JPS63225753A - Variable speed pulley device - Google Patents
Variable speed pulley deviceInfo
- Publication number
- JPS63225753A JPS63225753A JP4597987A JP4597987A JPS63225753A JP S63225753 A JPS63225753 A JP S63225753A JP 4597987 A JP4597987 A JP 4597987A JP 4597987 A JP4597987 A JP 4597987A JP S63225753 A JPS63225753 A JP S63225753A
- Authority
- JP
- Japan
- Prior art keywords
- movable
- pulley
- input shaft
- shaft
- screw member
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000007246 mechanism Effects 0.000 claims abstract description 21
- 230000008859 change Effects 0.000 claims abstract description 12
- 238000013459 approach Methods 0.000 abstract description 6
- 230000003247 decreasing effect Effects 0.000 abstract description 2
- 230000005540 biological transmission Effects 0.000 description 9
- 230000007423 decrease Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000008901 benefit Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
Classifications
-
- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
- F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
- F16H63/067—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions mechanical actuating means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmissions By Endless Flexible Members (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、自動車や＠業機械等において変速装置の一部
として使用される可変プーリ装置の改良に関するもので
ある。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an improvement in a variable pulley device used as a part of a transmission in automobiles, industrial machinery, and the like.
（従来の技術）
従来より、ベルト伝動を利用したベルト式変速装置とし
て、互いに平行に配置された１対の入出力軸の各々に、
該入出力軸の各々に対して回転一体にかつ摺動不能に固
定された固定シェイブと、各軸に可動シェイブとの間に
Ｖ字状のベルト湯を形成するように対向配置されて回転
一体にかつ開動自在に支持された可動シェイブとからな
る可変プーリを設けるとともに、これら両可変プーリの
ベルト溝間にベルト部材を巻き掛け、各可変プーリの可
動シェイブを軸方向に移動させて固定シェイブに接離さ
せ、両シェイブ間のベルト湛に巻き掛けられるベルト部
材に対する有効半径を可変とすることにより、入出力軸
間の変速比を変えるようにしたものはよく知られている
。そして、通常、上記可変プーリにおける可動シェイブ
に対する駆動制御を油圧を利用して行うようになされて
いる。(Prior Art) Conventionally, as a belt-type transmission using belt transmission, each of a pair of input and output shafts arranged parallel to each other,
A fixed shave that is rotatably and non-slidably fixed to each of the input/output shafts and a movable shaver for each shaft are arranged oppositely to form a V-shaped belt and are rotatably integral. A variable pulley consisting of a movable shave and a movable shave supported so as to be freely openable is provided, a belt member is wound between the belt grooves of both of these variable pulleys, and the movable shave of each variable pulley is moved in the axial direction to form a fixed shave. It is well known that the gear ratio between the input and output shafts is changed by making the effective radius of the belt member, which is moved toward and away from the shaft and wound around the belt between both shavers, variable. Usually, drive control of the movable shaver in the variable pulley is performed using hydraulic pressure.
しかし、この油圧を利用する場合は、油圧配管等を必要
とし、しかも可動シェイブの駆動制御が複雑になるとと
もに、装置溝成が大掛かりになるという難がおった。However, when using this hydraulic pressure, hydraulic piping and the like are required, and furthermore, the driving control of the movable shaver becomes complicated, and the equipment configuration becomes large-scale.
ところで、こうした可変プーリにおける可動シェイブを
機械的に駆動するようにしたものとして、従来、例えば
特開昭５９−６２７６０号公報に示されるように、回転
軸に雄ねじ筒を摺動不能にかつ回転自在に支持する一方
、この雄ねじ筒に外嵌合されて螺合される雌ねじ筒を回
転軸上の可変プーリの可動シェイブに軸方向に移動一体
にかつ回転自在に取り付け、該雌ねじ筒を支持枠の案内
）ＲにＭ嵌合し、サーボモータにより上記雄ねじ筒を回
転させて雌ねじ筒をねじ送りすることにより、可変プー
リにおける固定シェイブと可動シェイブとの間隔を変え
て可変プーリの有効半径を可変調整するようにしたもの
が提案されている。By the way, in order to mechanically drive the movable shaver in such a variable pulley, conventionally, as shown in Japanese Patent Application Laid-open No. 59-62760, a male threaded cylinder is attached to a rotating shaft so that it cannot slide but can rotate freely. At the same time, a female threaded tube that is externally fitted and screwed into this male threaded tube is attached to a movable shave of a variable pulley on a rotating shaft so that it can move integrally and rotatably in the axial direction. By fitting M into guide) R and rotating the male thread cylinder with a servo motor and threading the female thread cylinder, the effective radius of the variable pulley can be variably adjusted by changing the distance between the fixed shave and the movable shave on the variable pulley. It has been proposed to do so.
