periphery (radially outer side) of the fixed disk 10 and the radial connection part 17b. And a superposition plate portion 119b.

  As shown in FIG. 10A, the initial phase adjusting mechanism 80 includes an arc-shaped elongated hole 120 formed in the overlapping plate portion 119b along the relative rotation direction, and a screw hole 122 formed in the radial direction connecting portion 17b. And a bolt (fastening member) 121 that is inserted into the arc-shaped elongated hole 120 and screwed into the screw hole 122 to fasten the axial connection member 119 of the movable disk 19 and the connection disk portion 17b.

The overlapping plate part 119b integrated with the movable disk 19 can be rotated relative to the radial connection part 17b of the connection part 17, and by rotating the movable disk 19, the phase of the movable disk 19 with respect to the fixed disk 10 is changed. change, by displacing the first intersection CP ₁ in the radial direction, it is possible to change the initial phases of both disks (adjustment). In the state where the chain 6 is wound around both composite sprockets 5, the initial tension of the chain 6 is adjusted (mainly loosened) by changing the phase of the movable disk 19 and displacing the first intersection CP ₁ in the radial direction. Can take). Thus, if the initial tension obtained by removing the slack of the chain 6 is adjusted and the bolt 121 is inserted into the arc-shaped elongated hole 120 and screwed into the screw hole 122, the ideal initial tension state of the chain 6 (no looseness). State), the initial phase of the movable disk 19 relative to the fixed disk 10 is fixed.

[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-on 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.

  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.

[1-3. Action and effect)
Since the speed change mechanism according to the first embodiment of the present invention is configured as described above, the phase adjustment mechanism 80 can provide the following operations and effects.

  In assembling the speed change mechanism, after the chain 6 is wound around both the composite sprockets 5, the movable disk 19 is rotated in the direction to remove the looseness of the chain 6 with respect to the fixed disk 10. The relative phase is changed to an appropriate tension state such as a state in which the slack of the chain 6 is eliminated.

  Thereby, the overlapping plate portion 119b integrated with the movable disk 19 rotates relative to the radial direction connecting portion 17b of the connecting portion 17. In this state, when the bolt 121 is inserted into the arc-shaped elongated hole 120 and screwed into the screw hole 122 to fasten the overlapping plate portion 119b and the radial connection portion 17b, the chain 6 is in an appropriate tension state without loosening. The initial phase of the movable disk 19 with respect to the fixed disk 10 is fixed.

  Thus, when the transmission mechanism is assembled, the initial slack of the chain 6 can be eliminated, so that the slack of the chain 6 that tends to occur as the transmission torque increases can be suppressed, and the occurrence of tooth skipping can be suppressed. Thus, even a large torque can be reliably transmitted. Moreover, since it is possible to suppress loosening of the chain 6 without depending on the length adjustment between the shafts or the tensioner, it is possible to suppress an increase in power transmission loss as in the case of using the tensioner. Moreover, it does not require a large installation space like a tensioner and is easy to mount.

[1-4. Others]
In the present embodiment, the initial phase adjusting mechanism 80 is formed on one of the overlapping plate portion 119b and the radial direction connection portion (connection disk portion) 17b along the relative rotation direction of the movable disk 19 with respect to the fixed disk 10. The circular arc-shaped long hole 120, the screw hole 122 formed on the other of the overlapping plate portion 119b and the radial connection portion 17b, and the movable disk 19 are inserted into the circular arc-shaped long hole 120 and screwed into the screw hole 122. Although comprised from the volt | bolt 121 which fastens the radial direction connection part 17b, the fixed structure of the movable disk 19 is not restricted to this.

  The initial phase adjusting mechanism 80 according to the present embodiment may be a mechanism that displaces and fixes the relative position of the movable disk 19 and the radial connection portion 17b in the relative rotation direction. A structure shown in FIG. 10B is also conceivable. In this fixing structure, bolt brackets 17e facing the circumferential end surfaces 119c of the overlapping plate portion 119b are respectively erected on the radial connection portions 17b, and bolts (fastening members) screwed into the screw holes of the respective bolt brackets 17e. ) By changing the relative phase between the overlapping plate portion 119b and the radial connection portion 17b by adjusting the protruding length of the bolt 123 with respect to the bolt bracket 17e while abutting the tip end portion of 123 on the circumferential end surfaces 119c It is. This configuration can also change and fix the initial phase of the movable disk 19 with respect to the fixed disk 10.

[2. Second Embodiment]
Hereinafter, the speed change mechanism according to the second embodiment will be described with reference to FIGS. 11 and 12.
[2-1. Constitution〕
The speed change mechanism of the present embodiment is configured in the same manner as in the first embodiment, except that the initial phase adjusting mechanism 180 and the connection portion 17 of the second rotating portion 16 related thereto are different from those in the first embodiment.

[2-1-1. Connection part)
As shown in FIGS. 11 and 12, the connecting portion 17 of the present embodiment has the two composite sprockets 5 configured identically, and any of the connecting portions 17 is the output side of the first embodiment (FIGS. 1 and 2). It is configured in the same manner as the connecting portion 17B of the composite sprocket 5 on the middle and right side. Therefore, description of the connection part 17 of this embodiment is abbreviate | omitted.

