JP5922304B2 - Speed change mechanism - Google Patents

Speed change mechanism Download PDF

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JP5922304B2
JP5922304B2 JP2015508121A JP2015508121A JP5922304B2 JP 5922304 B2 JP5922304 B2 JP 5922304B2 JP 2015508121 A JP2015508121 A JP 2015508121A JP 2015508121 A JP2015508121 A JP 2015508121A JP 5922304 B2 JP5922304 B2 JP 5922304B2
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axis
moving mechanism
roller
shaft
scissors
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JPWO2014156251A1 (en
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山田　篤
篤 山田
瀬川　俊明
俊明 瀬川
川口　健一
健一 川口
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JATCO Ltd
University of Tokyo NUC
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University of Tokyo NUC
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/08—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B is a disc with a flat or approximately flat friction surface
    • F16H15/10—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B is a disc with a flat or approximately flat friction surface in which the axes of the two members cross or intersect
    • F16H15/12—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B is a disc with a flat or approximately flat friction surface in which the axes of the two members cross or intersect in which one or each member is duplicated, e.g. for obtaining better transmission, for lessening the reaction forces on the bearings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Friction Gearing (AREA)

Description

本発明は、変速機構に関する。   The present invention relates to a transmission mechanism.

特許文献１には、同軸上で相対回転可能に設けられた２枚の円板の間にローラを設けた構成の変速機構が開示されている。
この変速機構では、円板の半径方向におけるローラの位置を変更することで、一方の円板に入力された回転が、ローラの位置の応じて決まる変速比で変速されて、ローラの回転軸から出力されるようになっている。Patent Document 1 discloses a speed change mechanism having a configuration in which a roller is provided between two discs that are provided on the same axis so as to be relatively rotatable.
In this speed change mechanism, by changing the position of the roller in the radial direction of the disk, the rotation input to one of the disks is shifted at a speed ratio determined according to the position of the roller, and from the rotation axis of the roller. It is output.

特開平０５−２６３８８８号公報Japanese Patent Laid-Open No. 05-263888

この変速機構では、トルクの伝達にひとつのローラのみを用いているので、伝達できるトルクを大きくするには、ローラの数を増やす必要がある。
しかし、ローラの数を増やすと、変速比を変更する際に、円板の半径方向における各ローラの位置を同期させつつ変更する必要があり、各ローラの位置を個別に制御して、各ローラを同期させつつ半径方向に移動させることが難しかった。In this speed change mechanism, only one roller is used for torque transmission. Therefore, in order to increase the torque that can be transmitted, it is necessary to increase the number of rollers.
However, when the number of rollers is increased, when changing the transmission ratio, it is necessary to change the position of each roller in the radial direction of the disk in synchronism with each other. It was difficult to move them radially while synchronizing them.

そこで、複数のローラの位置を同期させつつ変更できるようにすることが求められている。   Therefore, it is required to be able to change the positions of a plurality of rollers while synchronizing them.

本発明は、
入力側の回転軸と出力側の回転軸のうちの一方に設けられた円板部材と、
前記入力側の回転軸と前記出力側の回転軸のうちの他方の回転が伝達されて、前記回転軸の径方向に延びる軸線周りに回転する支持軸と、
前記軸線方向に移動可能、かつ前記支持軸と一体回転可能に前記支持軸に設けられたローラと、を備え、
前記入力側の回転軸と前記出力側の回転軸との間の回転の伝達を、前記円板部材に当接させたローラを介して行うように構成された変速機構であって、
前記支持軸を前記回転軸周りの周方向に複数設けると共に、
前記支持軸の各々に設けたローラに連結されて、前記ローラの各々を前記軸線方向に同期して移動させる移動機構と、
前記移動機構を駆動する駆動手段と、を設け、
前記移動機構は、
一対のリンク部材を長手方向における中間部で互いに連結して共通の回動軸周りに相対回転可能としたシザーズ部材を、前記回動軸が前記回転軸に平行となる向きで、前記回転軸周りの周方向に並べてリング状に配置すると共に、前記周方向で隣接するシザーズ部材を、互いのリンク部材の前記長手方向における一端側と他端側の連結部同士を相対回転可能に連結して構成され、
前記リンク部材の回動軸を、当該リンク部材の一端側の連結部と他端側の連結部とを結ぶ直線からオフセットした位置に設定した構成の変速機構とした。The present invention
A disk member provided on one of the input side rotary shaft and the output side rotary shaft;
The other rotation of the input-side rotation shaft and the output-side rotation shaft is transmitted, and a support shaft that rotates around an axis extending in the radial direction of the rotation shaft;
A roller provided on the support shaft so as to be movable in the axial direction and capable of rotating integrally with the support shaft;
A transmission mechanism configured to transmit rotation between the input-side rotation shaft and the output-side rotation shaft via a roller in contact with the disk member;
While providing a plurality of the support shafts in the circumferential direction around the rotation shaft,
A moving mechanism coupled to the rollers provided on each of the support shafts and moving each of the rollers in synchronization with the axial direction;
Driving means for driving the moving mechanism;
The moving mechanism is
A scissors member that connects a pair of link members to each other at an intermediate portion in the longitudinal direction so as to be relatively rotatable around a common rotation axis, with the rotation axis being parallel to the rotation axis and around the rotation axis. The scissors members adjacent to each other in the circumferential direction are connected to each other in the longitudinal direction so as to be relatively rotatable with each other in the longitudinal direction. And
A transmission mechanism having a configuration in which the rotation shaft of the link member is set at a position offset from a straight line connecting the connecting portion on one end side and the connecting portion on the other end side of the link member.

このように構成すると、移動機構において一対のリンク部材の交差角を変更すると、移動機構の周方向の長さが変化して、移動機構の外径が、交差角の変更方向に応じて拡縮する。この際、移動機構の外径は、回転軸の径方向に均等に拡縮するので、移動機構に連結されたローラの各々は、回転軸の径方向（支持軸の軸線方向）に同期しつつ移動する。よって、一対のリンク部材の交差角を変更することで、ローラの各々を、回転軸の回転中心を基準とした同心円上に位置させた状態で、径方向に進退移動させることができる。
これにより、ひとつの移動機構を用いて、複数のローラの径方向位置を同期させて変化させることができることになる。If comprised in this way, if the crossing angle of a pair of link member will be changed in a moving mechanism, the length of the circumferential direction of a moving mechanism will change, and the outer diameter of a moving mechanism will expand / contract according to the change direction of a crossing angle. . At this time, since the outer diameter of the moving mechanism is uniformly expanded and contracted in the radial direction of the rotating shaft, each of the rollers connected to the moving mechanism moves while synchronizing with the radial direction of the rotating shaft (the axial direction of the support shaft). To do. Therefore, by changing the crossing angle of the pair of link members, each of the rollers can be moved back and forth in the radial direction while being positioned on a concentric circle with the rotation center of the rotation shaft as a reference.
Thereby, the radial direction position of a some roller can be changed synchronously using one moving mechanism.

実施の形態にかかる変速機構の概略構成図である。It is a schematic block diagram of the speed change mechanism concerning an embodiment. 変速機構における移動機構とシザーズ部材を説明する図である。It is a figure explaining the moving mechanism and scissors member in a transmission mechanism. 移動機構の動作を説明する図である。It is a figure explaining operation | movement of a moving mechanism. 移動機構の動作を説明する図である。It is a figure explaining operation | movement of a moving mechanism. シザーズ部材と移動機構の変形例を説明する図である。It is a figure explaining the modification of a scissors member and a moving mechanism. シザーズ部材と移動機構の変形例を説明する図である。It is a figure explaining the modification of a scissors member and a moving mechanism.

以下、本発明にかかる変速機構実施形態を説明する。
図１は、実施の形態にかかる変速機構１の概略構成図であり、（ａ）は断面図、（ｂ）は、出力軸３側からガイドプレート４と移動機構８とを見た平面図である。なお、（ｂ）では、移動機構８を構成するシザーズ部材２０において、重ねられたリンク部材１０Ａ、１０Ｂを互いに区別できるようにするために、一方のリンク部材１０Ａを、ハッチングを付して示している。Embodiments of a transmission mechanism according to the present invention will be described below.
FIG. 1 is a schematic configuration diagram of a transmission mechanism 1 according to an embodiment, where (a) is a cross-sectional view, and (b) is a plan view of the guide plate 4 and the moving mechanism 8 viewed from the output shaft 3 side. is there. In (b), in order to be able to distinguish the overlapping link members 10A and 10B from each other in the scissors member 20 constituting the moving mechanism 8, one link member 10A is shown with hatching. Yes.

図１の（ａ）に示すように、変速機構１では、入力軸２と出力軸３とが、共通の軸線Ｘ上で同軸に配置されており、出力軸３の入力軸２側の端部には、軸方向から見て円形の円板部５が設けられている。円板部５は、軸線Ｘに対して直交して設けられており、この円板部５の入力軸２側の面５ａは、ローラＲが当接する当接面となっている。   As shown in FIG. 1A, in the speed change mechanism 1, the input shaft 2 and the output shaft 3 are arranged coaxially on a common axis X, and the end of the output shaft 3 on the input shaft 2 side. Is provided with a circular disc portion 5 as viewed from the axial direction. The disc portion 5 is provided orthogonal to the axis X, and the surface 5a on the input shaft 2 side of the disc portion 5 is an abutting surface with which the roller R abuts.

入力軸２は、ガイドプレート４の中央に設けられた貫通孔４１を貫通して設けられており、この入力軸２の出力軸３側の端部には、かさ歯車２１が設けられている。
かさ歯車２１は、入力軸２と一体に、軸線Ｘ周りに回転するようになっており、軸線Ｘに対して傾斜した歯面には、ロッド６のかさ歯車６１が噛合している。The input shaft 2 is provided through a through hole 41 provided in the center of the guide plate 4, and a bevel gear 21 is provided at the end of the input shaft 2 on the output shaft 3 side.
The bevel gear 21 rotates about the axis X integrally with the input shaft 2, and the bevel gear 61 of the rod 6 meshes with the tooth surface inclined with respect to the axis X.