（発明が解決しようとする問題点）
しかし、この提案のものでは、アクチュエータとしての
サーボモータの出力により雌ねじ筒をねじ送りしてプー
リの可動シェイブを駆動するため、サーボモータに対す
る作動制御および装置の５偶造かやはり複雑になるとと
もに、高価なサーボモータを使用するのでコストアップ
するという問題が必る。(Problems to be Solved by the Invention) However, in this proposal, the output of the servo motor as an actuator is used to screw feed the female thread cylinder and drive the movable shave of the pulley. The five-way construction is also complicated, and requires an expensive servo motor, which inevitably increases costs.
本発明は斯かる諸点に鑑みてなされたものでおり、その
目的は、回転軸との相対回転により可変プーリにおける
可動シェイブを回転軸に対して移動させる手段を講じる
ことにより、回転軸の回転力を効果的に利用して可動シ
ェイブを駆動するようにし、よって可動シェイブに対す
る駆動１】す御を簡易にかつ簡単で安価な＠造でもって
行い得るようにすることにある。The present invention has been made in view of the above points, and an object of the present invention is to reduce the rotational force of the rotary shaft by providing means for moving the movable shave in the variable pulley with respect to the rotary shaft by relative rotation with the rotary shaft. To drive a movable shaver by effectively utilizing the 1) speed, and thereby to easily control the movable shaver with a simple and inexpensive construction.
（問題点を解決するための手段）
この目的を達成するために、本発明の解決手段は、可変
プーリか設けられる回転軸に対して、可変プーリの可動
シェイブを軸方向に移動させるためのねじ部材やカム部
材等の移動部＋１を支持し、この移動部材と回転軸との
相対回転により可動シェイブを軸方向に移動させるよう
にしたもので必る。(Means for solving the problem) In order to achieve this object, the solution of the present invention provides a screw for moving the movable shave of the variable pulley in the axial direction with respect to the rotating shaft on which the variable pulley is provided. It is necessary to support a moving part +1 such as a member or a cam member, and to move the movable shave in the axial direction by relative rotation between this moving member and a rotating shaft.
具体的には、本発明の構成は、回転軸に回転一体にかつ
摺動不能に固定された固定シェイブと、回転軸に軸方向
に囲動自在にかつ回転一体に支持された可動シェイブと
を備え、上記可動シェイブを固定シェイブに対し接離さ
せて両シェイブ間に巻き掛けられるベルト部材に対する
有効半径を可変とした可変プーリ装置を前提とする。Specifically, the configuration of the present invention includes a fixed shave that is rotatably and non-slidably fixed to a rotating shaft, and a movable shave that is rotationally and integrally supported to the rotating shaft so as to be movable in the axial direction. The present invention is based on a variable pulley device in which the movable shaver is moved toward and away from the fixed shaver, and the effective radius of the belt member wound between the two shavers is variable.
そして、上記回転軸上に支持され、かつ上記可動シェイ
ブに軸方向に移動一体に連結され、回転軸との相対回転
によりねじ送りあるいは押圧されて軸方向に移動可能な
移動部材を設けるとともに、この移動部材を回転軸に対
して相対回転させる変速切換機構を設ける。Further, a movable member is provided which is supported on the rotary shaft and integrally connected to the movable shaver so as to be movable in the axial direction by being screwed or pressed by relative rotation with the rotary shaft. A speed change switching mechanism is provided to rotate the moving member relative to the rotating shaft.
（作用）
この構成により、本発明では、変速切換機構の作動によ
り移動部材が回転軸に対して相対回転し、この相対回転
に伴って移動部材はねじ送りや抑圧により回転軸の軸方
向に移動し、このことにより移動部材に移動一体に連結
されている可変プーリの可動シェイブが移動して該プー
リの有効半径が可変調整される。(Function) With this configuration, in the present invention, the moving member rotates relative to the rotating shaft due to the operation of the speed change switching mechanism, and along with this relative rotation, the moving member moves in the axial direction of the rotating shaft by screw feeding or compression. As a result, the movable shave of the variable pulley that is movably connected to the movable member is moved, and the effective radius of the pulley is variably adjusted.
したがって、こうして回転軸とそれに支持された移動部
材との相対回転により、可変プーリの可動シェイブを軸
方向に移動させるため、構造が極めて簡単になり、その
制御も容易になるとともに、サーボモータ等が不要であ
るので、安価に製作できるのである。Therefore, the movable shave of the variable pulley is moved in the axial direction by the relative rotation between the rotary shaft and the movable member supported by the rotary shaft, making the structure extremely simple and easy to control. Since it is not necessary, it can be manufactured at low cost.
（第１実施例） 以下、本発明の実施例を図面に基づいて説明する。(First example) Embodiments of the present invention will be described below based on the drawings.
第１図および第２図は本発明の第１実施例に係るプーリ
式変速装置の全体構成を示しており、１は本発明でいう
回転軸としての入力軸、２は該入力軸１と平行に配設さ
れた出力軸であって、上記入力軸１上には駆動プーリ３
が設けられている。1 and 2 show the overall configuration of a pulley type transmission according to a first embodiment of the present invention, in which 1 is an input shaft as a rotating shaft in the present invention, and 2 is parallel to the input shaft 1. an output shaft disposed on the input shaft 1, and a drive pulley 3 on the input shaft 1;
is provided.
この駆動ブー９３は、入力軸１にキー４により回転一体
にかつ摺動不能に固定されたフランジ状の固定シェイブ
５と、該固定シェイブ５に対向するように入力軸１にボ
ス部６ａにてキー７により情動自在にかつ回転一体に結
合されたフランジ状の可動シェイブ６とからなり、これ
ら両シェイブ５゜６間には断面略Ｖ字状のベルト溝８が
形成されている。 ゛
一方、上記出力軸２上には上記駆動プーリ３と同様の構
成を持つ従動プーリ９が設けられている。The drive boo 93 includes a flange-shaped fixed shave 5 which is rotatably and non-slidably fixed to the input shaft 1 by a key 4, and a boss portion 6a attached to the input shaft 1 so as to face the fixed shave 5. It consists of a flange-shaped movable shaver 6 which is freely and rotatably connected by a key 7, and a belt groove 8 having a substantially V-shaped cross section is formed between the two shavers 5.6. On the other hand, a driven pulley 9 having the same configuration as the drive pulley 3 is provided on the output shaft 2.
すなわち、この従動プーリ９は、出力軸２にキー１０に
より回転一体にかつ摺動不能に固定されたフランジ状の
固定シェイブ１１と、該固定シェイブ１１に上記入力軸
１上の駆動プーリ３における固定シェイブ５に対する可
動シェイブ６の対向方向と逆方向でもって対向するよう
に出力軸２にキー１３により摺動自在にかつ回転一体に
結合されたフランジ状の可動シェイブ１２とからなり、
これら両シェイブ１１．１２間には断面略Ｖ字状のベル
ト溝１４が形成されている。また、上記従動プーリ９の
可動シェイブ１２背面側の出ツノ軸２にはスプリング受
座１５が一体に固定され、このスプリング受座１５と可
動シェイブ１２背面との間には可動シェイブ１２を固定
シェイブ１１側に向かう方向に付勢するスプリング１６
が縮装されている。そして、上記駆動プーリ３のベルト
１％８と従動プーリ９のベルト溝１４との間にはペル１
〜部材としての■ベルシト１フが巻きｌ卦けられており
、駆動プーリ３の可動シェイブ６を固定シェイブ５に対
して接離させて駆動プーリ３および従動ブーツ９のＶベ
ルト１７に対する有効半径を可変調整し、駆動プーリ３
の可動シェイブ６を固定シェイブ５に接近させたとぎに
は、駆動プーリ３の有効半径を人にし、Ｖベルト１７の
張力により従動プーリ９の可動シェイブ１２をスプリン
グ１６の付勢力に抗して固定シェイブ１１から離隔させ
て従動プーリ９の有効半径を駆動プーリ３よりも小さく
することにより、入出力軸１，２間の変速比を大きくす
る一方、駆動プーリ３の可動シェイブ６を固定シェイブ
５から離隔させたときには、駆動プーリ３の有効半径を
小にし、Ｖベルト１７の張力によって従動プーリ９の可
動シェイブ１２をスプリング１６のイ」勢力によって固
定シェイブ１１に接近させて従動プーリ９の有効半径を
駆動プーリ３よりも大きくすることにより、入出力軸１
゜２間の変速比を小さくするように構成されている。That is, this driven pulley 9 includes a flange-shaped fixed shave 11 that is rotatably and non-slidably fixed to the output shaft 2 by a key 10, and a fixed shaft 11 fixed to the drive pulley 3 on the input shaft 1 to the fixed shave 11. It consists of a flange-shaped movable shaver 12 that is slidably and rotatably connected to the output shaft 2 by a key 13 so as to face the movable shaver 6 in the opposite direction to the shaver 5,
A belt groove 14 having a substantially V-shaped cross section is formed between these shavers 11 and 12. Further, a spring catch 15 is integrally fixed to the protruding shaft 2 on the back side of the movable shave 12 of the driven pulley 9, and the movable shave 12 is fixed between the spring catch 15 and the back of the movable shave 12. Spring 16 biasing in the direction toward 11 side
has been reduced. There is a pel 1 between the belt 1% 8 of the drive pulley 3 and the belt groove 14 of the driven pulley 9.
- A belt seat 1 is wound as a member, and the movable shaver 6 of the driving pulley 3 is brought into contact with and separated from the fixed shaver 5 to adjust the effective radius of the driving pulley 3 and the driven boot 9 with respect to the V-belt 17. Variable adjustment and drive pulley 3
When the movable shaver 6 approaches the fixed shaver 5, the effective radius of the drive pulley 3 is adjusted to the maximum radius, and the movable shaver 12 of the driven pulley 9 is fixed against the biasing force of the spring 16 by the tension of the V-belt 17. By separating the driven pulley 9 from the drive pulley 3 and making the effective radius smaller than that of the drive pulley 3, the gear ratio between the input and output shafts 1 and 2 is increased, while the movable drive pulley 6 of the drive pulley 3 is separated from the fixed drive pulley 5. When they are separated, the effective radius of the driving pulley 3 is made small, and the tension of the V-belt 17 causes the movable sheave 12 of the driven pulley 9 to approach the fixed sheave 11 by the force of the spring 16, thereby reducing the effective radius of the driven pulley 9. By making the drive pulley 3 larger, the input/output shaft 1
It is configured to reduce the gear ratio between .degree.
ざらに、本発明の特徴として、上記駆動プーリ３におけ
る可動シェイブ６に対し固定シ呈イブ５と反対側の入力
軸１外周面には雄ねじ部１８が形成され、該雄ねじ部１
８には移動部材としての円筒状のねじ部材１９が外嵌螺
合され、このねじ部材１９は上記駆動ブー９３にあける
可動シェイブ６のボス部６ａにベアリング２０を介して
相対回転自在にかつ軸方向に移動一体に連結されており
、ねじ部ｖｉ１９を入力軸１に対し相対回転させること
により、該ねじ部材１９を可動シェイブ６と共にねじ送
りして入力軸１の軸方向に移動可能とし、例えばねじ部
材１９を入力軸１に対して減速方向に相対回転させたと
きには、該ねじ部材１９を可動シェイブ６が固定シェイ
ブ５に接近する方向（図で左方向〉に移動させ、逆にね
じ部材１９を入力軸１に対して増速方向に相対回転させ
たとