JP2015224732A - Transmission mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transmission mechanism for transmitting power by a chain wound on composite sprockets, capable of suppressing irregular motion or detachment of the chain while suppressing degradation of power transmission efficiency.SOLUTION: A transmission mechanism comprises: a rotary shaft 1; composite sprockets 5 each including a plurality of pinion sprockets 20 radially movable with respect to the rotary shaft 1 and a sprocket moving mechanism 40A synchronizing the pinion sprockets 20 and moving the pinion sprockets 20 radially; and a chain 6 wound on the composite sprockets 5, and changes a transmission gear ratio depending on a change in a circumscribed circle diameter for the pinion sprockets 20, the transmission mechanism comprising an orbit guide mechanism 171 pressing and contacting the chain 6 from an outer circumference of the chain 6 and guiding an orbit of the chain 6; and a chain followup moving mechanism moving the orbit guide mechanism 171 along a followup orbit FO to follow up a change in the orbit of the chain 6, the chain followup moving mechanism moving to be interlocked with the sprocket moving mechanism 40A.

Description

  The present invention relates to a transmission mechanism that transmits power by a plurality of pinion sprockets that are movable in a radial direction while maintaining an equal distance from a rotating shaft and that revolve with respect to the rotating shaft, and a chain wound around these pins. It is.

  Conventionally, a driving belt is wound around a primary pulley and a secondary pulley, and the driving belt is clamped by a thrust applied to the movable sheave of each pulley, and the power is transmitted using a frictional force generated between each pulley and the driving belt. Type continuously variable transmissions have been put into practical use as, for example, vehicle transmissions. In the case of a vehicle transmission, a metal belt is usually used as a drive belt, and in recent years, a belt that uses a chain instead of the drive belt has been put into practical use.

  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 and prevent the belt and pulley from slipping. At this time, the load on the drive source (engine or electric motor) that drives the oil pump for generating hydraulic thrust increases, which may lead to an increase in the fuel or power consumption of the drive source, There is a risk of impairing durability.

  On the other hand, as exemplified in Patent Document 1 and Patent Document 2, for example, a plurality of pinion sprockets and a chain wound around the pinion sprocket are used without using frictional force due to thrust, and the pinion sprocket and the chain A continuously variable transmission mechanism that transmits power by meshing with a gear has been developed.

  This continuously variable transmission mechanism is apparently formed by a plurality of pinion sprockets that are supported so as to rotate in a radial direction and integrally rotate while maintaining an equal distance from the rotating shaft and revolve with respect to the rotating shaft. Large sprockets (hereinafter referred to as “composite sprockets”) are provided on each of the input side and output side, and a chain is wound around these composite sprockets. Each pinion sprocket moves synchronously in the radial direction while maintaining the same distance from the rotation axis, whereby the size of the polygon changes in a similar manner, thereby changing the gear ratio.

  In such a speed change mechanism, power is transmitted by meshing the pinion sprocket and the chain, so there is no possibility of slippage unlike the power transmission between the belt and the pulley of the belt type continuously variable transmission. However, when the pinion sprocket and the chain are meshed, the chain may come off from the teeth of the pinion sprocket, or the chain may be violent and noise may be generated.

  That is, in the chain, a number of links are connected by pins, and sliding friction is generated at the coupling portion between the pins and the links. Further, the chain is also stretched according to the tension. As the chain stretches, the chain is likely to be violated, so noise is generated and the chain is separated. Further, when the chain tension approaches the limit, a force is generated in a direction in which the sprocket is detached from the chain. In particular, when the chain meshes with the sprocket, a large tension is generated locally and a force in the direction of separation is generated. On the other hand, if there is a portion where the tension is low due to the elongation of the chain, the chain is easily detached.

  In this regard, in Patent Documents 1 and 2, a guide member (idler pulley, tension device, chain guide, etc.) that presses the chain from the outside is provided at a position where the chain is separated from the composite sprocket between the two composite sprockets. Yes. Since these guide members secure the tension where the tension of the chain tends to decrease, an effect of preventing the chain from being detached can be expected.

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

  However, as in Patent Documents 1 and 2, when the chain is pressed from the outside with a guide member, the chain trajectory is changed when changing the gear ratio, so that the guide member can be operated properly. It is necessary to make the guide member follow the change in the trajectory of the chain. However, this point is not mentioned in Patent Documents 1 and 2.

  The present invention was devised in view of the above problems, and in a transmission mechanism that transmits power by a chain wound around a composite sprocket, it can suppress the runaway and separation of the chain while following the change in the trajectory of the chain. It is an object of the present invention to provide a speed change mechanism including a trajectory guide mechanism that can be used.

  (1) A speed change mechanism according to the present invention includes a rotating shaft to which power is input or output, a plurality of pinion sprockets supported so as to revolve in a radial direction and integrally with the rotating shaft, and the plurality of pinion sprockets. Two composite sprockets having a sprocket moving mechanism that moves the pinion sprockets of the pinion sprockets in the radial direction while maintaining an equal distance from the axis of the rotating shaft, and a chain wound around the two sets of composite sprockets A speed change mechanism that changes a gear ratio by changing a contact circle radius that surrounds any of the plurality of pinion sprockets and is in contact with any of the plurality of pinion sprockets. A track guide mechanism that pressure-contacts from the outer peripheral side to guide the track of the chain, and a change in the track of the chain by changing the radius of the contact circle. And a said track guide mechanism chain tracking moving mechanism for moving along a track orbit, the chain follower moving mechanism is characterized in that in conjunction with the sprocket moving mechanism.

  (2) A pre-meshing mechanism for phase-aligning the teeth of the pinion sprocket with the link groove on the inner periphery of the chain immediately before the pinion sprocket reaches a meshing point at which meshing with the chain is started by the revolution, It is preferable that a track guide mechanism is provided in the pre-meshing mechanism.

  (3) The pre-meshing mechanism is engaged with the chain from the outer peripheral side and rotates in phase synchronization with the chain, and rotates in phase synchronization with the first synchronous rotation member. It is preferable that the second synchronous rotating member that engages with the pinion sprocket to adjust the phase of the pinion sprocket immediately before reaching the meshing point, and that the first synchronous rotating member functions as the trajectory guide.

  (4) In this case, the first synchronous rotating member includes an input side synchronizing sprocket whose teeth are always meshed with the link groove on the outer periphery of the chain, and the second synchronous rotating member rotates integrally with the pinion sprocket. An output side sprocket and an input side sprocket shaft are provided to rotate integrally with each other, and have a pseudo link groove on the outer periphery imitating the link groove of the chain, and the pinion sprocket It is preferable that the pseudo link groove includes a synchronization rotating body that meshes with the teeth of the output-side synchronization sprocket when it arrives immediately before.

  (5) Furthermore, a support member that rotatably supports the first synchronous rotation member and the second synchronous rotation member is provided, and the chain following movement mechanism moves the support member along the following track. preferable.

  (6) The chain follow-up movement mechanism includes a guide rail extending along the follow-up track, a travel member that movably supports the support member and travels along the guide rail, and guides the travel member to the guide. It is preferable to include a follow-up drive mechanism that moves along the rail.

  (7) The support member includes a bearing portion that rotatably supports the first synchronous rotating member and the second synchronous rotating member, and an axial shape that extends in a press-contact direction in which the first synchronous rotating member is pressed against the chain. The shaft-like portion is supported by the traveling member so as to be movable in the axial direction, and the bearing portion is urged in the pressure-contact direction between the shaft-like portion and the traveling member. It is preferable that a spring member that elastically presses the first synchronous rotating member against the chain is provided.

  (8) The follow-up drive mechanism has a follow-up cam groove that extends in a direction inclined with respect to the axial direction of the rotating shaft, and moves in the axial direction. A chain follow-up movement drive device for driving the axial movement member in the axial direction and the movement of the chain follow-up movement axial movement member fixed to the support member and in sliding contact with the follow-up cam groove. Accordingly, it is preferable to include a slide member that moves along the following track.