図１の（ｂ）に示すように、ロッド６は、軸線Ｘに直交する軸線Ｙ（Ｙ１、Ｙ２）に沿って直線状に延びる棒状の部材であり、軸線Ｘ周りの周方向で、９０度間隔で４つ設けられている。
かさ歯車６１は、ロッド６の先端側（軸線Ｘ側）に固定されており、ロッド６と一体に、軸線Ｙ（Ｙ１、Ｙ２）周りに回転するようになっている。
そのため、入力軸２が軸線Ｘ周りに回転すると、入力軸２の回転が、かさ歯車２１、６１を介してロッド６に伝達されて、ロッド６が軸線Ｙ（Ｙ１、Ｙ２）周りに回転するようになっている。As shown in FIG. 1B, the rod 6 is a rod-like member extending linearly along an axis Y (Y1, Y2) orthogonal to the axis X, and is 90 degrees in the circumferential direction around the axis X. Four are provided at intervals.
The bevel gear 61 is fixed to the tip end side (axis X side) of the rod 6, and rotates around the axis Y (Y 1, Y 2) together with the rod 6.
Therefore, when the input shaft 2 rotates around the axis X, the rotation of the input shaft 2 is transmitted to the rod 6 via the bevel gears 21 and 61 so that the rod 6 rotates about the axis Y (Y1, Y2). It has become.

ロッド６の各々には、ローラＲが外挿して取り付けられている。
ローラＲの各々は、図示しないキー溝を介してロッド６に取り付けられており、ロッド６と一体に軸線Ｙ（Ｙ１、Ｙ２）周りに回転すると共に、ロッド６の長手方向（軸線Ｙ（Ｙ１、Ｙ２）の軸方向）に進退移動可能となっている。A roller R is attached to each rod 6 by extrapolation.
Each of the rollers R is attached to the rod 6 through a key groove (not shown), and rotates around the axis Y (Y1, Y2) integrally with the rod 6 and also the longitudinal direction of the rod 6 (axis Y (Y1, Y1, Y2)). Y2) axial direction) can be moved back and forth.

軸線Ｘの軸方向におけるロッド６とガイドプレート４との間には、ローラＲをロッド６の長手方向（軸線Ｘの径方向）に進退移動させるための移動機構８が、ガイドプレート４に載置された状態で設けられている。
この移動機構８には、ローラＲの各々が、連結部材７を介して揺動自在に連結されており、移動機構８に連結されたローラＲの各々は、軸線Ｘの軸方向から見て、軸線Ｘを中心とした同心円（図１の（ｂ）：仮想円Ｉｍ１参照）上に位置している。Between the rod 6 and the guide plate 4 in the axial direction of the axis X, a moving mechanism 8 for moving the roller R forward and backward in the longitudinal direction of the rod 6 (the radial direction of the axis X) is placed on the guide plate 4. It is provided in the state that was done.
Each of the rollers R is connected to the moving mechanism 8 in a swingable manner via a connecting member 7, and each of the rollers R connected to the moving mechanism 8 is viewed from the axial direction of the axis X, It is located on a concentric circle centered on the axis X (see (b) in FIG. 1: virtual circle Im1).

ローラＲの各々は、移動機構８により、ロッド６の長手方向に移動させられるようになっており、この際にローラＲの各々は、ロッド６の長手方向における位置が同じになるように同期して移動すると共に、軸線Ｘを中心とした同心円上に常に配置されるようになっている。   Each of the rollers R is moved in the longitudinal direction of the rod 6 by the moving mechanism 8. At this time, each of the rollers R is synchronized so that the positions in the longitudinal direction of the rod 6 are the same. And is always arranged on a concentric circle with the axis X as the center.

図１の（ａ）に示すように、ローラＲの各々には、出力軸３の先端に設けられた円板部５が、軸線Ｘの軸方向から当接している。
出力軸３には、スプリングＳｐが外挿して取り付けられており、このスプリングＳｐの一端は、円板部５の入力軸２とは反対側の面５ｂに当接しており、他端は、固定側部材Ｆｘに支持されている。
スプリングＳｐは、出力軸３の軸方向（軸線Ｘの軸方向）で圧縮された状態で設けられており、円板部５を、入力軸２側に付勢して、ローラＲに圧接させている。As shown in FIG. 1A, a disk portion 5 provided at the tip of the output shaft 3 is in contact with each roller R from the axial direction of the axis X.
A spring Sp is attached to the output shaft 3 by extrapolation. One end of the spring Sp is in contact with the surface 5b of the disc portion 5 opposite to the input shaft 2, and the other end is fixed. It is supported by the side member Fx.
The spring Sp is provided in a compressed state in the axial direction of the output shaft 3 (the axial direction of the axis X), and the disc portion 5 is urged toward the input shaft 2 to be brought into pressure contact with the roller R. Yes.

移動機構８について説明をする。
図２は、移動機構８を構成するシザーズ部材２０を説明する図であり、（ａ）は、シザーズ部材２０を構成するリンク部材１０を説明する図であり、（ｂ）は、リンク部材１０（１０Ａ、１０Ｂ）を連結して構成したシザーズ部材２０を説明する図であり、（ｃ）は、移動機構８を形成するために、軸線Ｘ周りの周方向に並べたシザーズ部材２０を互いに連結した状態を説明する図である。
なお、図２の（ｂ）、（ｃ）では、重ねられたリンク部材１０Ａ、１０Ｂを互いに区別できるようにするために、一方のリンク部材１０Ａを、ハッチングを付して示している。The moving mechanism 8 will be described.
2A and 2B are views for explaining the scissors member 20 constituting the moving mechanism 8, FIG. 2A is a view for explaining the link member 10 constituting the scissors member 20, and FIG. 10A and 10B) are diagrams for explaining the scissors member 20 configured by connecting the scissors members 20 arranged in the circumferential direction around the axis X to form the moving mechanism 8. FIG. It is a figure explaining a state.
In FIGS. 2B and 2C, one link member 10 </ b> A is shown with hatching so that the overlapped link members 10 </ b> A and 10 </ b> B can be distinguished from each other.

移動機構８は、２本のリンク部材１０（１０Ａ、１０Ｂ）を共通の回動軸Ｘｃ（連結部材１５）周りに相対回転可能に連結して構成されるシザーズ部材２０を、回動軸Ｘｃが入力軸２（軸線Ｘ）に対して平行となる向きで、入力軸２（軸線Ｘ）周りの周方向に並べてリング状に配置し、周方向で隣接するシザーズ部材２０を互いに連結して形成される。   The moving mechanism 8 includes a scissors member 20 configured by connecting two link members 10 (10A, 10B) so as to be relatively rotatable around a common rotation axis Xc (connection member 15). It is formed by connecting the scissors members 20 adjacent to each other in the circumferential direction, arranged in a ring shape in the direction parallel to the input shaft 2 (axis X), arranged in the circumferential direction around the input shaft 2 (axis X). The

図２の（ａ）に示すように、リンク部材１０の基部１１は、長手方向の全長Ｌａに亘って同じ厚みで形成された板状の部材であり、長手方向における一端部１１１と他端部１１２には、基部１１を厚み方向に貫通して貫通孔１３、貫通孔１４が設けられている。
基部１１の長手方向における中央には、膨出部１１３が設けられている。この膨出部１１３は、貫通孔１３の中心と貫通孔１４の中心とを結ぶ直線Ｌｍの直交方向に膨出しており、基部１１は、平面視において略三角形を有している。As shown to (a) of FIG. 2, the base 11 of the link member 10 is a plate-shaped member formed by the same thickness over the full length La of the longitudinal direction, and the one end part 111 and the other end part in a longitudinal direction A through hole 13 and a through hole 14 are provided at 112 through the base 11 in the thickness direction.
A bulging portion 113 is provided in the center of the base portion 11 in the longitudinal direction. The bulging portion 113 bulges in a direction orthogonal to a straight line Lm that connects the center of the through hole 13 and the center of the through hole 14, and the base portion 11 has a substantially triangular shape in plan view.

膨出部１１３にもまた、基部１１を厚み方向に貫通して貫通孔１２が設けられており、この貫通孔１２は、貫通孔１３の中心と貫通孔１４の中心とを結ぶ直線Ｌｍから、当該直線Ｌｍの直交方向にオフセットした位置に設けられている。   The bulging portion 113 is also provided with a through hole 12 that penetrates the base portion 11 in the thickness direction. The through hole 12 is formed from a straight line Lm that connects the center of the through hole 13 and the center of the through hole 14. It is provided at a position offset in the direction perpendicular to the straight line Lm.

ここで、貫通孔１２の中心を通り、前記した直線Ｌｍと直交する直線Ｌｍ２は、貫通孔１３と貫通孔１４の中間で直線Ｌｍと交差しており、この交点Ｐと貫通孔１３との離間距離Ｌｂと、交点Ｐと貫通孔１４との離間距離Ｌｂとが同じ長さとなっている。
さらに、リンク部材１０では、貫通孔１２と貫通孔１３との離間距離Ｌｃと、貫通孔１２と貫通孔１４との離間距離Ｌｃもまた、同じ長さとなっている。Here, a straight line Lm2 that passes through the center of the through hole 12 and is orthogonal to the straight line Lm described above intersects the straight line Lm in the middle of the through hole 13 and the through hole 14, and is separated from this intersection P and the through hole 13 The distance Lb and the distance Lb between the intersection P and the through hole 14 are the same length.
Furthermore, in the link member 10, the separation distance Lc between the through hole 12 and the through hole 13 and the separation distance Lc between the through hole 12 and the through hole 14 are also the same length.