[2-1-2. (Initial phase adjustment mechanism)
As shown in FIG. 11, the initial phase adjusting mechanism 180 of the present embodiment is mounted on a speed change fork (axial force transmission member) 35. In other words, the speed change fork 35 has an annular cam roller support portion 35a and a bridge portion 35b for connecting the cam roller support portions 35a, but a portion of the bridge portion 35b near one cam roller support portion 35a The first member 35A and the second member 35B are divided into two parts.

  The first member 35A is a member near the cam roller support portion 35a in which the groove portion 35c is recessed, and the second member 35B is a member connected to the axial movement mechanism 31 near the fork support portion 34. In the present embodiment, the portion near the cam roller support portion 35a of the left input-side composite sprocket 5 in FIG. 11 is divided into two parts, but the divided portion is close to the cam roller support portion 35a of the right output-side composite sprocket 5. The part of

  The plate-shaped transmission fork 35 is divided into two parts in the thickness direction so that the fracture surface is along the plate surface. At the divided part, the plate-shaped divided layer (overlapping part) on the first member 35A side is divided. ) 351 and the plate-shaped divided layer (overlapping portion) 352 on the second member 35B side are superposed in a laminated state and are coupled by a bolt 124. A shim (spacer) 181 is appropriately interposed between the divided layers 351 and 352. A plurality of shims 181 having different thicknesses are prepared, and a shim 181 having an appropriate thickness is selected and used.

Depending on the thickness of the interposed shim 181, the distance between the divided layers 351 and 352 changes, and the relative position in the axial direction of the first member 35 </ b> A with respect to the second member 35 </ b> B changes. For example, when the shim 181 is thickened, the first member 35A is raised, and when the shim 181 is thinned, the first member 35A is lowered. As the first member 35A moves up and down, the cam roller support portion 35a moves up and down, and the cam roller 90 moves up and down in the axial direction. When the cam roller 90 is raised and lowered, the second rotating portion 16 through the second cam groove 16a in the second intersection CP ₂ moves up and down is rotated relative to the first rotating portion 15.

Since the second rotating part 16 rotates integrally with the movable disk 19 and the first rotating part 10 rotates integrally with the fixed disk 10, when the second rotating part 16 rotates relative to the first rotating part 15, the movable disk 19. Rotates relative to the fixed disk 10. By relative rotation of the movable disc 19, the first intersection CP ₁ is moved in the radial direction.

Therefore, by preparing the shim 181 having a plurality of thicknesses and selecting and using the thickness of the shim 181, the first intersection CP ₁ can be moved in the radial direction, and the initial phases of both the disks 10, 19 can be obtained. Can be set so that the chain 6 is not loosened. Thus, by fixing the shim 181 having an appropriate thickness between the divided layer 351 on the first member 35A side and the divided layer 352 on the second member 35A side, and connecting them with the bolts 124, the fixed disk The initial phase of the movable disk 19 with respect to 10 can be adjusted and fixed so that the chain 6 is not loose.

[2-2. Action and effect)
Since the speed change mechanism according to the second embodiment of the present invention is configured as described above, the initial phase adjusting mechanism 180 can obtain the following operations and effects.

  In assembling the speed change mechanism, after the chain 6 is wound around the two composite sprockets 5, the movable disk 19 is rotated with respect to the stationary disk 10 in the direction of removing the looseness of the chain 6. The phase is changed to an appropriate tension state such as a state where the looseness of the chain 6 is eliminated.

  As a result, the size of the gap between the divided layer (overlapping portion) 351 on the first member 35A side and the divided layer (overlapping portion) 352 on the second member 35B side is determined. The phase of the movable disk 19 with respect to the fixed disk 10 is fixed without loosening of the chain 6 by selecting 181 and interposing between the two divided layers 351 and 352 and coupling with the bolt 124. As a result, the initial phase of the movable disk 19 with respect to the fixed disk 10 is fixed in an appropriate tension state where the chain 6 is not loosened.

  Thus, when the transmission mechanism is assembled, the initial slack of the chain 6 can be eliminated. Therefore, it is possible to suppress the slack in the chain 6 that is more likely to occur as the transmission torque increases, and to prevent tooth skipping. Thus, even a large torque can be reliably transmitted. Further, since it is possible to suppress loosening of the chain 6 without depending on the length adjustment between the shafts and the tensioner, the increase in cost can be suppressed without causing an increase in power transmission loss as in the case of using the tensioner. Moreover, it does not require a large installation space like a tensioner and is easy to mount.

[2-3. Others]
The phase adjusting mechanism 180 of the present embodiment divides the speed change fork (axial force transmission member) 35 into a first member 35A and a second member 35B, and the plate-shaped divided layers of the members 35A and 35B. (Polymerization unit) 351 and 352 are superposed in a laminated state, and a shim 181 is sandwiched therebetween, but is not limited to this configuration.

  For example, the phase adjusting mechanism 180 is configured such that a screw parallel to the bolt 124 is screwed into one of the divided layers 351 and 352 and the tip of the screw is in contact with the other facing surface of the divided layers 351 and 352. A relative position in the thickness direction of the divided layers 351 and 352 may be displaced by the protruding amount of the tip of the screw, and may be fixed by the bolt 124. The speed change fork (axial force transmission member) 35 may be the first member and the first member. Any mechanism may be used as long as it is divided into two members and these are fixed by displacing the relative positions in the axial direction.

[3. Third Embodiment]
Hereinafter, the speed change mechanism according to the third embodiment will be described with reference to FIGS.
[3-1. Constitution〕
The speed change mechanism of the present embodiment has a torque response phase adjustment mechanism 100 added to that of the second embodiment. Therefore, the description of the same configuration as in the second embodiment is omitted, and only the configuration related to the added torque response phase adjustment mechanism 100 will be described.

[3-1-1. (Fixed disk)
In the embodiment, there is a difference between the fixed disk 10 of the composite sprocket 5 on the input side and the fixed disk 10 ′ of the composite sprocket 5 on the output side. The fixed disk 10 of the composite sprocket 5 on the input side is the same as that of the first and second embodiments, but the fixed disk 10 'of the composite sprocket 5 on the output side is different from this. Elements of the composite sprocket 5 on the output side that are different from the elements of the composite sprocket 5 on the input side are marked with “′”.

  14 and 15, the sprocket fixed radial grooves 11a, 11b, 11c of the fixed disk 10 of the input-side composite sprocket 5 and the sprocket of the fixed disk 10 'of the output-side composite sprocket 5 are referred to. The fixed radial grooves 11a ′, 11b ′, and 11c ′ will be described.

  As shown in FIGS. 14 and 15, both the fixed radial grooves for sprockets 11a, 11b, and 11c and the fixed radial grooves for sprockets 11a ′, 11b ′, and 11c ′ are formed in the composite sprocket as they go radially outward. It has an inclined structure formed with an inclination angle with respect to the radial direction so as to shift in the rotation direction.

The inclination angle θ of the sprocket fixed radial grooves 11a, 11b, and 11c of the input-side composite sprocket 5 is the largest at the position of the minimum diameter (inclination angle θ ₁ ), and the smallest at the position of the maximum diameter (inclination angle θ ₂ ). It forms so that it may become large as it goes to radial inside. Here, the fixed radial grooves 11a, 11b, 11c for the sprocket are formed in a straight line. The fixed radial grooves 12 for rods are also formed in the same manner as the fixed radial grooves 11a, 11b, 11c for sprockets.

Conversely, the inclination angle θ of the sprocket fixed radial grooves 11a ′, 11b ′, and 11c ′ of the output-side composite sprocket 5 is the largest at the position of the maximum diameter (inclination angle θ ₃ ) and the smallest at the position of the minimum diameter ( The inclination angle θ ₄ ) is formed so as to increase toward the radially outer side. Here, the fixed radial grooves 11a ', 11b', 11c 'for the sprocket are formed in a concave curved shape in the rotational direction. The fixed radial grooves for rods 12 'are also formed in the same manner as the fixed radial grooves for sprockets 11a', 11b 'and 11c'.

  Such inclination of the fixed radial grooves 11a, 11b, 11c, 11a ', 11b', and 11c 'for the sprocket is used in the torque response phase adjusting mechanism 100 described later, and the meaning of these inclinations will be described later.

[3-1-2. (Torque response phase adjustment mechanism)
Next, the torque response phase adjustment mechanism 100 will be described with reference to FIGS. 13, 14, and 15. In the torque response phase adjusting mechanism 100, torque acting on the fixed disks 10, 10 ′ and the movable disk 19 changes the phase of the movable disk 19 with respect to the fixed disks 10, 10 ′ when power is transmitted. If it is intended to displace an intersection CP ₁ radially outward allows the displacement. However, in the torque response phase adjusting mechanism 100, the torque acting on the fixed disks 10, 10 ′ and the movable disk 19 changes the phase of the movable disk 19 with respect to the fixed disks 10, 10 ′, and thereby the first crossing point. When the CP ₁ is to be displaced radially inward, this displacement is restricted.

  The torque response phase adjusting mechanism 100 includes inclined structures of fixed radial grooves 11a, 11b, 11c, 11a ', 11b', 11c 'for sprockets formed on the fixed disks 10, 10' of the composite sprockets 5, 5. It is movable by the inclined structure of fixed radial grooves 11a, 11b, 11c, 11a ', 11b', 11c 'formed on the fixed disks 10, 10' from the support shafts 21a, 22a, 23a of the pinion sprockets 21, 22, 23. There are urging mechanisms 100A and 100B that apply a urging force to the movable disk 19 in a rotation direction (that is, a reverse rotation direction) opposite to the torque component applied to the disk 19.

  First, the inclined structure will be described. The fixed radial grooves 11a, 11b, 11c, 11a ′, 11b ′, 11c ′ for the sprocket are all shifted in the radial direction so as to shift toward the advance side in the rotational direction of the composite sprocket 5 toward the radially outer side. And an inclined structure formed with an inclination angle θ.

Note that the sprocket fixed radial grooves 11a, 11b, 11c, 11a ', 11b', and intersects the 11c ', the support shaft 21a, 22a, sprockets movable radial groove 23a forms a first intersection CP ₁ located 19a has an inclined structure that is inclined with respect to the radial direction so as to shift to the opposite side to the retard side of the rotational direction of the composite sprocket 5 (that is, the direction opposite to the fixed radial groove) as it goes outward in the radial direction. ing.

In the present embodiment, among the two sets of composite sprockets 5, 5, the fixed radial grooves 11a, 11b, 11c for sprockets formed on the fixed disk 10 of the left-side composite sprocket 5 in FIGS. As shown in FIG. 3A, the inclination angle θ is formed so as to increase toward the inner side in the radial direction, and the maximum inclination angle θ _{1 in} the state of the innermost minimum diameter in the radial direction. Thus, the minimum inclination angle θ ₂ is obtained in the state of the outermost maximum diameter in the radial direction.

On the other hand, the fixed radial grooves 11 a ′, 11 b ′, 11 c ′ for the sprocket formed in the fixed disk 10 ′ of the right output-side composite sprocket 5 in FIG. 1 and FIG. As shown in FIG. 4A, the inclination angle θ is formed so as to increase toward the outer side in the radial direction, and the maximum inclination in the state of the outermost maximum diameter in the radial direction. The angle θ ₃ , and the minimum inclination angle θ _{4 in} the state of the innermost minimum diameter in the radial direction.

  The biasing mechanism 100A of the input-side composite sprocket 5 is installed between the bridge portion (second member) 35b and the cam roller support portion (first member) 35a of the speed change fork 35. An annular holder portion 101 is fixed to the bridge portion 35b so as to sandwich the cam roller support portion 35a from above and below (from both sides in the axial direction). The holder unit 101 couples an upper wall unit 101a disposed above the cam roller support unit 35a, a lower wall unit 101b disposed below the cam roller support unit 35a, and an upper wall unit 101a and a lower wall unit 101b. And a cylindrical wall portion 101c.

  A spring (for example, a disc spring) 103 is interposed between the upper wall portion 101a and the upper surface portion of the cam roller support portion 35a in a preloaded state, and the lower surface portion of the cam roller support portion 35a is connected to the lower wall portion 101b. And the upward movement of the cam roller support portion 35a is restricted until an upward force higher than the preload is applied to the cam roller support portion 35a. When the fixed disk 10 and the movable disk 19 receive a torque component from the support shaft 20a, both the disks 10 and 19 try to rotate relative to each other, and the first cam groove 15a and the second cam groove 16a try to rotate relative thereto. As a result, the cam roller 90 tries to move the cam roller support portion 35a in the axial direction. If the movement direction in the axial direction is lower in FIG. 1, the movement is restricted by the lower wall portion 101b. However, the movement direction in the axial direction is upper in FIG. 1, and the torque component force is the preload. If it is greater than the spring force, the cam roller support 35a moves while further compressing the spring 103.

  The biasing mechanism 100B of the output-side composite sprocket 5 is also provided between the bridge portion 35b of the speed change fork 35 and the cam roller support portion 35a. The bridge portion 35b is provided with an annular portion 35e formed on the cam roller support portion 35a side so as to surround the cam roller support portion 35a. The cam roller support portion 35a includes the annular portion 35e of the bridge portion 35b from above and below (in the axial direction). An annular holder portion 102 arranged so as to be sandwiched (from both sides) is fixed. The holder portion 102 has an upper wall portion 102a disposed above the cam roller support portion 35a and a lower wall portion 102b disposed below the cam roller support portion 35a.

  A spring (for example, a disc spring) 104 is interposed between the upper wall portion 102a and the upper surface portion of the annular portion 35e of the bridge portion 35b in a state where the preload is suspended, and the lower surface portion of the cam roller support portion 35a is placed below the lower portion. The wall portion 102b is pressed against the wall portion 102b, and the downward movement of the cam roller support portion 35a is restricted by the same action as the urging mechanism 100A. When the fixed disk 10 'and the movable disk 19 receive a torque component from the support shaft 20a, the cam roller 90 tries to move the cam roller support portion 35a in the axial direction as in the urging mechanism 100A. If the movement direction in the axial direction is the upper direction in FIG. 1, the movement is restricted by the lower wall portion 102b. However, the movement direction in the axial direction is the lower direction in FIG. 1 and the torque component force is the preload. If it is greater than the spring force, the spring 104 can be moved while being further compressed.

  Thus, the relative rotation between the fixed disks 10 and 10 ′ and the movable disk 19 is possible if the acting force overcomes the preload force of the springs 103 and 104. That is, when the support shafts 21a, 22a, and 23a receive torque components and try to move radially outward, the sprocket fixed radial grooves 11a, 11b, 11c, 11a ', 11b', and 11c 'are radially outward. Since the composite sprocket 5 has an inclined structure that shifts toward the rotation direction advance side as it goes, the support shafts 21a, 22a, and 23a try to shift toward the rotation direction retard side.

  On the other hand, the sprocket movable radial groove 19a of the movable disk 19 is opposite to the sprocket fixed radial grooves 11a, 11b, 11c, 11a ', 11b', 11c ', and the composite sprocket 5 is directed radially outward. Therefore, the reaction shaft counteracts the movement of the support shafts 21a, 22a, 23a to move outward in the radial direction and toward the advance side in the rotation direction.

However, since the reaction force by the movable radial groove 19a for the sprocket depends on the preload force of the springs 103, 104, the force to move the support shafts 21a, 22a, 23a radially outwardly is the springs 103, 104. if can defeat the preload force, and the fixed disk 10, 10 'and the movable disc 19 rotate relative to the first intersection CP ₁ becomes possible to displace radially outward, radial direction of the first intersection CP ₁ Movement to the outside, and thus movement of the support shafts 21a, 22a, and 23a to the outside in the radial direction is allowed according to the force applied to the support shafts 21a, 22a, and 23a.

Note that when the support shafts 21a, 22a, and 23a receive a force radially inward in the fixed disks 10 and 10 ′ and try to move inward in the radial direction, the movable radial groove 19a for the sprocket of the movable disk 19 counters this. Demonstrate reaction force. This reaction force acts in the direction of moving the cam roller support portion 35a downward in the composite sprocket 5 on the input side, and acts in the direction of moving the cam roller support portion 35a upward in the composite sprocket 5 on the output side. each lower wall portion 101b, is restricted movement by 102b, the movement of the radially inner first intersection CP _1, therefore, the support shaft 21a, 22a, the movement of the radially inner 23a is prevented. Lower wall portion 101b, 102b is also called a inner movement restricting member for restricting the movement of the radially inward of the first intersection CP _1.

  In this speed change mechanism, during power running in which torque is transmitted from the input-side composite sprocket 5 to the output-side composite sprocket 5 in the direction of the white arrow shown in FIG. 2 (counterclockwise), it is applied to the fixed disk 10 ′ of the output-side composite sprocket 5. When attention is paid, as shown in FIG. 4, a force (driving force) F corresponding to the torque is transmitted from the support shafts 21a, 22a, 23a to the fixed disk 10 'through the fixed radial grooves 11a', 11b ', 11c' for sprockets. The

  As shown in FIG. 15, the force F acts in the tangential direction of the rotation circle of the support shafts 21a, 22a, and 23a, and acts on the force F and the inclination angle θ of the fixed radial grooves 11a ′, 11b ′, and 11c ′ for the sprocket. Accordingly, a component force (expansion force) Fr (= Fsinθ) of the force F that moves the support shafts 21a, 22a, and 23a radially outward is generated. The component force Fr moves the support shafts 21a, 22a, and 23a radially outward while rotating the movable disk 19 against the preload force of the spring 104. Thereby, the tension of the chain 6 is increased according to the driving force F and the inclination angle θ. The component force F applied to the wall surfaces of the sprocket fixed radial grooves 11a ′, 11b ′, 11c ′ is offset by the vertical drag Fn from the wall surfaces of the sprocket fixed radial grooves 11a ′, 11b ′, 11c ′. .

  As shown in FIG. 15, the inclination angle θ of the fixed radial grooves 11a ′, 11b ′, 11c ′ for the fixed disk 10 ′ of the output-side composite sprocket 5 increases toward the outer side in the radial direction. However, the component force Fr increases as the support shafts 21a, 22a, 23a go radially outward.

For example, the transmission torque becomes the largest during power running when a large torque is input with the lowest gear ratio, such as when the vehicle starts. At this time, the diameter of the input-side composite sprocket 5 is minimized. Thus, the diameter of the output-side composite sprocket 5 is maximized. In the output-side composite sprocket 5 having the maximum diameter, the inclination angle θ of the sprocket fixed radial grooves 11a ′, 11b ′, 11c ′ of the fixed disk 10 ′ is also maximized (θ ₃ ), so that a large component force Fr ₃ is obtained. Occur. Thus, the diameter of the output-side composite sprocket 5 is expanded by the large diameter expansion force Fr ₃ (= F ₃ sinθ ₃ ) corresponding to the large driving force F ₃ and the large inclination angle θ _3, and the tension of the chain 6 is reliably increased. It has become.

  On the other hand, in this speed change mechanism, the rotational direction is the same as that during power running, but during coasting when torque is transmitted from the output-side composite sprocket 5 to the input-side composite sprocket 5, as shown by the black arrows in FIG. The engine brake torque acts in the direction opposite to the rotation direction of the white arrow. In this case, the force (driving force) Fb opposite to the engine brake force is in the direction opposite to that during power running, that is, the output-side composite sprocket. 5 to the input-side composite sprocket 5. At this time, in the input-side composite sprocket 5, the force Fb is transmitted from the support shafts 21a, 22a, and 23a to the fixed disk 10 through the fixed radial grooves 11a, 11b, and 11c for the sprocket.

  As shown in FIG. 3A, the force Fb acts in the tangential direction of the rotation circle of the support shafts 21a, 22a, and 23a, and depends on the force Fb and the inclination angle θ of the fixed radial grooves for sprockets 11a, 11b, and 11c. Thus, a component force (expansion force) Fbr (= Fbsin θ) of the force Fb that moves the support shafts 21a, 22a, and 23a radially outward is generated. This component force Fbr moves the support shafts 21a, 22a, 23a radially outward while rotating the movable disk 19 against the preload force of the spring 104. Thereby, the tension of the chain 6 is increased according to the driving force Fb and the inclination angle θ. The component force Fb applied to the wall surfaces of the sprocket fixed radial grooves 11a, 11b, and 11c is offset by the vertical drag Fbn from the wall surfaces of the sprocket fixed radial grooves 11a, 11b, and 11c.

  As shown in FIG. 14, the inclination angle θ of the sprocket fixed radial grooves 11a, 11b, 11c of the fixed disk 10 of the input-side composite sprocket 5 increases toward the inner side in the radial direction. The component force Fr increases as the shafts 21a, 22a, and 23a go radially inward.

For example, the transmission torque increases during coasting when the gear ratio is close to the lowest. At this time, the diameter of the input-side composite sprocket 5 approaches the minimum, and the diameter of the output-side composite sprocket 5 approaches the maximum. . In the input-side composite sprocket 5 that has approached the minimum, the inclination angle θ of the fixed radial grooves 11a, 11b, and 11c for the fixed disk 10 is also large (for example, the maximum inclination angle θ ₁ ), and thus a large component force Fbr ₁ is generated. Occur. Thus, the diameter of the input-side composite sprocket 5 is expanded by the force Fb ₁ that opposes the large engine braking force and the large component force Fbr ₁ (= Fb ₁ sinθ ₁ ) corresponding to the large inclination angle θ ₁ , and the chain 6 is tensioned. It is sure to increase it.

[3-2. Action and effect)
Since the speed change mechanism according to the third embodiment of the present invention is configured as described above, in addition to the effects of the phase adjustment mechanism 180, the following functions and effects can be obtained by the torque response phase adjustment mechanism 100. it can.

  According to this speed change mechanism, when power is transmitted from the input-side composite sprocket 5 to the output-side composite sprocket 5, the power input from the rotary shaft 1 of the input-side composite sprocket 5 is transmitted to the support shaft via the fixed disk 10. 21 a, 22 a, 23 a and transmitted from the pinion sprockets 21, 22, 23 to the chain 6. Further, it is transmitted from the chain 6 to the pinion sprockets 21, 22, 23 of the output-side composite sprocket 5, and transmitted from the support shafts 21 a, 22 a, 23 a to the rotary shaft 1 of the output-side composite sprocket 5 through the fixed disk 10.

At this time, in the output-side composite sprocket 5, as shown in FIG. 4A, force (drive) is applied to the fixed disk 10 'from the support shafts 21a, 22a, 23a through the fixed radial grooves 11a', 11b ', 11c' for the sprocket. Force) F is transmitted.
Depending on this force F and the inclination angle θ of the fixed radial grooves 11a ′, 11b ′, 11c ′ for the sprocket, a component force (expansion force) Fr (= expansion force) that moves the support shafts 21a, 22a, 23a radially outward. Fsinθ) is generated. Since the support shafts 21a, 22a, 23a are moved radially outward according to the magnitude of the component force Fr, the tension of the chain 6 can be increased according to the driving force F and the inclination angle θ.

In particular, the inclination angle θ of the fixed radial grooves 11a ′, 11b ′, and 11c ′ for the sprocket of the fixed disk 10 ′ of the output-side composite sprocket 5 increases toward the outer side in the radial direction. The component force Fr increases as 21a, 22a, 23a goes radially outward. When the gear ratio is the lowest and a large torque is input, the diameter of the input-side composite sprocket 5 is minimized, and the diameter of the output-side composite sprocket 5 is maximized. The inclination angle θ of the grooves 11a ′, 11b ′, 11c ′ is also maximized, and a large component force Fr ₃ is generated. Thereby, the diameter of the output-side composite sprocket 5 can be expanded with a large component force Fr ₃ corresponding to the large driving force F ₃ and the large inclination angle θ _3, and the tension of the chain 6 can be reliably increased. Note that the sprocket fixed radial grooves 11a ', offsetting 11b', the component force of the force _{F 3} exerted on the wall of 11c' are sprocket fixed radial grooves 11a ', 11b', by the normal force Fn ₃ from the wall surface of 11c' Is done.

  On the other hand, in this speed change mechanism, it can be considered that torque corresponding to the engine braking force is transmitted from the output side sprocket 5 to the input side composite sprocket 5 during coasting. That is, the power input from the rotary shaft 1 of the output-side composite sprocket 5 is transmitted to the support shafts 21a, 22a, and 23a via the fixed disk 10 ', and is transmitted from the pinion sprockets 21, 22, and 23 to the chain 6. . Further, it is transmitted from the chain 6 to the pinion sprockets 21, 22, 23 of the input-side composite sprocket 5, and transmitted from the support shafts 21 a, 22 a, 23 a to the rotary shaft 1 of the input-side composite sprocket 5 through the fixed disk 10.

At this time, in the input-side composite sprocket 5, as shown in FIG. 3A, the force Fb is transmitted from the support shafts 21a, 22a, and 23a to the fixed disk 10 through the fixed radial grooves 11a, 11b, and 11c for the sprocket.
A force (expansion force) Fbr (= Fbsin θ) for moving the support shafts 21a, 22a, 23a radially outward is generated according to the force Fb and the inclination angle θ of the fixed radial grooves 11a, 11b, 11c for the sprocket. Then, the support shafts 21a, 22a, and 23a are moved radially outward. Thereby, the tension of the chain 6 can be increased according to the driving force Fb and the inclination angle θ.