  (9) In the sprocket moving mechanism, a plurality of fixed radial grooves into which the support shafts of the plurality of pinion sprockets are inserted are formed, and a fixed disk that rotates integrally with the rotary shaft, and the fixed radial grooves intersect with each other. A plurality of movable radial grooves, which are arranged at the intersections and into which the support shafts are respectively inserted, are arranged concentrically with the fixed disk and are rotatable relative to the fixed disk; and the movable disk is fixed to the fixed disk. A relative rotational drive mechanism that moves relative to the radial direction and moves the intersecting portion in the radial direction, the relative rotational drive mechanism provided along the axial direction of the rotational shaft, and the fixed disk A first cam groove provided in a first rotating portion that rotates integrally with the first cam groove, and provided along the axial direction while intersecting the first cam groove, And a second cam groove provided in a second rotating portion that rotates integrally with the shaft, and a second intersecting portion where the first cam groove and the second cam groove intersect, and one end portion thereof in the radial direction. A protruding cam roller, a groove for accommodating the one end of the cam roller, and an axial moving member for moving the sprocket that moves in the axial direction together with the cam roller, and an axial moving member for moving the sprocket in the axial direction A chain follow-up movement axial movement member provided integrally with the sprocket movement axial movement member, and the sprocket movement drive device comprises the chain follow-up movement shaft. It is preferable that the directional drive mechanism is also used.

  According to the speed change mechanism of the present invention, each pinion sprocket constituting the composite sprocket and the chain wound around the composite sprocket are engaged to transmit power. At this time, the track guide mechanism is located near the engagement point. Since the chain abuts against the chain from the outer peripheral side and guides the track of the chain, it is possible to suppress the runaway or detachment of the chain.

  In particular, when changing the gear ratio, the trajectory of the chain is changed. Therefore, in order for the trajectory guide mechanism to operate properly, the trajectory guide mechanism needs to follow the change in the trajectory of the chain. Since the moving mechanism is interlocked with the sprocket moving mechanism, the trajectory guide can surely follow the change in the trajectory of the chain.

It is a side view which shows typically the principal part of the transmission mechanism concerning one Embodiment of this invention, and is equivalent to the AA arrow line view of FIG. It is sectional drawing which shows typically the principal part which paid its attention to the relative rotational drive mechanism for radial direction movements, such as a pinion sprocket of the transmission mechanism concerning one Embodiment of this invention. FIG. 3 is a perspective view schematically showing a main part of the speed change mechanism according to the embodiment of the present invention, and is a perspective view seen from the direction B in FIG. 2, and a fixed disk portion of the speed change mechanism is shown by B <b> 1 in FIG. 2. The movable disk is removed along the line -B1. It is a side view paying attention to the fixed disk of the speed change mechanism concerning one embodiment of the present invention, and is equivalent to a CC arrow view of FIG. It is a side view paying attention to the movable disk of the speed change mechanism concerning one embodiment of the present invention, and is equivalent to a DD arrow view of FIG. In the speed change mechanism according to one embodiment of the present invention, a fixed disk and a movable disk for radial movement such as a pinion sprocket and the support shafts of the pinion sprocket and guide rod moved by these are shown, and the sprocket moving mechanism and the rod moving mechanism FIG. 3 is a view corresponding to the CC arrow view of FIG. 2 in which the tangent radius increases in the order of (a), (b), and (c), and the tangent radius is the smallest diameter. Is shown in (a), and the maximum diameter is shown in (c). It is a side view which shows typically the principal part of the transmission mechanism concerning one Embodiment of this invention, and is equivalent to the F arrow line view of FIG. It is a principal part enlarged view which expands and shows the 1st cam groove and 2nd cam groove of the transmission mechanism concerning one Embodiment of this invention, and is the EE arrow line view of FIG. It is a perspective view which shows a part of chain follower mechanism of the speed change mechanism concerning one Embodiment of this invention, and is equivalent to the G direction arrow view of FIG. It is a figure which shows a part of chain follow-up mechanism of the transmission mechanism concerning one Embodiment of this invention, and is equivalent to the HH arrow line view of FIG. It is typical sectional drawing of the principal part of the speed change mechanism which paid its attention to the pre-meshing mechanism and phase shift allowable power transmission mechanism concerning one Embodiment of this invention. It is a typical front view of the rotary body for a synchronization of the pre-meshing mechanism concerning one Embodiment of this invention. It is a figure explaining the chain concerning one embodiment of the present invention, (a) is the typical perspective view, (b) is the typical front view, and (c) is the typical top view. is there. It is a figure explaining the phase shift allowable power transmission mechanism of the pinion sprocket concerning one Embodiment of this invention, (a) is a typical block diagram seen from the axial direction of the pinion sprocket, (b) is the biasing member. (C), (d) is a principal part block diagram explaining operation | movement of a phase shift allowance power transmission mechanism.

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

[1. Constitution〕
First, the configuration of the speed change mechanism according to the present embodiment will be described.
[1-1. Overall structure of transmission mechanism]
As shown in FIGS. 1 to 3, the speed change mechanism includes two sets of composite sprockets 5, 5 and a chain 6 wound around the composite sprockets 5, 5. The composite sprocket 5 is an apparent large sprocket formed such that a plurality of pinion sprockets 20 and a plurality of guide rods 29, which will be described in detail later, form polygonal (here, 21-sided) vertices. means.

  One of the two sets of composite sprockets 5 and 5 is a composite sprocket 5 (shown to the right in FIG. 1) that rotates integrally with the input-side rotary shaft 1 (input shaft), and the other is the output side. 1 is a composite sprocket 5 (shown on the left in FIG. 1) that rotates integrally with the rotation shaft 1 (output shaft). Since these composite sprockets 5 and 5 are configured in the same manner, the following description will focus on the output-side composite sprocket 5 and describe its configuration. The input shaft 1 includes a small-diameter shaft portion 1a having a reduced diameter at an intermediate portion.

The composite sprocket 5 includes a rotating shaft 1 and a plurality (three in this case) of pinion sprockets 21, 22, and 23 (hereinafter referred to as reference numeral 20 unless otherwise distinguished) supported movably in the radial direction with respect to the rotating shaft 1. ) And a plurality (18 in this case) of guide rods 29. The three pinion sprockets 20 are arranged at equal intervals along the circumferential direction on the circumference centered on the axis C ₁ of the rotary shaft 1, and six guide rods 29 are interposed between the pinion sprockets 20. Is arranged.

  Although not shown in FIG. 1, the composite sprocket 5 rotates a sprocket moving mechanism 40A that moves a plurality of pinion sprockets 20 and the rotation pinion sprockets 22 and 23 of the pinion sprocket 20 in conjunction with the sprocket movement mechanism 40A. And a rod moving mechanism 40B that moves the plurality of guide rods 29 (see FIGS. 2 to 6). Details of these will be described later.

  This speed change mechanism has an outer diameter of an apparent large sprocket formed such that the pinion sprocket 20 and the guide rod 29 form the apex of a polygon (here, a twenty-one-sided polygon), that is, the outer diameter of the composite sprocket 5. The gear ratio is changed by changing (expanding / reducing diameter). Since the gear ratio can be continuously changed, it can be configured as a continuously variable transmission, but can also be changed in stages to be configured as a multi-stage stepped transmission.

  The outer diameter of the composite sprocket 5 is a radius of a circle (tangent circle) that surrounds all of the plurality of pinion sprockets 20 and is in contact with any of the plurality of pinion sprockets 20 (hereinafter referred to as “tangent circle radius”). Corresponding. Further, since the chain 6 is wound around the composite sprocket 5, it can be said that the outer diameter of the composite sprocket 5 corresponds to the contact radius between the plurality of pinion sprockets 20 and the chain 6. Therefore, when the tangent radius or the contact radius is the minimum diameter, the outer diameter of the composite sprocket 5 is the minimum diameter. When the tangent radius or the contact radius is the maximum diameter, the outer diameter of the composite sprocket 5 is the maximum. Is the diameter.

For this reason, it can be said that the speed change mechanism changes the speed ratio by changing the tangent radius.
In FIG. 1, a solid line indicates that the input side tangent radius is the minimum diameter and the output side tangent radius is the maximum diameter, and the input side tangent radius is the maximum diameter and the output side tangent radius is the maximum diameter. The one with the smallest radius is indicated by a two-dot chain line.
Hereinafter, the components of the speed change mechanism will be described in this order for the composite sprocket 5, the chain 6 wound around the composite sprocket 5, and the mechanisms related to both the composite sprocket 5 and the chain 6.

[1-2. (Composite sprocket)
In the following description of the configuration of the composite sprocket 5, first, main components such as the pinion sprocket 20, the guide rod 29, the fixed disk 10 and the movable disk 19, the first rotating part 15 and the second rotating part 15 will be described in this order. Subsequently, mechanisms such as a sprocket moving mechanism 40A, a rod moving mechanism 40B, a mechanical rotation driving mechanism 50, and an interlocking mechanism 60 that operate these components 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 fixed disk 10 and the movable disk 19 Corresponds to the radial direction of the rotating shaft 1.

[1-2-1. (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 rotational speed of the rotating shaft 1 is equal to the rotational speed of the pinion sprocket 20. In FIGS. 1 and 3, clockwise revolution directions are indicated by white arrows.

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

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

The fixed pinion sprocket 21 and the rotating pinion sprockets 22 and 23 are formed so as to protrude from the main body portions 21b, 22b, and 23b coupled to the support shafts 21a, 22a, and 23a and the entire outer periphery of the main body portions 22b and 23b. It has teeth 21c, 22c, 23c.
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.

  Although details will be described later, in FIGS. 1 and 3, the first rotation pinion sprocket 22 rotates counterclockwise when the tangent radius is expanded, and rotates clockwise when the tangent radius is reduced. On the other hand, the second rotation pinion sprocket 23 rotates clockwise when the tangent radius is increased, and rotates counterclockwise when the tangent radius is reduced.

  When the pinion sprockets 21, 22, and 23 are not distinguished from each other, the pinion sprocket is denoted by reference numeral 20, the support shaft of the pinion sprocket 20 is denoted by reference numeral 20a, the main body of the pinion sprocket 20 is denoted by reference numeral 20b, and the pinion The teeth of the sprocket 20 are denoted by reference numeral 20c.

  Further, between each pinion sprocket 20 and its support shaft 20a, the phase of the pinion sprocket 20 with respect to each support shaft 20a is allowed within a certain range (that is, only a minute rotation), and each pinion sprocket 20 is also allowed. A phase shift allowable power transmission mechanism (also referred to as a micro-rotation allowance mechanism) 190 that elastically biases the power to a neutral position in the permissible micro-rotation range to realize power transmission is interposed. This will be described later.

  In this embodiment, as illustrated for the rotation pinion sprocket 22 in FIG. 2, each pinion sprocket 21, 22, 23 includes three rows of gears in the axial direction, and a chain corresponding to each of the rows of gears. 6 is also wound around different things. Here, the three rows of gears of each pinion sprocket 20 are provided at a distance from each other via a spacer.

The number of gear rows of each pinion sprocket 21, 22, 23 depends on the magnitude of the transmission torque of the continuously variable transmission mechanism, but may be two rows, four rows or more, or one row.
FIG. 2 is a schematic cross-sectional view partially expanded for easy understanding, and the two composite sprockets 5 and 5 are largely separated from each other. As shown in FIGS. 1 and 3, they are arranged close to each other.

[1-2-2. Guide rod)
As shown in FIG. 1, the plurality of guide rods 29 are capable of reducing the variation in the distance between the chain 6 and the axis C ₁ of the rotating shaft 1, that is, allowing the path of the chain 6 around the rotating shaft 1. Equipped as close to the circular orbit as possible. That is, by providing a plurality of guide rods 29 between the pinion sprockets 21, 22, 23, the pinion sprockets 21, 22, 23 and each guide rod 29 are polygons having a larger number of angles (substantially regular polygons). The shape of The chain 6 that meshes with the pinion sprockets 21, 22, and 23 rolls along the polygonal shape while being guided by the guide rod 29 by contacting the outer peripheral surface of the guide rod 29.

  Each guide rod 29 has a cylindrical guide member 29b fitted on the outer periphery of a rod support shaft 29a (shown by a broken line in FIG. 1), is supported by the rod support shaft 29a, and is an outer peripheral surface of the guide member 29b. To guide the chain 6.

Note that the number of guide rods 29 is not limited to 18 and may be more or less. In this case, it is preferable that the same number of guide rods 29 are provided between the pinion sprockets 20. In this case, the number of guide rods 29 is a multiple of the number of pinion sprockets 20 (three in this case). Moreover, as provided many guide rods 29 closer to composite sprocket 5 to a perfect circle, although it is possible to reduce variation in the distance between the chain 6 and the axis C ₁ of the rotary shaft 1, the manufacturing cost and weight due to an increase in parts In addition, there is a need to ensure the strength and rigidity of each part, and further there are structural limitations of the moving mechanism 40B described later. Is preferred. In order to obtain a simple configuration, the guide rod 29 may be omitted.

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

  As shown in FIGS. 4 and 6, the fixed disk 10 corresponds to the fixed radial grooves 11 a, 11 b, 11 c for the sprockets provided for the pinion sprockets 21, 22, 23 and the guide rods 29. Two types of radial grooves are formed, which are a fixed radial groove 12 for rods (a reference numeral is attached to only one location). In FIG. 4, a clockwise revolution direction is indicated by a white arrow.

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

In the fixed radial groove 12 for rod (a reference is given to only one place), a rod support shaft 29a (a reference is given to only one place) of the corresponding guide rod 29 is inserted.
Details of the shapes of the fixed radial grooves 11a, 11b, 11c, and 12 will be described later.

[1-2-4. (Movable disc)
As shown in FIG. 2, the movable disk 19 is provided on each of one side and the other side with the pinion sprocket 20 interposed therebetween. As shown in FIG. 1, connecting shafts 1b are provided between the pinion sprockets 21, 22, and 23 so as not to interfere with each other. Both movable discs 19 are connected to each other by these connecting shafts 1b. As a result, the movable disk 19 on one side and the movable disk 19 on the other side rotate together.

  As shown in FIGS. 5 and 6, the movable disk 19 (shown by a broken line in FIG. 6) has a sprocket movable radial groove 19 a and a rod movable radial groove 19 b (both are provided with reference numerals only in one place, Two types of movable radial grooves are formed (shown by broken lines in FIG. 6). Note that the outer shape of the movable disk 19 is circular, and overlaps with the outer shape of the fixed disk 10 that is circular, but in FIG. 6, 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. Pinion sprockets 21, 22, and 23 are provided at first intersecting points CP ₁ where only the sprocket movable radial grooves 19 a and the sprocket fixed radial grooves 11 a, 11 b, and 11 c intersect (only one place is indicated in FIG. 6). Each support shaft 21a, 22a, 23a is located.

[1-2-5. (First rotating part)
As shown in FIG. 2, the first rotating portion 15 is a portion that rotates integrally with the fixed disk 10, that is, a portion that rotates integrally with the rotating shaft 1. Here, the first rotating portion 15 is provided on a part of the rotating shaft 1. The first rotating portion 15 is disposed on the outer side in the axial direction than the fixed disk 10 and the movable disk 19.

As shown in FIGS. 2, 7 and 8, the first rotating portion 15 is provided with a first cam groove 15a. The first cam groove 15 a is provided so as to be recessed along the axial direction of the rotary shaft 1. Here, the first cam groove 15 a is formed so as to extend in parallel with the axis C ₁ of the rotating 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.

[1-2-6. (Second rotating part)
As shown in FIGS. 2 and 7, the second rotating portion 16 is connected to the movable disk 19 via the connecting portion 17. In FIG. 7, a white arrow indicates the counterclockwise revolution direction. First, the connecting portion 17 will be described, and then the second rotating portion 16 will be described.

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

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

As shown in FIGS. 2 and 7, the radial direction connecting portion 17 b has a radially outer side connected to the axial direction connecting portion 17 a and a radially inner side connected to the second rotating portion 16. 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. 7, the radial connection portion 17b is provided with a lightening portion 17c. The lightening portion 17c is formed at a position corresponding to the racks 53 and 54 and the pinions 51 and 52 of the mechanical rotation driving mechanism 50, which will be described in detail later. FIG. 6 shows an example in which fan-shaped thinned portions 17c provided at three locations are provided at equal intervals with the radial connecting portion 17b interposed therebetween. However, the shape and number of the thinned portions 17c may be set according to the surrounding configuration, required specifications, and the like, and various shapes and numbers can be employed.

Next, the second rotating unit 16 will be described.
As shown in FIGS. 2 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 has a cylindrical shape concentric with the axis C ₁ of the rotating shaft 1. Is formed. Here, as shown in FIG. 2, the second rotating portion 16 is shifted from the outer peripheral end portion 19 t of the movable disk 19 to the inner peripheral side and provided along the axial direction.

As shown in FIGS. 2, 7 and 8, the second rotating portion 16 is provided with a second cam groove 16a. The second cam groove 16a is provided adjacent to the outer periphery of the first cam groove 15a. The second cam groove 16a is formed to extend in a direction intersecting the first cam groove 15a, that is, in a direction obliquely intersecting the axial direction of the rotary shaft 1.
FIG. 7 illustrates a case where the second cam groove 16a (a reference numeral is attached to only one place) is provided at four places at intervals in the circumferential direction. The number of formations is set according to the formation location and the number of formations of the first cam grooves 15a.

[1-2-7. (Relative rotation drive mechanism)
In addition to the first cam groove 15a provided in the first rotating part 15 and the second cam groove 16a provided in the second rotating part 16, the relative rotation drive mechanism 30 includes the first cam groove 15a and the first cam groove 15a. A cam roller 90 disposed at a second intersection CP ₂ where the two cam grooves 16a intersect, an eyeglass fork (an axial movement member for sprocket movement) 35 for moving the cam roller 90 in the axial direction, and the eyeglass fork 35 And an axial drive mechanism 31 for moving the sprocket.

Hereinafter, the cam roller 90, the glasses fork 35, and the sprocket moving axial drive mechanism 31 will be described in this order.
As shown in FIGS. 2 and 7, the cam roller 90 is formed in a cylindrical shape. This cam roller 90 has an axial center along a direction orthogonal to the axial center C ₁ of the rotating shaft 1, and a second intersecting point CP ₂ (both of which the first cam groove 15 a and the second cam groove 16 a intersect each other). It is inserted through only one place. For this reason, the cam roller 90 rotates around the axis C ₁ of the rotating shaft 1 in conjunction with the rotation of the rotating shaft 1. A bearing is fitted on the outer periphery of the cam roller 90 at locations corresponding to the first cam groove 15a and the second cam groove 16a. Here, one set of the two sets of cam rollers 90 and 90 having a phase difference of 180 degrees is used as a continuous one, but these may be configured separately.

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

  The glasses fork 35 is provided across the two sets of composite sprockets 5 and 5. The spectacles fork 35 includes an annular cam roller support part 35a (corresponding only to one side) provided corresponding to each of the composite sprockets 5 and 5, and a bridge part 35b for connecting the cam roller support parts 35a. Have. The first rotating portion 15 and the second rotating portion 16 are disposed on the inner peripheral side of the cam roller support portion 35a.

  The glasses fork 35 is a plate-like member, and is parallel to the disks 10 and 19 and is juxtaposed 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. Yes.

The cam roller support portion 35a is provided with a groove portion 35c so as to form an annular space over the entire inner circumference.
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 37 (a reference numeral is given only at one place) that can be in rolling contact with the cam roller 90. This rolling element 37 is provided to prevent the cam roller 90 from rotating around the axis when the cam roller 90 rotating around the axis C ₁ of the rotating shaft 1 contacts the side wall of the groove 35c. A rolling element 37 is disposed on a cam roller support portion 35a that forms a side wall of 35c. Here, the some rolling element 37 is arrange | positioned along with the fixed space | interval over the perimeter of the groove part 35c. 2 and 7 illustrate a needle bearing as the rolling element 37, a ball bearing may be used instead.

  The axial drive mechanism 31 for moving the sprocket includes a motor 32, a motion conversion mechanism 33 that switches the rotational motion of the output shaft 32a of the motor 32 to a linear motion, and the glasses fork 35 to move the glasses fork 35 in the axial direction. And a fork support portion 34 that is supported and linearly moved by the motion conversion mechanism 33. As the motor 32, a stepping motor can be used. Further, the spectacle fork 35 is penetrated by a guide pin 36 extending in the axial direction. When the spectacle fork 35 is moved in the axial direction, the guide pin 36 guides the movement, and the spectacle fork 35 does not tilt with the movement. The posture is maintained.

Hereinafter, with reference to FIG.2 and FIG.7, the axial direction drive 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.
Further, the fork support portion 34 has a female screw portion 34a threadedly engaged with a male screw portion 32b formed on the output shaft 32a of the motor 32 on the inner periphery, and is engaged with the bridge portion 35b of the glasses fork 35 on the outer periphery. A fork groove 34b is recessed.

  The fork groove 34b is formed to have a width (axial length) corresponding to the thickness (axial length) of the bridge portion 35b of the glasses fork 35. An intermediate portion of the bridge portion 35b (between the two composite sprockets 5 and 5) is fitted into the fork groove 34b, and the fork support portion 34 and the bridge portion 35b of the glasses fork 35 are integrally coupled.

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 drive mechanism 31 converts the rotational motion of the motor 31 into a linear motion by the motion conversion mechanism 33, and causes the fork support portion 34 to linearly move in the axial direction by this linear motion.
The relative rotation drive mechanism 30 including the glasses fork 35 and the axial drive mechanism 31 for moving the sprocket is shifted in the axial direction from the pinion sprockets 21, 22, and does not interfere with each other.

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 drive mechanism 31, the glasses fork 35 coupled to the fork support 34 moves integrally in the axial direction. Accordingly, the cam rollers 90 of the two composite sprockets 5 and 5 also move in the axial 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 rotates relatively.

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

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

Thus, relative rotation drive mechanism 30 drives rotates relative to the fixed disk 10 the movable disk 19 by the sprocket movement axis drive mechanism 31 moves the first intersection CP ₁ in the radial direction. Further, the relative rotation drive mechanism 30 drives the movable disks 19 of the two composite sprockets 5 and 5 relative to the fixed disk 10 via the glasses fork 35, so that both the input and output composite sprockets 5 and 5 , it moves each first intersection CP ₁ in the radial direction.
Of course, the two composite sprockets 5 and 5 are linked when, for example, the input-side composite sprocket 5 expands, the output-side composite sprocket 5 contracts, and conversely, the input-side composite sprocket 5 contracts. The composite sprocket 5 on the output side is configured to expand its diameter.

[1-2-8. 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 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 sprocket moving mechanism 40A includes a fixed disk 10 formed with fixed radial grooves 11a, 11b, and 11c for sprockets in which support shafts 21a, 22a, and 23a provided in pinion sprockets 21, 22, and 23 are inserted, and a sprocket. The movable disk 19 is provided with a movable radial groove 19a and a relative rotation drive mechanism 30 (see FIGS. 2 and 7).

The rod moving mechanism 40B includes a fixed disk 10 in which the rod fixed radial groove 12 into which the rod support shaft 29a is inserted, a movable disk 19 in which the rod movable radial groove 19b is formed, and a relative rotation drive mechanism. 30.
As described above, the configurations of the moving mechanisms 40A and 40B are the same except for the support shafts of the respective moving objects.

Next, movement by the moving mechanisms 40A and 40B will be described with reference to FIGS. 6 (a) to 6 (c).
FIG. 6 (a) shows the support shafts 21a, 22a, 23a of the pinion sprockets 21, 22, 23 (see FIGS. 1 and 2 etc.) in the radial grooves 11a, 11b, 11c, 19a and the rod support in the radial grooves 12, 19b. It shows what the shaft 29a is located at the closest position from the axis C ₁ of the rotary shaft 1.

In this case, when the rotational phase of the movable disk 19 is changed with respect to the fixed disk 10 by the relative rotation drive mechanism 30 (see FIG. 2), the fixed radial grooves 11a for the sprocket are sequentially displayed in the order of FIGS. 6 (b) and 6 (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 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.

[1-2-9. Mechanical rotation drive mechanism)
Next, the mechanical rotation driving mechanism 50 will be described with reference to FIGS. Here, since the mechanical rotation driving mechanism 50 is configured symmetrically with the pinion sprocket 20 in between, the description will be made focusing on the configuration on one side (the upper side in FIG. 2).

As described above, the mechanical rotation drive mechanism 50 rotates the rotation pinion sprockets 22 and 23 so that the phase shift between the pinion sprockets 20 with respect to the chain 6 is eliminated from the sprocket moving mechanism 40A. It is mechanically driven to rotate in conjunction with it. In other words, the mechanical rotation drive mechanism 50 includes the rotation pinion sprocket 22, so as to eliminate the phase shift of the plurality of pinion sprockets 20 with respect to the chain 6 in accordance with the radial movement of the plurality of pinion sprockets 20 by the sprocket moving mechanism 40 </ b> A. 23 is driven to rotate in conjunction with the sprocket moving mechanism 40A.
However, the mechanical rotation drive mechanism 50 also has a configuration that does not rotate the fixed pinion sprocket 21 when moving in the radial direction.

First, a configuration for preventing the fixed pinion sprocket 21 (see FIG. 1) from rotating in the mechanical rotation driving mechanism 50 will be described.
As shown in FIGS. 3 and 7, the support shaft 21 a of the fixed pinion sprocket 21 is inserted into 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. 3 is inserted into the sprocket fixed radial groove 11a of the fixed disk 10 on the lower side of FIG.