実施の形態では、重ね合わせた２つのリンク部材１０（１０Ａ、１０Ｂ）を互いに連結してシザーズ部材２０を構成しており、シザーズ部材２０においてリンク部材１０（１０Ａ、１０Ｂ）は、貫通孔１２に挿入した連結部材１５で互いに相対回転可能に連結されている（図２の（ｂ）参照）。
この状態において、リンク部材１０Ａ、１０Ｂは、貫通孔１２の中心を通る共通の回動軸Ｘｃ周りに相対回転可能となっており、シザーズ部材２０は、回動軸Ｘｃの軸方向から見て紙面手前側に位置するリンク部材１０Ａと紙面奥側に位置するリンク部材１０Ｂとを交差させた状態で、移動機構８に組み込まれている。In the embodiment, the two linked link members 10 (10A, 10B) are connected to each other to form the scissors member 20. In the scissors member 20, the link members 10 (10A, 10B) are formed in the through holes 12. The inserted connecting members 15 are connected so as to be rotatable relative to each other (see FIG. 2B).
In this state, the link members 10 </ b> A and 10 </ b> B are relatively rotatable around a common rotation axis Xc passing through the center of the through hole 12, and the scissors member 20 is a paper surface as viewed from the axial direction of the rotation axis Xc. The link member 10 </ b> A located on the near side and the link member 10 </ b> B located on the back side of the drawing are crossed and incorporated in the moving mechanism 8.

図２の（ｃ）に示すように、移動機構８においてシザーズ部材２０は、入力軸２（軸線Ｘ）の軸線方向から見て、リンク部材１０Ａの一端部１１１Ａとリンク部材１０Ｂの他端部１１２Ｂとを内径側に、リンク部材１０Ａの他端部１１２Ａとリンク部材１０Ｂの一端部１１１Ｂとを外径側に、それぞれ配置させた向きで、入力軸２（軸線Ｘ）周りの周方向に並べられている。この状態において各シザーズ部材２０は、リンク部材１０Ａ、１０Ｂの回動軸Ｘｃを、入力軸２（軸線Ｘａ）に対して平行に位置させている。
さらに、各シザーズ部材２０においてリンク部材１０Ａとリンク部材１０Ｂは、貫通孔１３の中心と貫通孔１４の中心とを結ぶ直線ＬｍＡと、貫通孔１３の中心と貫通孔１４の中心とを結ぶ直線ＬｍＢとを交差させて設けられている。この状態において、各リンク部材１０Ａは、その膨出部１１３を、軸線Ｘまわりの周方向で時計回り方向における下流側向けて配置されており、各リンク部材１０Ｂは、その膨出部１１３を、軸線Ｘまわりの周方向で反時計回り方向における下流側に向けて配置されている。As shown in FIG. 2 (c), in the moving mechanism 8, the scissors member 20 is seen from the axial direction of the input shaft 2 (axis X), and the one end 111A of the link member 10A and the other end 112B of the link member 10B. Are arranged in the circumferential direction around the input shaft 2 (axis X) with the other end 112A of the link member 10A and the one end 111B of the link member 10B arranged on the outer diameter side. ing. In this state, each scissors member 20 positions the rotation axis Xc of the link members 10A and 10B in parallel to the input shaft 2 (axis line Xa).
Further, in each scissors member 20, the link member 10 </ b> A and the link member 10 </ b> B are a straight line LmA that connects the center of the through hole 13 and the center of the through hole 14, and a straight line LmB that connects the center of the through hole 13 and the center of the through hole 14. And is provided to cross. In this state, each link member 10A is arranged with its bulging portion 113 facing downstream in the clockwise direction in the circumferential direction around the axis X, and each link member 10B It is arranged toward the downstream side in the counterclockwise direction in the circumferential direction around the axis X.

移動機構８においてシザーズ部材２０の各々は、リンク部材１０Ａの一端部１１１Ａおよび他端部１１２Ａを、周方向で隣接する他のシザーズ部材２０のリンク部材１０Ｂの他端部１１２Ｂおよび一端部１１１Ｂに重ねた状態で設けられており、重ねられたリンク部材１０Ａの一端部１１１Ａおよび他端部１１２Ａと、リンク部材１０Ｂの他端部１１２Ｂおよび一端部１１１Ｂは、貫通孔１３、１４に挿入した連結部材１６、１７により、回動軸Ｘｃに対して略平行な回動軸Ｘｄ（連結軸）周りに相対回転可能に連結されている。   In the moving mechanism 8, each of the scissors members 20 overlaps one end 111A and the other end 112A of the link member 10A with the other end 112B and one end 111B of the link member 10B of another scissors member 20 adjacent in the circumferential direction. The one end 111A and the other end 112A of the link member 10A, and the other end 112B and the one end 111B of the link member 10B are connected to the connecting member 16 inserted into the through holes 13 and 14, respectively. , 17 are connected so as to be relatively rotatable about a rotation axis Xd (connection axis) substantially parallel to the rotation axis Xc.

ここで、軸線Ｘの軸方向から移動機構８を見ると、周方向で隣接するシザーズ部材２０の各々は、リンク部材１０Ａ、１０Ｂの中央の連結点（連結部材１５）を、軸線Ｘを中心とする同心円（仮想円Ｉｍ２）上に位置させると共に、内径側の連結点（連結部材１６）と、外径側の連結点（連結部材１７）を、それぞれ軸線Ｘを中心とする同心円（仮想円Ｉｍ１、Ｉｍ３）上に位置させている。   Here, when the moving mechanism 8 is viewed from the axial direction of the axis X, each of the scissors members 20 adjacent in the circumferential direction has a central connection point (connecting member 15) of the link members 10A and 10B as a center. The concentric circle (virtual circle Im2) and the concentric circle (virtual circle Im1) centering on the axis X are respectively connected to the connecting point (connecting member 16) on the inner diameter side and the connecting point (connecting member 17) on the outer diameter side. , Im3).

シザーズ部材２０では、リンク部材１０Ａ、１０Ｂの交差角θ（軸線Ｘの径方向における交差角θ）が大きくなると、周方向で隣接するシザーズ部材２０の外径側の連結点（連結部材１７）の離間距離Ｒａと、内径側の連結点（連結部材１６）の軸線Ｘ周りの周方向における、離間距離Ｒｂがそれぞれ大きくなる（図２の（ｃ）参照）。
そのため、交差角θが大きくなると、軸線Ｘ周りの周方向における移動機構８の長さが長くなって、移動機構８の外径（直径）が大きくなるようになっている。In the scissors member 20, when the crossing angle θ (the crossing angle θ in the radial direction of the axis X) of the link members 10A and 10B increases, the connecting point (the connecting member 17) on the outer diameter side of the scissors member 20 adjacent in the circumferential direction. The separation distance Ra and the separation distance Rb in the circumferential direction around the axis X of the connection point (connection member 16) on the inner diameter side increase (see (c) in FIG. 2).
Therefore, when the crossing angle θ increases, the length of the moving mechanism 8 in the circumferential direction around the axis X increases, and the outer diameter (diameter) of the moving mechanism 8 increases.

また、リンク部材１０Ａ、１０Ｂの交差角θ（軸線Ｘの径方向における交差角θ）が小さくなると、軸線Ｘ周りの周方向における移動機構８の長さが短くなって、移動機構８の外径（直径）が小さくなるようになっている。   Further, when the crossing angle θ of the link members 10A and 10B (crossing angle θ in the radial direction of the axis X) is reduced, the length of the moving mechanism 8 in the circumferential direction around the axis X is reduced, and the outer diameter of the moving mechanism 8 is reduced. (Diameter) becomes smaller.

この際、シザーズ部材２０の外径側の連結点（連結部材１７）と、内径側の連結点（連結部材１６）は、軸線Ｘから径方向に延びる直線Ｌｒ上を、リンク部材１０Ａ、１０Ｂの交差角θの変化方向に応じて決まる一方向に移動するようになっている。   At this time, the connecting point (connecting member 17) on the outer diameter side of the scissors member 20 and the connecting point (connecting member 16) on the inner diameter side of the link members 10A and 10B are on the straight line Lr extending in the radial direction from the axis X. It moves in one direction determined according to the changing direction of the crossing angle θ.

実施の形態では、図１に示すように、移動機構８の内径側の連結点（連結部材１６）のうちの４箇所に、連結部材７を介してローラＲが連結されている。
そのため、移動機構８の外径の拡縮により、移動機構８の内径側の連結点（連結部材１６）が直線Ｌｒ上を進退移動すると、ローラＲの各々が、この進退移動に連動して軸線Ｘの径方向（軸線Ｙ（Ｙ１、Ｙ２）方向）に進退移動するようになっている。In the embodiment, as shown in FIG. 1, the roller R is connected to the four positions among the connecting points (connecting member 16) on the inner diameter side of the moving mechanism 8 via the connecting member 7.
Therefore, when the connecting point (connecting member 16) on the inner diameter side of the moving mechanism 8 moves forward / backward on the straight line Lr due to the expansion / contraction of the outer diameter of the moving mechanism 8, each roller R moves along the axis X in conjunction with this forward / backward movement. In the radial direction (axis Y (Y1, Y2) direction).

ここで、ローラＲの連結部材７が連結された連結部材１６Ａは、軸方向の長さが、他の連結部材１６よりも長くなっており、連結部材７とは反対側の端部を、ガイドプレート４に載置に設けたガイド溝４３に挿入させている。
このガイド溝４３は、軸線Ｘの径方向に、軸線Ｙ（Ｙ１，Ｙ２）に沿って直線状に設けられており、ローラＲの各々が、移動機構８により軸線Ｘの径方向（円板部５の半径方向）に進退移動する際に、連結部材１６Ａがガイド溝４３に沿って移動することで、ローラＲを、軸線Ｙ（Ｙ１、Ｙ２）に沿って正確に進退移動させることができるようになっている。Here, the connecting member 16 </ b> A to which the connecting member 7 of the roller R is connected has an axial length longer than that of the other connecting members 16, and the end on the side opposite to the connecting member 7 is guided. It is inserted into a guide groove 43 provided on the plate 4.
The guide groove 43 is linearly provided along the axis Y (Y1, Y2) in the radial direction of the axis X, and each roller R is moved by the moving mechanism 8 in the radial direction (disk portion). When the connecting member 16A moves along the guide groove 43 when moving forward and backward in the radial direction of 5), the roller R can be moved forward and backward accurately along the axis Y (Y1, Y2). It has become.

図１の（ａ）に示すように、シザーズ部材２０の外径側の連結点（連結部材１７）のうちの１つ（連結部材１７Ａ）は、他の連結部材１７よりも軸方向の長さが長くなっている。この連結部材１７Ａは、ガイドプレート４に設けられたスリット４２を貫通しており、その先端部は、軸線Ｘの径方向に延びる連結棒９１の一端に、揺動自在に連結されている。ここで、連結棒９１は、アクチュエータ９０により、軸線Ｘの径方向（軸線Ｙ２方向）に進退移動するようになっており、連結棒９１が軸線Ｙ２方向に進退移動すると、シザーズ部材２０の外径側の連結点（連結部材１７Ａ）が、軸線Ｙ２方向に進退移動するようになっている。   As shown in FIG. 1A, one of the connection points (connection member 17) on the outer diameter side of the scissors member 20 (connection member 17 </ b> A) is longer in the axial direction than the other connection members 17. Is getting longer. The connecting member 17A passes through a slit 42 provided in the guide plate 4, and a tip end of the connecting member 17A is swingably connected to one end of a connecting rod 91 extending in the radial direction of the axis X. Here, the connecting rod 91 is moved forward and backward in the radial direction of the axis X (axis Y2 direction) by the actuator 90. When the connecting rod 91 moves back and forth in the direction of the axis Y2, the outer diameter of the scissors member 20 is increased. The connecting point (connecting member 17A) on the side moves forward and backward in the direction of the axis Y2.

ここで、移動機構８は、一対のリンク部材１０（１０Ａ、１０Ｂ）を相対回転可能に連結して構成されるシザーズ部材２０を、互いのリンク部材１０（１０Ａ、１０Ｂ）の端部同士を相対回転可能に連結して構成されている。
そのため、移動機構８を構成するシザーズ部材２０のうちの１つのシザーズ部材２０において、リンク部材１０Ａ、１０Ｂの交差角を変更すると、残りのシザーズ部材２０におけるリンク部材１０Ａ、１０Ｂの交差角もまた、変更されるようになっている。Here, the moving mechanism 8 has a pair of link members 10 (10A, 10B) connected to each other so that they can rotate relative to each other, and the end portions of the link members 10 (10A, 10B) are relative to each other. It is configured to be rotatably connected.
Therefore, when the crossing angle of the link members 10A and 10B is changed in one scissors member 20 among the scissors members 20 constituting the moving mechanism 8, the crossing angles of the link members 10A and 10B in the remaining scissors member 20 are also changed. It has been changed.

実施の形態では、周方向で隣接するリンク部材１０の外径側の連結点（連結部材１７）のうちの１つの連結点（連結部材１７Ａ）の位置を、アクチュエータ９０により、軸線Ｘの径方向に移動させて、連結点（連結部材１７Ａ）の両側に位置するシザーズ部材２０におけるリンク部材１０Ａ、１０Ｂの交差角を変更することで、移動機構８を構成する総てのシザーズ部材２０におけるリンク部材１０Ａ、１０Ｂの交差角を変更して、移動機構８の外径を拡縮するようになっている。   In the embodiment, the position of one connecting point (connecting member 17A) among the connecting points (connecting member 17) on the outer diameter side of the link members 10 adjacent in the circumferential direction is changed by the actuator 90 in the radial direction of the axis X. The link members in all scissors members 20 constituting the moving mechanism 8 are changed by changing the crossing angles of the link members 10A and 10B in the scissors members 20 located on both sides of the connection point (connection member 17A). By changing the crossing angle of 10A and 10B, the outer diameter of the moving mechanism 8 is expanded or reduced.

移動機構８の動作を説明する。
図３および図４は、移動機構８の動作を説明する図である。
図３の（ａ）は、出力軸３側からガイドプレート４と移動機構８とを見た平面図であって、移動機構８が最小の外径となった状態を示す図であり、（ｂ）は、（ａ）における移動機構８の一部を拡大した図である。
図３の（ｃ）は、出力軸３側からガイドプレート４と移動機構８とを見た平面図であって、移動機構８が図３の（ａ）よりも大きい外径となった状態を示す図であり、（ｄ）は、（ｃ）における移動機構８の一部を拡大した図である。
図４の（ａ）は、出力軸３側からガイドプレート４と移動機構８とを見た平面図であって、移動機構８が図３の（ｃ）よりも大きい外径となった状態を示す図であり、（ｂ）は、（ａ）における移動機構８の一部を拡大した図である。
なお、図３および図４では、重ねられたリンク部材１０Ａ、１０Ｂを互いに区別できるようにするために、一方のリンク部材１０Ａを、ハッチングを付して示している。The operation of the moving mechanism 8 will be described.
3 and 4 are diagrams for explaining the operation of the moving mechanism 8.
FIG. 3A is a plan view of the guide plate 4 and the moving mechanism 8 viewed from the output shaft 3 side, and shows a state in which the moving mechanism 8 has a minimum outer diameter. () Is the figure which expanded a part of moving mechanism 8 in (a).
FIG. 3C is a plan view of the guide plate 4 and the moving mechanism 8 viewed from the output shaft 3 side, and shows a state in which the moving mechanism 8 has an outer diameter larger than that of FIG. It is a figure shown, (d) is the figure which expanded a part of the moving mechanism 8 in (c).
4A is a plan view of the guide plate 4 and the moving mechanism 8 viewed from the output shaft 3 side, and shows a state in which the moving mechanism 8 has an outer diameter larger than that of FIG. It is a figure shown, (b) is the figure which expanded a part of the moving mechanism 8 in (a).
In FIGS. 3 and 4, one link member 10 </ b> A is shown with hatching so that the overlapped link members 10 </ b> A and 10 </ b> B can be distinguished from each other.

図３の（ａ）、（ｂ）に示す状態では、リンク部材１０Ａ、１０Ｂの交差角θは、リンク部材１０Ａ、１０Ｂの内径側の連結点（連結部材１６）を、軸線Ｘを中心とした同心円（仮想円Ｉｍ１）上に位置させる交差角となっている。
そのため、連結部材１６に連結されたローラＲは、軸線Ｘの近傍に位置すると共に、出力軸３側の円板部５の内径側に当接している。In the state shown in FIGS. 3A and 3B, the crossing angle θ of the link members 10A and 10B is centered on the axis X at the connection point (connection member 16) on the inner diameter side of the link members 10A and 10B. The crossing angle is positioned on a concentric circle (virtual circle Im1).
Therefore, the roller R coupled to the coupling member 16 is positioned in the vicinity of the axis X and is in contact with the inner diameter side of the disk portion 5 on the output shaft 3 side.

この状態から、外径側の連結点（連結部材１７Ａ）の位置を、移動機構８の外径が大きくなる方向（図中矢印ａ参照）に、アクチュエータ９０を駆動して移動させると、リンク部材１０Ａ、１０Ｂは、互いの交差角θが大きくなる方向（図中矢印ａ参照）に、互いの連結点（連結部材１５）周りに回動する。
そうすると、リンク部材１０Ａ、１０Ｂの内径側の連結点（連結部材１６）と外径側の連結点（連結部材１７）の位置が、軸線Ｘの径方向に延びる直線Ｌｒに沿って径方向外側に移動して、移動機構８の軸線Ｘ周りの周方向の長さが長くなるので、移動機構８の外径は、図３の（ｃ）、（ｄ）に示す形状まで拡大する。From this state, when the actuator 90 is driven and moved in the direction in which the outer diameter of the moving mechanism 8 increases (see arrow a in the figure), the position of the connecting point (connecting member 17A) on the outer diameter side becomes a link member. 10A and 10B rotate around the connection point (connection member 15) in the direction in which the crossing angle θ increases (see arrow a in the figure).
Then, the positions of the connecting points (connecting member 16) on the inner diameter side and the connecting points (connecting member 17) on the outer diameter side of the link members 10A and 10B are radially outward along the straight line Lr extending in the radial direction of the axis X. Since it moves and the circumferential length around the axis X of the moving mechanism 8 becomes longer, the outer diameter of the moving mechanism 8 expands to the shapes shown in FIGS.

この場合、リンク部材１０Ａ、１０Ｂの交差角θが、θ１からθ２まで大きくなることで、軸線Ｘから連結部材１６までの半径は、ｒ１からｒ２まで拡径し、軸線Ｘから連結部材１７までの半径は、Ｒ１からＲ２まで拡径している。
これにより、ローラＲの円板部５との当接位置が、円板部５の半径方向における外側に移動して、軸線Ｙ（Ｙ１、Ｙ２）の軸方向で軸線Ｘを挟んで対称に配置されたローラＲの離間距離Ｌは、Ｌ１からＬ２に拡大している。In this case, when the crossing angle θ of the link members 10A and 10B increases from θ1 to θ2, the radius from the axis X to the connecting member 16 increases from r1 to r2, and from the axis X to the connecting member 17 The radius is increased from R1 to R2.
Thereby, the contact position of the roller R with the disk part 5 moves outward in the radial direction of the disk part 5, and is arranged symmetrically with the axis X in the axial direction of the axis Y (Y1, Y2). The separation distance L of the roller R is increased from L1 to L2.

なお、移動機構８が拡径する際に、内径側の連結部材１６の各々の位置が直線Ｌｒに沿って同期した状態で径方向外側に移動するので、内径側の連結部材１６連結されたローラＲの各々の位置も、同期した状態で径方向外側に移動することになる。よって、移動機構８が拡径する際に、ローラＲの各々は、軸線Ｘを中心とした同心円上に常に位置した状態で、移動することになる。   In addition, when the moving mechanism 8 expands the diameter, each position of the connecting member 16 on the inner diameter side moves radially outward in a synchronized state along the straight line Lr. Therefore, the roller connected to the connecting member 16 on the inner diameter side. Each position of R also moves radially outward in a synchronized state. Therefore, when the moving mechanism 8 expands in diameter, each of the rollers R moves while being always located on a concentric circle with the axis X as the center.

この状態から、外径側の連結点（連結部材１７Ａ）の位置を、移動機構８の外径がさらに大きくなる方向（図中矢印ａ１参照）に移動すると、リンク部材１０Ａ、１０Ｂは、互いの交差角θがさらに大きくなる方向（図中矢印ａ１参照）に、互いの連結点（連結部材１５）周りに回動する
そうすると、リンク部材１０Ａ、１０Ｂの内径側の連結点（連結部材１６）と外径側の連結点（連結部材１７）の位置が、軸線Ｘの径方向に延びる直線Ｌｒに沿って径方向外側にさらに移動して、移動機構８の軸線Ｘ周りの周方向の長さが長くなるので、移動機構８の外径は、図４の（ａ）、（ｂ）に示す形状まで外径が拡大する。From this state, when the position of the connecting point (connecting member 17A) on the outer diameter side is moved in the direction in which the outer diameter of the moving mechanism 8 is further increased (see arrow a1 in the figure), the link members 10A and 10B are In the direction in which the crossing angle θ further increases (see the arrow a1 in the figure), it rotates around the connection point (connection member 15). Then, the connection point (connection member 16) on the inner diameter side of the link members 10A and 10B The position of the connection point (connection member 17) on the outer diameter side is further moved radially outward along the straight line Lr extending in the radial direction of the axis X, and the circumferential length around the axis X of the moving mechanism 8 is increased. Since it becomes long, the outer diameter of the moving mechanism 8 is expanded to the shapes shown in FIGS. 4 (a) and 4 (b).

この場合、リンク部材１０Ａ、１０Ｂの交差角θが、θ２からθ３まで大きくなることで、軸線Ｘから連結部材１６までの半径は、ｒ２からｒ３まで拡径し、軸線Ｘから連結部材１７までの半径は、Ｒ２からＲ３まで拡径している。
これにより、ローラＲの円板部５との当接位置が、円板部５の半径方向における外側に移動して、軸線Ｙ（Ｙ１、Ｙ２）の軸方向で軸線Ｘを挟んで対称に配置されたローラＲの離間距離Ｌは、Ｌ２からＬ３に拡大している。In this case, when the crossing angle θ of the link members 10A and 10B increases from θ2 to θ3, the radius from the axis X to the connecting member 16 increases from r2 to r3, and from the axis X to the connecting member 17 The radius is increased from R2 to R3.
Thereby, the contact position of the roller R with the disk part 5 moves outward in the radial direction of the disk part 5, and is arranged symmetrically with the axis X in the axial direction of the axis Y (Y1, Y2). The separation distance L of the roller R is increased from L2 to L3.

逆に、図３の（ｃ）、（ｄ）に示す状態から、外径側の連結点（連結部材１７Ａ）の位置を、移動機構８の外径が小さくなる方向（図中矢印ｂ１参照）に移動すると、リンク部材１０Ａ、１０Ｂは、互いの交差角θが小さくなる方向に、互いの連結点（連結部材１５）周りに回動する（図中矢印ｂ１参照）
そうすると、リンク部材１０Ａ、１０Ｂの内径側の連結点（連結部材１６）と外径側の連結点（連結部材１７）の位置が、軸線Ｘの径方向に延びる直線Ｌｒに沿って径方向内側に移動して、移動機構８の軸線Ｘ周りの周方向の長さが短くなるので、移動機構８は、図３の（ａ）、（ｂ）に示す形状まで外径が縮小する。Conversely, from the state shown in FIGS. 3C and 3D, the position of the outer diameter side connecting point (the connecting member 17A) is changed in the direction in which the outer diameter of the moving mechanism 8 decreases (see arrow b1 in the figure). The link members 10A and 10B rotate around the connection point (connection member 15) in the direction in which the cross angle θ decreases (see arrow b1 in the figure).
Then, the positions of the connection points (connection member 16) on the inner diameter side and the connection points (connection member 17) on the outer diameter side of the link members 10A and 10B are radially inward along the straight line Lr extending in the radial direction of the axis X. Since it moves and the circumferential length around the axis X of the moving mechanism 8 is shortened, the outer diameter of the moving mechanism 8 is reduced to the shape shown in FIGS.

この場合、リンク部材１０Ａ、１０Ｂの交差角θが、θ２からθ１まで小さくなることで、軸線Ｘから連結部材１６までの半径は、ｒ２からｒ１まで縮径し、軸線Ｘから連結部材１７までの半径は、Ｒ２からＲ１まで縮径している。
これにより、ローラＲの円板部５との当接位置が、円板部５の半径方向における内側に移動して、軸線Ｙ（Ｙ１、Ｙ２）の軸方向で軸線Ｘを挟んで対称に配置されたローラＲの離間距離Ｌは、Ｌ２からＬ１に狭まっている。In this case, the crossing angle θ of the link members 10A and 10B decreases from θ2 to θ1, so that the radius from the axis X to the connecting member 16 is reduced from r2 to r1, and from the axis X to the connecting member 17 The radius is reduced from R2 to R1.
Thereby, the contact position of the roller R with the disk part 5 moves inward in the radial direction of the disk part 5, and is arranged symmetrically with the axis X in the axial direction of the axis Y (Y1, Y2). The separation distance L of the roller R is narrowed from L2 to L1.

なお、移動機構８が縮径する際にもまた、内径側の連結部材１６の各々の位置が直線Ｌｒに沿って同期した状態で径方向内側に移動するので、内径側の連結部材１６連結されたローラＲの各々の位置も、同期した状態で径方向内側に移動することになる。よって、移動機構８が縮径する際にも、ローラＲの各々は、軸線Ｘを中心とした同心円上に常に位置した状態で、移動することになる。
また、上記した移動機構８の外径が小さくなる場合の挙動は、移動機構８が、図４の（ａ）、（ｂ）に示す状態から、縮径する場合も同様であるが、ここでは、その説明を省略する。Even when the diameter of the moving mechanism 8 is reduced, each position of the connecting member 16 on the inner diameter side moves radially inward along the straight line Lr, so that the connecting member 16 on the inner diameter side is connected. Each position of the roller R also moves radially inward in a synchronized state. Therefore, even when the moving mechanism 8 is reduced in diameter, each of the rollers R moves while being always located on a concentric circle with the axis X as the center.
Further, the behavior when the outer diameter of the moving mechanism 8 is reduced is the same when the moving mechanism 8 is reduced in diameter from the state shown in FIGS. 4 (a) and 4 (b). The description is omitted.

このように、軸線Ｘ周りの周方向にリング状に配置したシザーズ部材２０を連結して構成された移動機構８に、軸線Ｘ周りの周方向に複数設けられたローラＲを支持させることで、ローラＲの各々を、軸線Ｘの径方向に同期させつつ移動させることができる。   In this way, by supporting the plurality of rollers R provided in the circumferential direction around the axis X on the moving mechanism 8 configured by connecting the scissors members 20 arranged in a ring shape in the circumferential direction around the axis X, Each of the rollers R can be moved while being synchronized with the radial direction of the axis X.

以上の通り、実施の形態では、
入力軸２（入力側の回転軸）と出力軸３（出力側の回転軸）とが、共通の軸線Ｘ上で同軸に設けられており、出力軸３に設けられた円板部５（円板部材）と、入力軸２の回転が伝達されて、入力軸２（軸線Ｘ）の径方向に延びる軸線Ｙ（Ｙ１、Ｙ２）周りに回転するロッド６（支持軸）と、ロッド６において軸線Ｙ（Ｙ１、Ｙ２）方向に移動可能、かつロッド６と一体回転可能に設けられたローラＲと、を備え、入力軸２と出力軸３との間の回転の伝達を、円板部５に当接させたローラＲを介して行うように構成された変速機構１であって、
ロッド６を軸線Ｘ周りの周方向に９０度間隔で４つ設けると共に、
ロッド６の各々に設けられたローラＲに連結されて、ローラＲの各々を軸線Ｙ（Ｙ１、Ｙ２）方向に同期して移動させる移動機構８と、移動機構８を駆動する駆動手段９と、を設け、
移動機構８は、
一対のリンク部材１０（１０Ａ、１０Ｂ）を長手方向の中間部で互いに連結して共通の回動軸Ｘｃ周りに相対回転可能としたシザーズ部材２０を、回動軸Ｘｃが軸線Ｘに平行となる向きで、軸線Ｘ周りの周方向に並べてリング状に配置すると共に、周方向で隣接するシザーズ部材２０を、互いのリンク部材１０（１０Ａ、１０Ｂ）の端部同士（一端部１１１Ａおよび他端部１１２Ｂ、他端部１１２Ａおよび一端部１１１Ｂ）を相対回転可能に連結して形成して構成され、
リンク部材１０の回動軸Ｘｃを、リンク部材１０（１０Ａ、１０Ｂ）の内径側の連結点（連結部材１６）と外径側の連結点（連結部材１７）を結ぶ直線Ｌｍからオフセットした位置に設定した構成の変速機構１とした。As described above, in the embodiment,
An input shaft 2 (input-side rotation shaft) and an output shaft 3 (output-side rotation shaft) are provided coaxially on a common axis X, and a disk portion 5 (circle) provided on the output shaft 3 Plate member), the rotation of the input shaft 2 is transmitted, the rod 6 (support shaft) rotating around the axis Y (Y1, Y2) extending in the radial direction of the input shaft 2 (axis X), and the axis of the rod 6 A roller R that is movable in the Y (Y1, Y2) direction and is integrally rotatable with the rod 6, and transmits the rotation between the input shaft 2 and the output shaft 3 to the disk portion 5. A speed change mechanism 1 configured to be performed via a contacted roller R,
Four rods 6 are provided at intervals of 90 degrees in the circumferential direction around the axis X, and
A moving mechanism 8 that is connected to a roller R provided on each of the rods 6 and moves each of the rollers R in synchronization with the direction of the axis Y (Y1, Y2); and a driving means 9 that drives the moving mechanism 8; Provided,
The moving mechanism 8 is
The scissors member 20 in which the pair of link members 10 (10A, 10B) are coupled to each other at the intermediate portion in the longitudinal direction so as to be relatively rotatable around the common rotation axis Xc, the rotation axis Xc is parallel to the axis X. The scissors members 20 that are adjacent to each other in the circumferential direction are arranged in a ring shape in the circumferential direction around the axis X, and the ends of the link members 10 (10A, 10B) are connected to each other (the first end portion 111A and the other end portion). 112B, the other end 112A and the one end 111B) are connected to each other so as to be rotatable relative to each other.
The rotation axis Xc of the link member 10 is offset from a straight line Lm connecting the connection point (connection member 16) on the inner diameter side of the link member 10 (10A, 10B) and the connection point (connection member 17) on the outer diameter side. The transmission mechanism 1 having the set configuration is obtained.

このように構成すると、移動機構８において一対のリンク部材１０（１０Ａ、１０Ｂ）の交差角θを変更すると、移動機構８の周方向の長さが変化して、移動機構８の外径が、交差角θの変更方向に応じて拡縮する。この際、移動機構８の外径は、回転軸２（軸線Ｘ）を中心とした径方向に均等に拡縮するので、移動機構８に連結されたローラＲの各々は、回転軸２の径方向（軸線Ｙ（Ｙ１、Ｙ２））に同期しつつ移動する。
よって、一対のリンク部材１０（１０Ａ、１０Ｂ）の交差角θを変更することで、ローラＲの各々を、回転軸２の回転中心（軸線Ｘ）を基準とした同心円上に位置させた状態で、径方向に進退移動させることができる。With this configuration, when the crossing angle θ of the pair of link members 10 (10A, 10B) is changed in the moving mechanism 8, the circumferential length of the moving mechanism 8 changes, and the outer diameter of the moving mechanism 8 is Scale up / down according to the change direction of the crossing angle θ. At this time, the outer diameter of the moving mechanism 8 is uniformly expanded and contracted in the radial direction around the rotation shaft 2 (axis X), so that each of the rollers R connected to the movement mechanism 8 is in the radial direction of the rotation shaft 2. It moves while synchronizing with (Axis Y (Y1, Y2)).
Therefore, by changing the crossing angle θ of the pair of link members 10 (10A, 10B), each of the rollers R is positioned on a concentric circle with the rotation center (axis line X) of the rotation shaft 2 as a reference. It can be moved forward and backward in the radial direction.

移動機構８では、ローラＲが、リンク部材１０（１０Ａ、１０Ｂ）の内径側の連結点（連結部材１６Ａ）に、連結部材７を介して設けられており、連結部材７は連結部材１６と一体に、リンク部材１０に対して相対回転可能に設けられている構成とした。   In the moving mechanism 8, the roller R is provided at a connecting point (connecting member 16 </ b> A) on the inner diameter side of the link member 10 (10 </ b> A, 10 </ b> B) via the connecting member 7, and the connecting member 7 is integrated with the connecting member 16. In addition, the structure is provided so as to be rotatable relative to the link member 10.

移動機構８では、一対のリンク部材１０（１０Ａ、１０Ｂ）の交差角θが変化すると、リンク部材１０の長手方向の中間に位置する膨出部１１３（連結部材１５）と、シザーズ部材２０（リンク部材１０）の内径側の連結点（連結部材１６）と、シザーズ部材２０（リンク部材１０）の外径側の連結点（連結部材１７）の各々が、入力軸２（軸線Ｘ）の径方向に同期して移動するので、連結点（連結部材１６）に連結された各ローラＲは、その径方向の位置を同期させながら径方向に移動する。これにより、各ローラＲを、回転軸の回転中心（軸線Ｘ）を基準とした同心円上に位置させた状態で、径方向に移動させることができる。
よって、ひとつの移動機構８を用いて、複数のローラＲの径方向位置を同期させて変化させることができる。
また、移動機構８は、一対のリンク部材１０（１０Ａ、１０Ｂ）を相対回転可能に連結して構成されるシザーズ部材２０を、互いのリンク部材１０（１０Ａ、１０Ｂ）の端部同士を相対回転可能に連結して構成されているので、移動機構８の外径を変化させる際に生じる摩擦が少なくて済み、必要な駆動力が少なくて済む。そして、少ない駆動力で、ローラＲの位置を同期させて変化させることができるので、入力軸２と出力軸３の間のトルクの伝達を、高効率で行うことができる。
さらに、移動機構８（シザーズリンク機構）における最も内径側にローラが連結されるので、外径側の連結点（連結部材１６）にローラＲを設ける場合よりも、軸線Ｘの径方向（円板部５の半径方向）におけるローラＲの移動量を大きくすることができる。これにより、円板部５の半径方向におけるローラＲの接触半径の変化幅が広くなるので、変速機構１における変速比の幅を広くすることができる。
また、連結部材７は連結部材１６と一体に、リンク部材１０に対して相対回転可能に設けられていることで、リンク部材１０（１０Ａ、１０Ｂ）の交差角θを変えて移動機構８の外径を変化させる際に、リンク部材１０の交差角の変化が、ロッド６の長手方向にのみ移動可能とされたローラＲにより阻害されることがない。In the moving mechanism 8, when the crossing angle θ of the pair of link members 10 (10 </ b> A, 10 </ b> B) changes, the bulging portion 113 (the connecting member 15) located in the middle in the longitudinal direction of the link member 10, The connecting point (connecting member 16) on the inner diameter side of the member 10) and the connecting point (connecting member 17) on the outer diameter side of the scissors member 20 (link member 10) are each in the radial direction of the input shaft 2 (axis X). Therefore, each roller R coupled to the coupling point (coupling member 16) moves in the radial direction while synchronizing its radial position. Thereby, each roller R can be moved in the radial direction while being positioned on a concentric circle with reference to the rotation center (axis line X) of the rotation shaft.
Therefore, it is possible to change the radial positions of the plurality of rollers R in synchronization by using one moving mechanism 8.
Moreover, the moving mechanism 8 relatively rotates the scissors member 20 configured by connecting the pair of link members 10 (10A, 10B) so as to be relatively rotatable, and the ends of the link members 10 (10A, 10B) are relatively rotated. Since it is configured so as to be connected, it is possible to reduce the friction generated when the outer diameter of the moving mechanism 8 is changed, and to reduce the required driving force. Since the position of the roller R can be changed synchronously with a small driving force, torque can be transmitted between the input shaft 2 and the output shaft 3 with high efficiency.
Further, since the roller is coupled to the innermost diameter side in the moving mechanism 8 (scissers link mechanism), the radial direction of the axis X (disc) is larger than when the roller R is provided at the outer diameter side coupling point (coupling member 16). The amount of movement of the roller R in the radial direction of the portion 5 can be increased. As a result, the width of change in the contact radius of the roller R in the radial direction of the disc portion 5 is widened, so that the width of the gear ratio in the speed change mechanism 1 can be widened.
Further, the connecting member 7 is provided integrally with the connecting member 16 so as to be relatively rotatable with respect to the link member 10, so that the crossing angle θ of the link member 10 (10 </ b> A, 10 </ b> B) is changed and the outside of the moving mechanism 8. When the diameter is changed, the change in the crossing angle of the link member 10 is not hindered by the roller R that is movable only in the longitudinal direction of the rod 6.

ここで、移動機構８は、軸線Ｘの軸方向から見てリング状のガイドプレート４に載置されており、リンク部材１０（１０Ａ、１０Ｂ）の内径側の連結点（連結部材１６）のうち、ローラＲが連結された連結部材１６Ａは、軸方向の長さが他の連結部材１６よりも長くなっており、連結部材７とは反対側の端部を、ガイドプレート４に設けたガイド溝４３に挿入させており、ガイド溝４３は、軸線Ｙ（Ｙ１、Ｙ２）に沿って、軸線Ｘの径方向に直線状に設けられている構成としたので、ローラＲの各々が軸線Ｙ（Ｙ１、Ｙ２）に進退移動する際に、連結部材１６Ａがガイド溝４３に沿って移動することで、ローラＲの軸線Ｙ（Ｙ１、Ｙ２）方向の移動をより正確に行うことができる。
ローラＲが軸線Ｙ（Ｙ１、Ｙ２）から逸れて、ローラＲの軸線Ｙ（Ｙ１、Ｙ２）方向の位置がズレると、円板部５の半径方向におけるローラＲの接触位置がズレてしまい、入力軸の回転が予定されていた変速比で変速されないことになるが、上記のように構成することで、かかる事態の発生が好適に防止される。Here, the moving mechanism 8 is placed on the ring-shaped guide plate 4 when viewed from the axial direction of the axis X, and is included in the connecting point (connecting member 16) on the inner diameter side of the link member 10 (10A, 10B). The connecting member 16A to which the roller R is connected has an axial length longer than that of the other connecting members 16, and a guide groove provided on the guide plate 4 at the end opposite to the connecting member 7. Since the guide groove 43 is linearly provided in the radial direction of the axis X along the axis Y (Y1, Y2), each of the rollers R has the axis Y (Y1). , Y2), when the connecting member 16A moves along the guide groove 43, the roller R can be moved in the direction of the axis Y (Y1, Y2) more accurately.
If the roller R deviates from the axis Y (Y1, Y2) and the position of the roller R in the direction of the axis Y (Y1, Y2) shifts, the contact position of the roller R in the radial direction of the disc portion 5 shifts, and the input Although the shaft is not rotated at the gear ratio that the rotation of the shaft is planned, the configuration as described above suitably prevents the occurrence of such a situation.