For example, when the gear ratio is close to the lowest during coasting, the torque acting on the input-side composite sprocket 5 increases, and the diameter of the input-side composite sprocket 5 approaches the minimum. The inclination angle θ of the ten fixed radial grooves 11a, 11b, and 11c for sprocket is also increased, and the diameter of the input-side composite sprocket 5 is expanded with a large driving force Fb ₁ and a large component force Fbr ₁ corresponding to the large inclination angle θ _1. The tension of the chain 6 can be reliably increased. The component force Fb ₁ applied to the wall surfaces of the sprocket fixed radial grooves 11a, 11b, and 11c is offset by the vertical drag Fbn ₁ from the wall surfaces of the sprocket fixed radial grooves 11a, 11b, and 11c.

Further, when the vehicle moves backward, each composite sprocket 5 rotates in the direction opposite to the rotation direction of the white arrow.
During reverse power running of the vehicle, the reverse power input from the rotary shaft 1 of the input-side composite sprocket 5 is transmitted to the support shafts 21a, 22a, 23a via the fixed disk 10, and the chain 6 from the pinion sprockets 21, 22, 23 Is transmitted to. Further, it is transmitted from the chain 6 to the pinion sprockets 21, 22, 23 of the output-side composite sprocket 5, and transmitted from the support shafts 21 a, 22 a, 23 a to the rotary shaft 1 of the output-side composite sprocket 5 through the fixed disk 10 ′. .

  At this time, in the input side composite sprocket 5, a force corresponding to the drag force Fbn shown in FIG. 3A is transmitted from the sprocket fixed radial grooves 11a, 11b, 11c of the fixed disk 10 to the support shafts 21a, 22a, 23a. In contrast, the support shafts 21a, 22a, and 23a counteract with a reaction force corresponding to the force Fb shown in FIG. As a result, the force (expansion force) Fbr (= Fbsinθ) that moves the support shafts 21a, 22a, and 23a radially outward in accordance with the force Fb and the inclination angle θ of the fixed radial grooves 11a, 11b, and 11c for the sprocket. And the support shafts 21a, 22a, and 23a are moved radially outward. Thereby, the tension | tensile_strength of the chain 6 can be raised according to the driving force Fb and inclination | tilt angle (theta) similarly to the time of advance.

  On the other hand, at the time of reverse coasting of the vehicle, the power in the reverse direction input from the rotary shaft 1 of the output-side composite sprocket 5 is reversely supported by the driving shafts 21a, 22a, 23a via the fixed disk 10 '. To the chain 6 from the pinion sprockets 21, 22, and 23. Further, it is transmitted from the chain 6 to the pinion sprockets 21, 22, 23 of the input-side composite sprocket 5, and transmitted from the support shafts 21 a, 22 a, 23 a to the rotary shaft 1 of the output-side composite sprocket 5 via the fixed disk 10.

  At this time, in the output-side composite sprocket 5, a force corresponding to the drag force Fn shown in FIG. 4A is applied from the sprocket fixed radial grooves 11 a ′, 11 b ′, 11 c ′ of the fixed disk 10 ′ to the support shafts 21 a, 22 a, The support shafts 21a, 22a, and 23a are opposed to each other by a reaction force corresponding to the force F shown in FIG. As a result, the force (expansion force) Fr (= Fsinθ) that moves the support shafts 21a, 22a, and 23a radially outward according to the force F and the inclination angle θ of the fixed radial grooves 11a, 11b, and 11c for the sprocket. And the support shafts 21a, 22a, and 23a are moved radially outward. Thereby, the tension | tensile_strength of the chain 6 can be raised according to the driving force F and inclination-angle (theta) similarly to the time of advance.

[3-3. Others]
Although the third embodiment of the present invention has been described above, each configuration of the embodiment can be selected as necessary and may be appropriately combined.

  For example, in the above embodiment, the shift fork (axial force transmission member) 35 is divided into a bridge portion (second member) 35b and a cam roller support portion (first member) 35a, and an urging mechanism is provided therebetween. 100A and 100B are provided, but any biasing force may be applied to the movable disk 19 in the rotational direction opposite to the torque applied to the movable disk 19 from the support shafts 21a to 23a, and the configuration is limited to the configuration of the embodiment. Is not to be done.

  Further, regarding the inclined structure, the inclination angle θ of the fixed radial grooves 11a to 11c formed in the fixed disk 10 of the input side composite sprocket 5 is formed so as to increase inward in the radial direction, and the output side composite sprocket 5 Although the inclination angle θ of the fixed radial grooves 11a ′ to 11c ′ formed in the fixed disk 10 ′ is formed to increase toward the outer side in the radial direction, the present invention is not limited to this.

  For example, the inclination angle θ of the fixed radial grooves 11a to 11c formed on the fixed disk 10 of the input-side composite sprocket 5 is formed to be the largest at or near the position of the minimum diameter of the input-side composite sprocket 5 and output. The inclination angle θ of the fixed radial grooves 11 ′ to 11 c ′ formed in the fixed disk 10 ′ of the side composite sprocket 5 is simply formed so as to be the largest at the position of the maximum diameter of the output side composite sprocket 5 or in the vicinity thereof. However, it does not necessarily have to be configured so as to increase toward the inner side or the outer side in the radial direction.

  The fixed radial grooves 11a to 11c and 11a 'to 11c' formed on the fixed disks 10 and 10 'of the composite sprockets 5 are each changed in diameter so as to shift in the rotational direction of the composite sprocket toward the radially outer side. In particular, it is not necessary to specify the magnitude of the inclination angle, only by forming the inclination angle with respect to the direction.

[4. Others]
Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention. Each structure of one Embodiment mentioned above can be selected as needed, and may be combined suitably.

In particular, the phase adjustment mechanism as long as it can tension of the first crossing the point CP ₁ is displaced radially chain 6 by changing the phase of the movable disc 19 relative to the fixed disk 10 is fixed in a proper state, the It is not limited to the initial phase adjustment mechanisms 80 and 180 of the embodiments.
Furthermore, the torque response phase adjustment mechanism of the third embodiment may be combined with other initial phase adjustment mechanisms such as the initial phase adjustment mechanism of the first embodiment.

DESCRIPTION OF SYMBOLS 1 Rotating shaft 5 Composite sprocket 6 Chain 10, 10 'Fixed disk (1st support member, radial direction fixed disk, rotation fixed disk)
11a, 11b, 11c, 11a ′, 11b ′, 11c ′ Fixed radial groove for sprocket (fixed pinion sprocket guide groove)
12, 12 'Fixed radial groove for rod 15 First rotating portion 15a First cam groove 16 Second rotating portion 16a Second cam groove 17, 17A, 17B Connecting portion 17a Axial connecting portion 17b Radial connecting portion (connecting disk portion) )
17e bolt bracket 19 movable disk (first support member, movable disk for radial movement)
19a Movable radial groove for sprocket 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)
20a, 21a, 22a, 23a Support shafts 21c, 22c, 23c Teeth of pinion sprockets 21, 22, 23 29 Guide rod 30 Relative rotation drive mechanism 31 Axial movement mechanism 32 Motor 33 Motion conversion mechanism 34 Fork support portion 35 Shifting fork (Axial moving member for moving sprocket)
35A First member 35B Second 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)
80, 180 Initial phase adjustment mechanism 90 Cam roller 100 Torque response phase adjustment mechanism 100A, 100B Biasing mechanism 101, 102 Holder part 103, 104 Spring 119 Axial connection member 119a Axial connection part 119b Superposition plate part 119c Circumferential end faces 120 Arc-shaped slot 121, 123, 124 Bolt (fastening member)
122 Screw holes 351, 352 Dividing layer (overlapping part)
C ₁ , C ₂ , C ₃ , C ₄ axis CP ₁ first intersection CP ₂ second intersection θ _S , θ _C radial direction

Claims (6)

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 each of the plurality of pinion sprockets and the plurality of guide rods. There,
The moving mechanism is
A plurality of fixed radial grooves into which the support shafts of the plurality of pinion sprockets and the plurality of guide rods are inserted, and a fixed disk that rotates integrally with the rotation shaft;
A plurality of movable radial grooves in which the support shaft is located at first intersecting points intersecting with each of the fixed radial grooves, a movable disk that is concentrically arranged with respect to the fixed disk and is relatively rotatable;
A relative rotation drive mechanism for driving the movable disk relative to the fixed disk to move the first intersection in the radial direction, and
A speed change mechanism comprising: an initial phase adjusting mechanism that changes an initial phase of the movable disk with respect to the fixed disk and displaces the first intersecting portion in a radial direction. The movable disk is connected to the relative rotation drive mechanism via a connection disk part,
The speed change mechanism according to claim 1, wherein the initial phase adjusting mechanism is a mechanism that displaces and fixes a relative position of the movable disk and the connection disk portion in the relative rotation direction. The movable disk has an overlapping plate portion that overlaps with the connection disk portion,
The initial phase adjusting mechanism is formed in one of the overlap plate portion and the connection disk portion in an arcuate long hole formed along the relative rotation direction, and the other of the overlap plate portion and the connection disk portion. 3. The screw hole according to claim 2, further comprising: a fastening member that is inserted into the arc-shaped elongated hole and screwed into the screw hole to fasten the movable disk and the connection disk portion. Transmission mechanism. The relative rotation drive mechanism is
A first cam groove provided in a first rotating portion provided along the axial direction of the rotating shaft and rotating integrally with the fixed disk;
A second cam groove provided in a second rotating portion that intersects with the first cam groove and is provided along the axial direction and rotates integrally with the movable disk;
A cam roller disposed at a second intersection where the first cam groove and the second cam groove intersect, and having one end projecting in the radial direction;
An axial force transmission member provided with a groove portion for accommodating the one end portion of the cam roller, and transmitting the axial force to the cam roller;
An axial movement mechanism for moving the axial force transmission member in the axial direction,
The axial force transmission member is divided into a first member provided with the groove and a second member connected to the axial movement mechanism,
The speed change mechanism according to claim 1, wherein the initial phase adjustment mechanism is a mechanism that displaces and fixes a relative position of the first member and the second member in the axial direction. The axial force transmission member has a plate shape arranged in parallel with the movable disk, and the first member and the second member are overlapped by being divided in the thickness direction of the plate shape and overlapping each other. Each with
The said initial phase adjustment mechanism is a mechanism which displaces the relative position of the said thickness direction, and fixes the overlap part of said 1st member and the overlap part of said 2nd member, It is characterized by the above-mentioned. Transmission mechanism. The initial phase adjusting mechanism includes a spacer whose thickness can be selected, and a fastening member that is fastened with the spacer interposed between the overlapping portion of the first member and the overlapping portion of the second member. The speed change mechanism according to claim 5, wherein

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