  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. It can be said that the pinion sprocket 21 is fixed. That is, the guide member 59 is formed in a shape that is slidable in the radial direction in the fixed radial groove 11a for the sprocket and has a function of preventing rotation. Here, the predetermined length is a length that can secure a drag force of a rotational force that causes the fixed pinion sprocket 21 to rotate.

4 and 6, the fixed radial groove for sprocket 11a is formed to have a longitudinal direction in the radial direction, and the side wall surface of the rectangular guide member 59 faces the fixed radial groove for sprocket 11a. The example which slides on a wall surface is shown.
Further, if bearings are attached to the side walls of the guide member 59 in contact with the inner wall of the fixed radial groove 11a for the sprocket, particularly the four corners of the guide member 59, smoother sliding of the guide member 59 can be ensured.

Next, the structure for rotationally driving the rotation pinion sprockets 22 and 23 in the mechanical rotation drive mechanism 50 will be described.
The mechanical rotation drive mechanism 50 meshes with the pinions 51 and 52 fixed so as to rotate integrally with the support shafts 22a and 23a of the rotation pinion sprockets 22 and 23, respectively, corresponding to the pinions 51 and 52, respectively. Racks 53 and 54 provided as described above.

  The pinions 51 and 52 are provided at axial ends of the support shafts 22a and 23a of the rotation pinion sprockets 22 and 23, respectively. 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. 7, the first rack 53 is arranged on the retard side with respect to the first pinion 51 on the basis of the revolution direction. Conversely, the second rack 54 is disposed on the advance side with respect to the second pinion 52 on the basis of the revolution direction. For this reason, the pinions 51 and 52 and the racks 53 and 54 are opposite to each other by the racks 53 and 54 meshing with the pinions 51 and 52 when the pinions 51 and 52 are moved in the diameter increasing direction or the diameter reducing direction. It is arranged to be rotated.

  That is, the mechanical rotation drive mechanism 50 sets the rotation phase for rotation of the rotation pinion sprockets 22 and 23 according to the radial position of the pinion sprocket 20 moved by the sprocket moving mechanism 40A. That is, the mechanical rotation drive 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.

[1-3. chain〕
Next, the chain 6 will be described.
As shown in FIG. 13 (a), 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.

  Also, depending on the transmission torque of the speed change mechanism, two or less or four or more chains 6 are used. In this case, it is preferable that the pitch of each chain is shifted by “1 / number of chains”.

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

  In this embodiment, as shown in FIGS. 13A and 13C, a large number of auxiliary link plates 63 are arranged in series in the power transmission direction at both ends in the thickness direction of the chains 6A, 6B, 6C. The auxiliary link plate row 63S is provided. The auxiliary link plate row 63S is guided by the guide rod 29 by a guide surface 63a formed on the inner peripheral side of the auxiliary link plate 63.

  However, in this embodiment, at least one of the chains 6A, 6B, 6C (here, the chain 6A) has teeth 63a formed on the outside of the chain 6 as shown in FIG. In FIG. 13 (a) and (c), the tooth 63a is omitted.) That is, as shown in FIG. 13B, on the inner peripheral side of each link plate 61 of the chain 6, a pair of teeth 61a that form a link groove 61c is formed between them. A pair of teeth 63a is formed on the outer peripheral side of the auxiliary link plate 63, and an outer link groove 63b is formed between the pair of teeth 63a.

[1-4. Pre-meshing mechanism with track guide)
Next, the pre-meshing mechanism with a trajectory guide which is characteristic in the continuously variable transmission mechanism will be described.
Since the pinion sprocket 20 revolves with respect to the rotating shaft 1, the state of meshing with the chain 6 and the state of separating from the chain 6 are repeated, and when changing the gear ratio, the teeth 20c of the pinion sprocket 20 and the chain Therefore, when the pinion sprocket 20 starts to engage with the chain 6, the teeth 20c of the pinion sprocket 20 may be out of phase with the link groove 61c of the chain 6 and jump out of teeth. There is.

  Therefore, in each composite sprocket 5, the phase of the teeth 20c of the pinion sprocket 20 is adjusted in the vicinity of the engagement point where the engagement of the teeth 20c of the pinion sprocket 20 and the link groove 61c of the chain 6 starts. A pre-meshing mechanism 170 is provided.

  As shown in FIG. 10, the pre-meshing mechanism 170 engages with the chain 6 and rotates in phase synchronization with the first synchronous rotation member 171 and rotates in phase synchronization with the first synchronous rotation member 171. A second synchronous rotating member 172 that engages with the pinion sprocket 20 and adjusts the phase of the pinion sprocket 20 immediately before the meshing point is provided.

The first synchronous rotation member 171 includes an input-side synchronization sprocket 173 in which the teeth 173 a are always engaged with the outer link groove 63 b of the chain 6.
The second synchronization rotating member 172 includes an output side synchronization sprocket 176 that rotates integrally with the pinion sprocket 20 and a synchronization chain (synchronization rotating body) 175 that meshes with the output side synchronization sprocket 176.

Note that the input-side synchronization sprocket 173 has substantially the same teeth 173a as the pinion sprocket 20 and has a smaller diameter than the pinion sprocket 20 due to space constraints, but in order to ensure smooth operability. Those having a diameter as large as possible are preferred.
The output-side synchronization sprocket 176 is the same diameter as the pinion sprocket 20.

  The synchronization chain 175 is mounted on the shaft 171 a of the first synchronous rotation member 171 so as to rotate together with the input-side synchronization sprocket 173. The synchronization chain 175 is a chain formed by connecting pseudo links 175a simulating the link plate 61 of the chain 6 with connecting pins 175b. A pseudo link groove 175 c simulating the link groove 61 c is formed on the outer periphery of the synchronization chain 175. The pseudo link groove 175c meshes with the teeth 176a of the output side synchronization sprocket 176 when the pinion sprocket 20 arrives just before the meshing point.

  The synchronization chain 175 and the output-side synchronization sprocket 176 are arranged on the outer side in the axial direction than the chain 6A on one end side so that the synchronization chain 175 does not interfere with any of the chains 6A to 6C. The synchronization chain 175 is a rotating body simulating the chains 6A to 6C, and can also be called a sprocket having teeth corresponding to the pseudo link groove 175c.

  In this embodiment, as shown in FIG. 12, the synchronization chain 175 imitates a silent chain. Since the synchronization chain 175 has a relatively small diameter, the number of pseudo links 175a is reduced, and the pseudo links 175a are reduced. The connection angle between them also increases. For this reason, even if the pseudo link groove 175c of the pseudo link 175a is formed at a relatively wide angle, the angle of the pseudo link groove 175c becomes sufficiently large. Therefore, the adjacent pseudo link 175a has an angle where the teeth forming the pseudo link groove 175c are slightly overlapped without being completely overlapped, thereby suppressing the substantial opening angle of the pseudo link groove 175c. However, even in this case, the substantial angle of the pseudo link groove 175c is sufficiently large so that the output-side synchronization sprocket 176 can easily mesh with the pseudo link groove 175c.

  As shown in FIG. 1, the pre-meshing mechanism 170 is provided in each composite sprocket 5, but the input-side synchronization sprocket 173 and the shaft 171a of the synchronization chain 175 are attached to the support member 180 as shown in FIG. The input-side synchronization sprocket 173 is elastically pressed against the chain 6. In particular, the input-side synchronization sprocket 173 that is elastically pressed against the chain 6 functions as a track guide that contacts the chain 6 from the outer peripheral side and guides the track of the chain 6 so as not to swell from the outside. That is, the pre-meshing mechanism 170 also has a track guide mechanism that guides the track of the chain 6.

  As shown in FIG. 10, the support member 180 has a bearing portion 181 that rotatably supports the input-side synchronization sprocket 173 and the synchronization chain 175, and a bearing portion 181 fixed to the tip, and the input-side synchronization sprocket 173. And an axial arm portion 182 extending in the press-contact direction for press-contacting to the chain 6A. The arm portion 182 is slidably supported by a slide member 183 that slides along a follow-up track, which will be described later, and the support member 180 is movable in the press-contact direction and can move along the follow-up track. Yes.

  In other words, the intermediate portion of the arm portion 182 is inserted into the hole portion of the arm engaging portion 183b of the slide member 183, and the arm portion 182 is guided by this hole portion so that the input-side synchronization sprocket 173 becomes the chain 6A. It is movable in the direction of pressure contact.

  The bearing 181 is urged in the press-contact direction between the arm 182 and the arm engagement portion 183b of the slide member 183, and the input-side synchronization sprocket (following guide) 173 is elastically pressed against the chain 6A. A coil spring (spring member) 186 is provided. A stopper 182a is provided at the base end of the arm portion 182 so that the arm portion 182 does not separate from the arm engaging portion 183b.

  Further, the trajectory of the chain 6 is changed by changing the tangent radius of each composite sprocket 5, and the meshing point is moved accordingly. In order for the pre-meshing mechanism 170 to guide the pre-meshing and the track of the chain 6 from the outside, the input-side synchronization sprocket 173 and the synchronization chain 175 of the pre-meshing mechanism 170 are engaged with each other when the track of the chain 6 is changed. It is necessary to move along a trajectory (following trajectory) FO (see FIG. 1) following the movement of the point.

  For this reason, the support member 180 that supports the main part of the pre-meshing mechanism 170 can move along the tracking track FO through the slide member 183, and the support member 180 is moved along with the change of the track of the chain 6. A chain following movement mechanism 80 for moving along the following track FO is provided. The chain following movement mechanism 80 will be described later.

The slide member 183 is slidably supported by a guide rail 184 having a smooth outer periphery. The guide rail 184 is fixed to a wall 185 such as a casing of the speed change mechanism via a bracket 185a or the like, and here, two guide rails 184 parallel to each other are provided. In this example, each guide rail 184 has a cylindrical shape, and is arranged along the follower track FO, that is, parallel or substantially parallel to the follower track FO. The slide member 183 is provided with two slide hole portions 183a, and two guide rails 184 are inserted into the respective slide hole portions 183a. The slide member 183 follows the guide rail 184, that is, follows. It can slide along the track FO.
[1-5. Chain following movement mechanism)

As shown in FIGS. 9 and 10, the chain follower moving mechanism 80 includes a guide rail 184, a slide member 183, and a follower drive mechanism 200 that moves the slide member 183 along the guide rail 184.
Further, the follow-up drive mechanism 200 includes a follow-up cam that engages a cam roller 182b provided at the base end portion of the arm portion 182 of the support member 180 and a cam roller 182b that extends in a direction inclined with respect to the axial direction of the rotary shaft 1. An axial movement member 187 for chain follow movement that has a groove 188 and moves in the axial direction, and an axial drive mechanism for chain follow movement that drives this chain follow movement axial movement member 187 in the axial direction. Yes.

  When the axial movement member 187 for chain follow-up movement moves as shown by an arrow A1 in FIG. 9, the follow cam groove 188 moves, so that the cam roller 182b moves as shown by an arrow A2 in FIG. For example, in FIG. 9, when the axial movement member 187 for chain follow-up movement moves down, it moves to the left. In FIG. 9, the chain follow-up movement axial movement member 187 is indicated by a two-dot chain line for convenience.

  The cam roller 182b is mounted on the support member 180, and the support member 180 is slidable along the tracking track FO through the guide rail 184 and the slide member 183. Therefore, the input-side synchronization sprocket supported by the support member 180 and the support member 180. 173 and the synchronization chain 175 slide along the tracking track FO together with the cam roller 182b.

  Further, the axial drive mechanism for chain follow-up movement is designed so that the pinion sprocket 20 at the time of changing the gear ratio follows the travel trajectory of the chain 6 that is changed by changing the tangent radius of each composite sprocket 5 by radial movement. Since the side synchronization sprocket 173 and the synchronization chain 175 are moved, the sprocket moving axial drive mechanism 31 is also used in this embodiment.

  That is, as shown in FIG. 7, the coupling fork 35 d is provided for each composite sprocket 5 on the glasses fork 35, and the chain follow-up movement axial movement member 187 is coupled to each coupling arm 35 d. . Thus, the axial movement member 187 for chain follow-up movement is also moved in the axial direction simultaneously with the movement of the glasses fork 35 in order to change the speed ratio.

  Since the axial position of the glasses fork 35 corresponds to the gear ratio, the axial movement member 187 for chain follow-up movement also corresponds to the gear ratio. Further, the position of the meshing point and the track of the chain 6 also correspond to the gear ratio. Therefore, the chain follower movement axial movement member 187 is connected to the glasses fork 35 and the sprocket movement axial drive mechanism 31 is operated to move the chain follower movement axial movement member 187 along with the movement of the movable disk 19. Thus, the input-side synchronization sprocket 173 and the synchronization chain 175 can be moved along the change in the position of the meshing point and the trajectory of the chain 6.

[1-6. Phase shift allowable power transmission mechanism)
By the way, the phase alignment of the teeth 20c of the pinion sprocket 20 by the pre-meshing mechanism 170 cannot be realized unless the teeth 20c of the pinion sprocket 20 are movable in the phase alignment direction, that is, the rotation direction. However, if the teeth 20c of the pinion sprocket 20 are simply made movable in the rotational direction, the transmission of power between the pinion sprocket 20 and the chain 6 will be hindered.

That is, in the composite sprocket 5 on the input side, the pinion sprocket 20 revolves around the axis C ₁ of the rotating shaft 1 by the rotation of the rotating shaft 1, and the chain 6 is rotated along with this revolution. At this time, in order for power to be transmitted from the pinion sprocket 20 to the chain 6, it is necessary that the rotation of the pinion sprocket 20 is restricted. If the pinion sprocket 20 freely rotates during revolution, power is not transmitted from the pinion sprocket 20 to the chain 6.

  Therefore, the pinion sprocket 20 and the shaft 20a that supports the pinion sprocket 20 are formed separately, allowing the pinion sprocket 20 to rotate minutely with respect to the shaft 20a and neutralizing the pinion sprocket 20 with respect to the shaft 20a in the rotational direction. A phase shift allowable power transmission mechanism (also referred to herein as a micro-rotation allowance mechanism) 190 that biases the position and elastically restricts micro-rotation is provided.

  As shown in FIGS. 11 and 14, the phase shift allowable power transmission mechanism 190 according to the present embodiment is equipped to rotate integrally with the inner peripheral side of the pinion sprocket 20 and the inner peripheral side of the output side synchronization sprocket 176. A rotation permission mechanism 190A including a key member 191 and a key groove 192 that is formed on the outer peripheral side of the shaft 20a of the pinion sprocket 20 and engages the key member 191 with a certain range of play in the rotation direction, and the key member 191. Has a biasing member 193 for biasing the key member 191 from both the normal rotation direction and the reverse rotation direction to the reference phase position (centering position) so that the key groove 192 is positioned at the neutral position in the rotation direction of the key groove 192. And an urging mechanism 190B.

  As described above, the three pinion sprockets 20 are arranged in series corresponding to each chain 6A, 6B, 6C, and the pitch of each chain 6A, 6B, 6C is shifted from each other by 1/3 pitch. The teeth 20c of the pinion sprockets 20 arranged in the above are also arranged in a state shifted by 1/3 pitch correspondingly. The output-side synchronization sprocket 76 is also arranged at one end of the series pinion sprocket 20 in accordance with a predetermined phase with respect to each of the pinion sprockets 20.

In each pinion sprocket 20 and the output-side synchronization sprocket 176, a key groove 20d into which the key member 191 is fitted without a gap is formed on the peripheral surface of the hole through which the shaft 20a passes, and each pinion sprocket 20 has 1 as described above. The key member 191 passes through the key groove 20d of each pinion sprocket 20 and the output-side synchronization sprocket 176 at the same time with the phase shifted by / 3 pitches and the output-side synchronization sprocket 176 also in a predetermined phase state. As a result, the output-side synchronization sprocket 76 and each pinion sprocket 20 always rotate around the shaft centers C ₂ , C ₃ , C ₄ of the shaft 20a with the same phase relationship.

  A key groove 192 is formed on the outer periphery of the shaft 20a. Since the key groove 192 has a circumferential span larger than the width of the key member 191, the key member 191 is mounted in the key groove 192. When inserted, the key member 191 is movable in the key groove 192 by a gap d between the key member 191 and the inner wall surface of the key groove 192. The gap d is set in correspondence with the half teeth of the teeth 20c of the pinion sprocket 20. Accordingly, the output-side synchronization sprocket 176 and each pinion sprocket 20 that rotate integrally through the key member 191 and the key member 191 are rotatable by the half teeth of the teeth 20c with respect to the shaft 20a.

  However, a biasing member 193 is provided between the peripheral surface of the hole of the pinion sprocket 20 and the outer peripheral surface of the shaft 20a to bias the key member 191 to the key groove 192 in the circumferential neutral position. Unless the key is applied, the key member 191 is held in the circumferentially neutral position in the key groove 192. This urging member 193 is formed by stacking a plurality of C-shaped ring-shaped plates (C-shaped rings) whose annular portions are broken in the thickness direction, and the joints 193a and 193b of the broken portions are parallel or substantially parallel to each other. It is formed in a planar shape. The key member 191 is fitted between the facing joints 193a and 193b without a gap. The urging member 193 is made of an elastic material such as steel.

  The biasing member 193 has a semi-cylindrical recess 194b on the opposite side of the fractured portion where the joints 193a and 193b are located, that is, on an intermediate portion (an opposite side of 180 degrees) having the same central angle from the joints 193a and 193b. A semi-cylindrical recess 194a is also formed on the opposite side (180 degree opposite side) of the key groove 20d on the peripheral surface of the hole of the pinion sprocket 20 and the output side synchronization sprocket 76. The urging member 193 is interposed in a gap 195 formed between the inner peripheral wall 20w of the pinion sprocket 20 and the inner peripheral wall of the hole of the output side synchronization sprocket 176 and the outer peripheral wall 20aw of the shaft 20A. A pin (locking member) 194 is interposed in the cylindrical space formed by the recesses 194a and 194b. The pin 194 engages with the recesses 194a and 194b and is sandwiched between the inner peripheral wall 20w of the pinion sprocket 20 and the inner peripheral wall of the hole of the output side synchronization sprocket 176 and the outer peripheral wall 20aw of the shaft 20A.

  The urging member 193 is sandwiched between the outer peripheral surface of the pin 194 and the outer peripheral surface of the shaft 20a. When no external force is applied, the key member 191 is inserted into the key groove 92 as shown by a solid line in FIG. The state located in the circumferential neutral position is maintained. When an external force that rotates the pinion sprocket 20 is applied, the biasing member 193 is elastically deformed, and the pinion sprocket 20 is shown by a two-dot chain line in FIG. 14A or as shown in FIGS. 14C and 14D. Of the urging member 193 is in contact with the opposing surfaces 191a and 191b of the key member 191 so that the key member 191 is in the circumferential neutral position in the key groove 192. Such an elastic force is applied to the pinion sprocket 20. Of course, when the key member 191 contacts any one of the inner wall surfaces of the key groove 192, further rotation of the pinion sprocket 20 is completely restricted.

[2. Action and effect)
Since the continuously variable transmission mechanism according to one embodiment of the present invention is configured as described above, the following operations and effects can be obtained.

[2-1. Action and effect of pre-meshing mechanism with track guide)
When the pinion sprocket 20 revolves around the rotary shaft 1 and starts to engage with the chain 6, the pre-meshing mechanism 170 aligns the phases of the teeth 20c of the pinion sprocket 20 immediately before the meshing point.

  In other words, since the teeth 173a of the input-side synchronization sprocket 173 are always meshed with the teeth 63a outside the chain 6, the synchronization chain 175 supported on the shaft 171a together with the input-side synchronization sprocket 173 is also always connected to the chain 6 and teeth. Rotating in matched in-phase condition.

  When the pinion sprocket 20 reaches just before the meshing point, the output-side synchronization sprocket 176 meshes with the pseudo link groove 175c of the synchronization chain 175. The teeth 176a of the output-side synchronization sprocket 176 are sharper than the teeth 20c of the pinion sprocket 20, and the output-side synchronization sprocket 176 is placed in the pseudo link groove 175c even if there is a half-tooth phase shift. The teeth 176a easily bite.

  Since the synchronization chain 175 rotates in the same phase as the chain 6, when the output-side synchronization sprocket 176 also meshes with the synchronization chain 175, the phase of the chain 6 is synchronized. However, since the output-side synchronization sprocket 176 also meshes with the synchronization chain 175 with a slight phase difference, a phase difference is generated between the output-side synchronization sprocket 176 and the chain 6. Is slight.

  Therefore, the teeth 20c of the pinion sprocket 20 having a phase relationship (a constant phase difference) always corresponding to the output-side synchronization sprocket 176 is also phase-adjusted within a slight phase difference from the link groove 61c of the chain 6, and at the meshing point. The teeth 20c of the pinion sprocket 20 are surely engaged with the link groove 61c of the chain 6. As a result, the possibility that the teeth 20c of the pinion sprocket 20 hit the link plate 61 of the chain 6 and the tooth skips is eliminated, and the continuously variable transmission mechanism operates smoothly.

  In addition, the input-side synchronization sprocket 173 functions as a track guide that presses against the chain 6 from the outer peripheral side in the vicinity of the meshing point and guides the track of the chain 6 from the outside, so that the track of the chain 6 is slightly shifted inward. It is possible to suppress the runaway and detachment of the chain 6 and to guide the track of the chain 6 while suppressing a decrease in power transmission efficiency. Moreover, the chain trajectory is guided while the teeth of the pinion sprocket 20 are engaged with the chain 6 immediately before the meshing point where the force of the direction in which the chain tension becomes near the limit and the pinion sprocket 20 is released from the chain 6 is generated. Can be extremely effective.

[2-2. Action and effect of chain following movement mechanism)
Further, if the pinion sprocket 20 moves in the radial direction when the speed change ratio is changed and the diameter of the composite sprocket 5 is changed, the traveling track of the chain 6 changes and the position of the meshing point also changes. The moving mechanism 80 also moves the input-side synchronization sprocket 173 and the synchronization chain 175 of the pre-meshing mechanism 170 so as to follow the change in the travel trajectory of the chain 6, so that it is necessary to change the speed ratio before and after the change. Tooth alignment can be carried out without hindrance.

  Further, when the speed ratio is changed, the path of the chain 6 also changes. However, since the input-side synchronization sprocket 173 also moves along the tracking path FO following the change, Even after the change, the input-side synchronizing sprocket 173 can be pressed against the chain 6 from the outer peripheral side in the vicinity of the meshing point to guide the path of the chain 6 from the outside, and the runaway and separation of the chain 6 can be effectively suppressed.

  In addition, the chain follow-up movement mechanism 80 is configured to also serve as a part of the relative rotation drive mechanism 30, that is, the glasses fork 35 and the sprocket movement axial movement mechanism 31, which increases the number of parts and the cost. While suppressing the complication of the structure and surely following the change of the track of the chain 6, it is possible to perform pre-toothing and guide from the outside of the chain 6 track.

[2-3. Action and effect of phase shift allowable power transmission mechanism)
In addition, in order to phase the teeth 20c of the pinion sprocket 20 by the pre-meshing mechanism 170, the teeth 20c of the pinion sprocket 20 must be movable in the rotational direction, but if simply moved, the pinion sprocket 20 And the transmission of power between the chain 6 will be hindered. However, a phase shift allowable power transmission mechanism 190 that allows minute rotation of the pinion sprocket 20 with respect to the shaft 20a and urges the pinion sprocket 20 to a neutral position in the rotation direction with respect to the shaft 20a to elastically restrict minute rotation. Since it is equipped, the pinion sprocket 20 can be moved in the rotational direction while realizing the power transmission between the pinion sprocket 20 and the chain 6, and the tooth alignment can be realized. Further, since the urging member 193 of the urging mechanism 190B elastically restricts the relative rotation of the key member 191 with respect to the key groove 192, the impact when the teeth 20c of the pinion sprocket 20 are engaged with the chain 6 is also absorbed, and the engagement shock. Smoothly meshes without causing any problems.

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

  For example, in the above embodiment, the chain moving axial movement member 187 is provided integrally with the glasses fork (sprocket moving axial movement member) 35, and the chain tracking moving axial drive mechanism is connected to the sprocket moving axial drive mechanism. 31 and the chain follow-up movement mechanism 80 uses a part of the relative rotational drive mechanism 30. However, if attention is paid to the point that the input-side synchronization sprocket 173 functions as a follow-up guide, the chain follow-up movement mechanism 80 is Alternatively, it may be provided independently of the relative rotation drive mechanism 30 and separately from the relative rotation drive mechanism 30. In this case, the chain follower moving axial movement member 187 is made independent of the glasses fork 35 and moved by a drive mechanism different from the sprocket moving axial drive mechanism 31.

  Further, the chain follow-up movement mechanism 80 may be any mechanism that moves the pre-meshing mechanism 170, in particular, the first synchronous rotating member 171 in accordance with the change in the trajectory of the chain 6, as in the above embodiment. The cam structure is not limited to the cam structure in which the cam roller 182b is inserted into the cam groove 188. In this case, the pre-meshing mechanism 170 may be moved mechanically following the change in the trajectory of the chain 6, or the pre-meshing mechanism 170 may be moved mechanically following the change in the trajectory of the chain 6 under the control of the controller. Yes.

  The chain follower movement axial movement member 187 is provided integrally with the glasses fork (sprocket movement axial movement member) 35, and the chain follower movement axial drive mechanism is also used as the sprocket movement axial drive mechanism 31. If attention is paid to this point, the follow-up guide mechanism may be provided separately from the pre-meshing mechanism 170 (the input-side synchronization sprocket 173 of the first synchronization rotating member 171). In this case, the follow-up guide mechanism only needs to guide the track of the chain 6 from the outside, and guides the track of the chain 6 at a place different from the meshing point. Well, that is, the track of the chain 6 can be guided by slightly pressing the chain 6.

  Further, as a minute rotation allowance mechanism, a disc spring may be interposed between the pinion sprocket 20 and its support shaft 20a instead of the aforementioned phase shift allowance colleague transmission mechanism 190. This disc spring also restricts relative rotation while allowing minute rotation between the support shaft 20a and the pinion sprocket 20, so that the pinion sprocket 20 and the chain 6 that can be generated during the change of the transmission gear ratio are engaged. It is possible to absorb shocks.

DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Accommodating space 5 Compound sprocket 6, 6A-6C, 106, 106A-106C Chain 10 Fixed disk group 11 First fixed disk (fixed disk for radial movement)
11a Fixed radial groove for sprocket 11b Fixed radial groove for rod 12 Second fixed disk (fixed disk for rotation)
12a First guide groove (fixed pinion sprocket guide groove)
12b Second guide groove 12c Third guide groove 19 Movable disc (movable disc for radial movement)
19a Movable radial groove for sprocket 19b Movable radial groove for rod 19A Peripheral teeth 20 Pinion sprocket (gear)
20a Pinion sprocket shaft (gear shaft)
20c Pinion sprocket teeth 20w Inner peripheral wall of pinion sprocket (gear) 20aw Outer peripheral wall of pinion sprocket shaft (gear shaft) 21 Fixed pinion sprocket 21a Support shaft 22 First rotating pinion sprocket (advanced side rotating pinion sprocket)
22a Support shaft 23 Second rotation pinion sprocket (retarding side pinion sprocket)
23a Support shaft 29 Guide rod 29a Rod support shaft 29b Guide member 30 Relative rotation drive mechanism 31 Axial drive mechanism for sprocket movement 35 Glasses fork (Axial movement member for sprocket movement)
40A Sprocket moving mechanism 40B Rod moving mechanism 50 Mechanical rotation drive mechanism 51 First pinion (advance side pinion)
52 Second pinion (retarding pinion)
53 First rack (advanced side rack)
54 Second rack (retard side rack)
59 Guide member 61 Link plate (drive link)
61S Link plate row 61a Tooth portion of link plate 61 61b Pin hole 61c Link groove 62 Connecting pin 63 Auxiliary link 63S Auxiliary link row 63a Guide surface 63b Pin hole 64A, 64B Superposed portion 65a Thin portion 65b Notch portion 80 Chain following movement mechanism 90 Cam roller 170 Pre-meshing mechanism 171 First synchronous rotating member (trajectory guide mechanism)
171a Shaft of first synchronous rotating member 171 172 Second synchronous rotating member 172a Shaft of second synchronous rotating member 172 173 Input side synchronizing sprocket 173a Teeth of the input side synchronizing sprocket 173 173b Shaft of input side synchronizing sprocket 173 175 Synchronization chain 175a Pseudo link 175b Connecting pin 175c Pseudo link groove 176 Output side synchronization sprocket 176a Output side synchronization sprocket 76, 176 teeth 180 Support member 181 Bearing portion 182 Arm portion 182b Cam roller 187 Axis moving member for chain follow movement 188 Tracking cam groove 183 Slide member 186 Coil spring (spring member)
190 phase shift allowable power transmission mechanism 190A rotation allowable mechanism 190B urging mechanism 191 key member 192 key groove 193 urging member (C-shaped ring)
193a, 193b Energizing member 194 pin (locking member)
195 Clearance 200 Following drive mechanism C ₁ , C ₂ , C ₃ , C ₄ axis FO Follow track

Claims (9)

A rotating shaft to which power is input or output, a plurality of pinion sprockets supported so as to revolve in a radial direction and integrally with the rotating shaft, and the plurality of pinion sprockets are axially centered on the rotating shaft. Two composite sprockets having a sprocket moving mechanism that moves in synchronization with each other in the radial direction while maintaining an equal distance from each other, and a chain wound around the two composite sprockets, and the plurality of pinion sprockets A speed change mechanism that changes a gear ratio by changing a contact circle radius that surrounds any of the plurality of pinion sprockets and is in contact with any of the plurality of pinion sprockets,
A trajectory guide mechanism that presses against the chain from the outer periphery side and guides the trajectory of the chain;
A chain follow-up movement mechanism for moving the track guide mechanism along the track following the track change of the chain by changing the radius of the circle of contact,
The transmission mechanism according to claim 1, wherein the chain following movement mechanism is interlocked with the sprocket movement mechanism. Immediately before the pinion sprocket reaches a meshing point at which meshing with the chain is started by the revolution, a pre-meshing mechanism that phase-matches the teeth of the pinion sprocket with the link groove on the inner periphery of the chain,
A speed change mechanism, wherein a track guide mechanism is provided in the pre-meshing mechanism. The pre-meshing mechanism is engaged with the chain from the outer peripheral side and rotates in phase synchronization with the chain, and rotates in phase synchronization with the first synchronous rotation member and the meshing point. A second synchronous rotating member that engages with the pinion sprocket immediately before reaching the pinion sprocket to adjust the phase of the pinion sprocket,
The speed change mechanism according to claim 1, wherein the first synchronous rotating member functions as the trajectory guide. The first synchronous rotating member includes an input-side synchronization sprocket on the outer periphery of the chain where teeth are constantly meshed with the link groove,
The second synchronous rotating member is equipped with an output-side synchronous sprocket that rotates integrally with the pinion sprocket, and a pseudo-link that imitates the link groove of the chain. A synchronization rotator having a groove on the outer periphery, and the pseudo link groove meshes with the teeth of the output-side synchronization sprocket when the pinion sprocket reaches immediately before the engagement point. The transmission mechanism according to claim 3. A support member that rotatably supports the first synchronous rotation member and the second synchronous rotation member;
The speed change mechanism according to claim 4, wherein the chain following movement mechanism moves the support member along the following track. The chain following movement mechanism is
A guide rail extending along the following track,
A slide member that movably supports the support member and slides along the guide rail;
The speed change mechanism according to claim 5, further comprising a follow-up drive mechanism that moves the slide member along the guide rail. The support member includes a bearing portion that rotatably supports the input-side synchronization sprocket and the synchronization rotator, and an axial arm portion that extends in a pressure-contact direction to press-contact the input-side synchronization sprocket to the chain. With
The arm portion is movably supported in the axial direction by the slide member, urges the bearing portion in the press-contact direction between the arm portion and the slide member, and the input-side synchronization sprocket is connected to the chain. The speed change mechanism according to claim 6, further comprising a spring member that elastically presses the spring member. The following drive mechanism is
An axial moving member for chain follow-up movement that has a follow-up cam groove that extends in a direction inclined with respect to the axial direction of the rotary shaft and engages with a cam roller mounted on the support member, and moves in the axial direction;
An axial drive mechanism for chain follow movement for driving the chain follow movement axial movement member in the axial direction,
8. The slide member according to claim 6, wherein the slide member is slidably brought into contact with the follow cam groove and moves along the follow track with the movement of the chain follow movement axial movement member. Transmission mechanism. The sprocket moving mechanism is
A plurality of fixed radial grooves into which the support shafts of the plurality of pinion sprockets are inserted, and a fixed disk that rotates integrally with the rotation shaft;
A movable disk that is arranged so as to intersect with the fixed radial groove and that has a plurality of movable radial grooves in which the support shafts are respectively inserted is formed at the intersection, and is arranged concentrically with the fixed disk and is relatively rotatable. When,
A relative rotation drive mechanism for driving the movable disk relative to the fixed disk and moving the intersection in the radial direction;
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;
A groove for accommodating the one end of the cam roller, and an axial movement member for moving the sprocket that moves in the axial direction together with the cam roller;
A sprocket moving axial drive mechanism for moving the sprocket moving axial moving member in the axial direction,
The chain following movement axial movement member is provided integrally with the sprocket movement axial movement member, and the sprocket movement axial drive mechanism is also used as the chain following movement axial drive mechanism. The transmission mechanism according to claim 8.

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