駆動手段９を、シザーズ部材２０における外径側の連結点（連結部材１７）のうちのひとつの連結部材１７Ａに相対回転可能に連結された連結棒９１と、連結棒９１を軸線Ｙ２の軸方向に進退移動させるアクチュエータ９０と、から構成した。   The drive means 9 is connected to one connecting member 17A of the outer diameter side connecting points (connecting member 17) of the scissors member 20 so as to be relatively rotatable, and the connecting rod 91 is axially moved along the axis Y2. And an actuator 90 that moves forward and backward.

このように構成すると、シザーズ部材２０の外径側の連結点（連結部材１７）のうちの一箇所の連結点（連結部材１７Ａ）を、軸線Ｘの径方向（軸線Ｙ２方向）に進退移動させることで、移動機構８を構成する各シザーズ部材２０におけるリンク部材１０（１０Ａ、１０Ｂ）の交差角θを変化させて、移動機構８全体の外径を変更できるので、１つのアクチュエータ９０のみで移動機構８の外径を拡縮して、移動機構８に連結された各ローラＲの軸線Ｙ（Ｙ１、Ｙ２）方向の位置を、同期させながら移動させることができる。
これにより、軸線Ｘ周りの周方向に複数設けられたローラＲ毎に、ローラＲを移動させるための機構を用意して、各機構を独立して制御する必要が生じないので、変速機構の構成の複雑化を防止できる。また、各機構を独立して制御する場合には、各ローラＲの位置を同期させながら移動させる必要が生じるので、各機構の制御が難しくなる。前記した実施の形態では、共通の移動機構８を用いて各ローラＲを同期させながら移動させることができるようになっており、ローラＲの移動に１つのアクチュエータ９０のみを採用しているので、各機構を独立して制御する場合に見られるような、制御上の困難性が生ずることもない。If comprised in this way, one connection point (connection member 17A) of the connection points (connection member 17) by the side of the outer diameter of the scissors member 20 will be moved forward and backward in the radial direction of the axis X (direction of the axis Y2). As a result, the outer diameter of the entire moving mechanism 8 can be changed by changing the crossing angle θ of the link members 10 (10A, 10B) in each scissors member 20 constituting the moving mechanism 8, so that only one actuator 90 moves. The outer diameter of the mechanism 8 can be enlarged or reduced, and the position of each roller R connected to the moving mechanism 8 in the direction of the axis Y (Y1, Y2) can be moved while being synchronized.
Accordingly, it is not necessary to prepare a mechanism for moving the roller R for each of the plurality of rollers R provided in the circumferential direction around the axis X and to control each mechanism independently. Can be prevented from becoming complicated. In addition, when each mechanism is controlled independently, it is necessary to move the respective rollers R while synchronizing the positions thereof, so that the control of each mechanism becomes difficult. In the above-described embodiment, each roller R can be moved while being synchronized using the common moving mechanism 8, and only one actuator 90 is used for the movement of the roller R. There is no control difficulty as seen when the mechanisms are controlled independently.

前記した実施の形態では、入力軸の回転に連動してローラＲが回転するように構成すると共に、出力軸３に円板部５を設けて、図示しない駆動源からの回転駆動力が、入力軸２、ローラＲ、円板部５、出力軸３の順番で伝達されるようにしたが、円板部を入力軸２側に設けると共に、ローラＲの回転に連動して出力軸３が回転するように構成して、図示しない駆動源からの回転駆動力が、入力軸２、円板部、ローラＲ、出力軸３の順番に伝達されるようにしても良い。
さらに、移動機構８における内径側の連結点（連結部材１６）にローラＲを設ける場合を例示したが、外径側の連結点（連結部材１７）やシザーズ部材２０を構成する２本のリンク部材の回動軸（連結部材１５）にローラＲを設けた構成としても良い。In the above-described embodiment, the roller R is configured to rotate in conjunction with the rotation of the input shaft, and the disk portion 5 is provided on the output shaft 3 so that the rotational driving force from a driving source (not shown) is input. The shaft 2, the roller R, the disc portion 5, and the output shaft 3 are transmitted in this order, but the disc portion is provided on the input shaft 2 side and the output shaft 3 rotates in conjunction with the rotation of the roller R. In this configuration, a rotational driving force from a driving source (not shown) may be transmitted in the order of the input shaft 2, the disk portion, the roller R, and the output shaft 3.
Furthermore, although the case where the roller R is provided at the connecting point (connecting member 16) on the inner diameter side in the moving mechanism 8 is illustrated, the two link members constituting the connecting point (connecting member 17) on the outer diameter side and the scissors member 20 are illustrated. It is good also as a structure which provided the roller R in the rotating shaft (connection member 15).

すなわち、移動機構８では、一対のリンク部材（１０Ａ、１０Ｂ）の互いの連結点（連結部材１５）、シザーズ部材２０（リンク部材１０）の内径側の連結点（連結部材１６）、シザーズ部材２０（リンク部材１０）の外径側の連結点（連結部材１７）のうちの何れか一箇所に、リンク部材１０（１０Ａ、１０Ｂ）に対して相対回転可能に設けられた連結部材７を介してローラＲが連結されている構成とすることで、各ローラＲの位置を、回転軸の回転中心（軸線Ｘ）を基準とした同心円上に位置させた状態で、径方向に同期させつつ移動させることができる。   That is, in the moving mechanism 8, the connection point (connection member 15) of the pair of link members (10 </ b> A, 10 </ b> B), the connection point (connection member 16) on the inner diameter side of the scissors member 20 (link member 10), and the scissors member 20. Via a connecting member 7 provided to be rotatable relative to the link member 10 (10A, 10B) at any one of the connecting points (connecting member 17) on the outer diameter side of the (link member 10). By adopting a configuration in which the rollers R are connected, the position of each roller R is moved while being synchronized in the radial direction in a state where the position of each roller R is positioned on a concentric circle with respect to the rotation center (axis line X) of the rotation shaft. be able to.

また、移動機構８における外径側の連結点（連結部材１７）のうちのひとつに連結された連結棒９１を進退移動させるアクチュエータ９０を例示したが、内径側の連結点（連結部材１６）のうちのひとつ、または、シザーズ部材２０を構成する２本のリンク部材の回動軸（連結部材１５）のうちのひとつに連結棒９１を連結して、この連結棒９１を進退移動させるアクチュエータを設けた構成としてもよい。 Moreover, although the actuator 90 which moves the connecting rod 91 connected to one of the outer diameter side connecting points (connecting member 17) in the moving mechanism 8 is illustrated, the inner diameter side connecting point (connecting member 16) is illustrated. An actuator for connecting the connecting rod 91 to one of the rotating shafts (connecting members 15) of the two link members constituting the scissors member 20 and moving the connecting rod 91 back and forth is provided. It is good also as a structure.

以下、シザーズ部材と移動機構の変形例を説明する。
図５および図６は、シザーズ部材と移動機構の変形例を説明する図である。
図５の（ａ）は、変形例にかかるシザーズ部材２０Ａを説明する図であり、（ｂ）は、シザーズ部材２０Ａを３つ組み合わせて構成した移動機構８Ａを説明する図である。
図５の（ｃ）は、変形例にかかるシザーズ部材２０Ｂを説明する図であり、（ｂ）は、シザーズ部材２０Ｂを４つ組み合わせて構成した移動機構８Ａを説明する図である。
図６の（ａ）は、変形例にかかるシザーズ部材２０Ｃを説明する図であり、（ｂ）は、シザーズ部材２０Ｃを６つ組み合わせて構成した移動機構８Ｃを説明する図であり、（ｃ）は、変形例にかかるシザーズ部材２０Ｄを説明する図であり、（ｄ）は、シザーズ部材２０Ｄを６つ組み合わせて構成した移動機構８Ｄを説明する図である。なお、図５および図６では、シザーズ部材２０Ａ〜２０Ｄにおいて、重ねられたリンク部材１０（１０Ａ、１０Ｂ）を互いに区別できるようにするために、一方のリンク部材１０Ａを、ハッチングを付して示している。Hereinafter, modified examples of the scissors member and the moving mechanism will be described.
FIG. 5 and FIG. 6 are diagrams for explaining modifications of the scissors member and the moving mechanism.
FIG. 5A is a diagram illustrating a scissors member 20A according to a modification, and FIG. 5B is a diagram illustrating a moving mechanism 8A configured by combining three scissors members 20A.
(C) of FIG. 5 is a figure explaining the scissors member 20B concerning a modification, (b) is a figure explaining the moving mechanism 8A comprised combining four scissors members 20B.
FIG. 6A is a diagram illustrating a scissors member 20C according to a modification, and FIG. 6B is a diagram illustrating a moving mechanism 8C configured by combining six scissors members 20C. These are figures explaining scissors member 20D concerning a modification, and (d) is a figure explaining movement mechanism 8D constituted by combining six scissors members 20D. 5 and 6, in order to be able to distinguish the overlapping link members 10 (10A, 10B) from each other in the scissors members 20A to 20D, one link member 10A is shown with hatching. ing.

前記した実施の形態では、軸線Ｘ周りの周方向に合計１２個のシザーズ部材２０をリング状に連ねて構成した移動機構８の場合を例示したが、シザーズ部材をリング状に連結することができる範囲内で、シザーズ部材の数を適宜変更することが可能である。さらに、シザーズ部材におけるリンク部材の形状も、シーザー部材を構成するもう一方のリンク部材との連結点の位置が、当該リンク部材における他のシザーズ部材のリンク部材との連結点同士を繋ぐ直線Ｌｍからオフセットした位置に設けられている限り、適宜変更可能である。
そして、移動機構８に連結するローラＲの数も適宜変更可能である。In the above-described embodiment, the case of the moving mechanism 8 configured by connecting a total of twelve scissors members 20 in a ring shape in the circumferential direction around the axis X is illustrated, but the scissors members can be connected in a ring shape. Within the range, the number of scissors members can be changed as appropriate. Furthermore, the shape of the link member in the scissors member is also determined from the straight line Lm where the position of the connection point with the other link member constituting the caesar member connects the connection points with the link member of the other scissors member in the link member. As long as it is provided at the offset position, it can be appropriately changed.
The number of rollers R connected to the moving mechanism 8 can be changed as appropriate.

例えば、図５に示すように、合計３個のシザーズ部材２０Ａをリング状に連ねて構成した移動機構８Ａとすることや、合計４個のシザーズ部材２０Ｂをリング状に連ねて構成した移動機構８Ｂとしても良い。
さらに、図６に示すように、合計６個のシザーズ部材２０Ｃをリング状に連ねて構成した移動機構８Ｃとすることや、合計６個のシザーズ部材２０Ｄをリング状に連ねて構成した移動機構８Ｄとしても良い。
このようにすることによっても、シザーズ部材２０Ａ、２０Ｂ、２０Ｃ、２０Ｄにおけるリンク部材１０Ａ、１０Ｂの交差角θを変更すると、シザーズ部材２０Ａ、２０Ｂ、２０Ｃ、２０Ｄの外径側の連結点（連結部材１７）と、内径側の連結点（連結部材１６）は、軸線Ｘから径方向に延びる直線Ｌｒ上を、リンク部材１０Ａ、１０Ｂの交差角θの変化方向に応じて決まる一方向に移動する。よって、例えば内径側の連結部材１６または外径側の連結部材１７にローラＲを設けることで、軸線Ｘの径方向におけるローラＲの位置を、同期させながら変化させることができる。For example, as shown in FIG. 5, a moving mechanism 8A configured by connecting a total of three scissors members 20A in a ring shape, or a moving mechanism 8B configured by connecting a total of four scissors members 20B in a ring shape. It is also good.
Further, as shown in FIG. 6, a moving mechanism 8C configured by connecting a total of six scissors members 20C in a ring shape, or a moving mechanism 8D configured by connecting a total of six scissors members 20D in a ring shape. It is also good.
Also by doing in this way, if the crossing angle θ of the link members 10A, 10B in the scissors members 20A, 20B, 20C, 20D is changed, the connecting point (the connecting member on the outer diameter side of the scissors members 20A, 20B, 20C, 20D) 17) and the connecting point (connecting member 16) on the inner diameter side move on a straight line Lr extending in the radial direction from the axis X in one direction determined according to the changing direction of the crossing angle θ of the link members 10A and 10B. Therefore, for example, by providing the roller R on the inner diameter side connecting member 16 or the outer diameter side connecting member 17, the position of the roller R in the radial direction of the axis X can be changed while being synchronized.

特に、図６の（ｂ）に示すように、合計６個のシザーズ部材２０Ｃをリング状に連ねて構成した移動機構８Ｃを構成するに当たり、リンク部材１０Ａ、１０Ｂの、貫通孔１４側の端部に段部１４ａを設けたうえで、一方のリンク部材１０Ａが紙面手前側に、他方のリンク部材１０Ｂが紙面奥側に配置されるようにすると、内径側の連結点（連結部材１６）が、直線Ｌｒ上で外径側の連結点（連結部材１７）と重なる位置まで、移動機構８Ｃの外径を大きくすることができる。
そうすると、内径側の連結点（連結部材１６）に連結したローラＲの径方向の移動量を、図６の（ｃ）に示す移動機構８Ｄの場合よりも大きくすることができるので、変速比幅を大きくすることが可能となる。In particular, as shown in FIG. 6 (b), in configuring the moving mechanism 8C configured by connecting a total of six scissors members 20C in a ring shape, the end portions of the link members 10A and 10B on the through-hole 14 side. If the one link member 10A is disposed on the front side of the paper and the other link member 10B is disposed on the back side of the paper surface, the inner diameter side connection point (the connection member 16) is The outer diameter of the moving mechanism 8 </ b> C can be increased to a position that overlaps with the outer-diameter-side connecting point (connecting member 17) on the straight line Lr.
As a result, the amount of movement in the radial direction of the roller R connected to the connecting point (connecting member 16) on the inner diameter side can be made larger than in the case of the moving mechanism 8D shown in FIG. Can be increased.

Claims (4)

入力側の回転軸と出力側の回転軸のうちの一方に設けられた円板部材と、
前記入力側の回転軸と前記出力側の回転軸のうちの他方の回転が伝達されて、前記回転軸の径方向に延びる軸線周りに回転する支持軸と、
前記軸線方向に移動可能、かつ前記支持軸と一体回転可能に前記支持軸に設けられたローラと、を備え、
前記入力側の回転軸と前記出力側の回転軸との間の回転の伝達を、前記円板部材に当接させたローラを介して行うように構成された変速機構であって、
前記支持軸を前記回転軸周りの周方向に複数設けると共に、
前記支持軸の各々に設けたローラに連結されて、前記ローラの各々を前記軸線方向に同期して移動させる移動機構と、
前記移動機構を駆動する駆動手段と、を設け、
前記移動機構は、
一対のリンク部材を長手方向における中間部で互いに連結して共通の回動軸周りに相対回転可能としたシザーズ部材を、前記回動軸が前記回転軸に平行となる向きで、前記回転軸周りの周方向に並べてリング状に配置すると共に、前記周方向で隣接するシザーズ部材を、互いのリンク部材の前記長手方向における一端側と他端側の連結部同士を相対回転可能に連結して構成され、
前記リンク部材の回動軸を、当該リンク部材の一端側の連結部と他端側の連結部とを結ぶ直線からオフセットした位置に設定した変速機構。A disk member provided on one of the input side rotary shaft and the output side rotary shaft;
The other rotation of the input-side rotation shaft and the output-side rotation shaft is transmitted, and a support shaft that rotates around an axis extending in the radial direction of the rotation shaft;
A roller provided on the support shaft so as to be movable in the axial direction and capable of rotating integrally with the support shaft;
A transmission mechanism configured to transmit rotation between the input-side rotation shaft and the output-side rotation shaft via a roller in contact with the disk member;
While providing a plurality of the support shafts in the circumferential direction around the rotation shaft,
A moving mechanism coupled to the rollers provided on each of the support shafts and moving each of the rollers in synchronization with the axial direction;
Driving means for driving the moving mechanism;
The moving mechanism is
A scissors member that connects a pair of link members to each other at an intermediate portion in the longitudinal direction so as to be relatively rotatable around a common rotation axis, with the rotation axis being parallel to the rotation axis and around the rotation axis. The scissors members adjacent to each other in the circumferential direction are connected to each other in the longitudinal direction so as to be relatively rotatable with each other in the longitudinal direction. And
A speed change mechanism in which a rotation shaft of the link member is set at a position offset from a straight line connecting a connecting portion on one end side and a connecting portion on the other end side of the link member. 前記移動機構では、前記リンク部材の前記中間部、前記一端側の連結部、前記他端側の連結部のうちの何れか一箇所に、前記ローラが連結されている請求項１に記載の変速機構。   2. The speed change according to claim 1, wherein in the moving mechanism, the roller is connected to any one of the intermediate portion of the link member, the connecting portion on the one end side, and the connecting portion on the other end side. mechanism. 前記ローラは、前記リンク部材の前記一端側の連結部と前記他端側の連結部のうち、前記回転軸の軸方向から見て内径側に位置する連結部に設けられている請求項１に記載の変速機構。   The said roller is provided in the connection part located in the internal diameter side seeing from the axial direction of the said rotating shaft among the connection part of the said one end side of the said link member, and the connection part of the said other end side. The transmission mechanism described. 前記駆動手段は、
前記リンク部材の端部同士の連結部のうち前記回転軸の軸方向から見て外径側に位置する連結部のうちのひとつに連結されたロッドと、
前記ロッドを前記軸線方向に進退移動させるアクチュエータと、から構成される請求項１から請求項３の何れか一項に記載の変速機構。The driving means includes
A rod connected to one of the connecting portions located on the outer diameter side when viewed from the axial direction of the rotating shaft among the connecting portions of the end portions of the link member;
The speed change mechanism according to any one of claims 1 to 3, further comprising an actuator that moves the rod forward and backward in the axial direction.
JP2015508121A 2013-03-25 2014-01-23 Speed change mechanism Expired - Fee Related JP5922304B2 (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB452422A (en) * 1935-02-15 1936-08-17 Charles Humphrey Woods Improvements in variable speed and reversing gearing
US4819494A (en) * 1987-04-01 1989-04-11 Giuliani Robert L Continuously variable transmission
JPH02278048A (en) * 1989-04-19 1990-11-14 Takashi Takahashi Continuously variable trnsmission

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB452422A (en) * 1935-02-15 1936-08-17 Charles Humphrey Woods Improvements in variable speed and reversing gearing
US4819494A (en) * 1987-04-01 1989-04-11 Giuliani Robert L Continuously variable transmission
JPH02278048A (en) * 1989-04-19 1990-11-14 Takashi Takahashi Continuously variable trnsmission

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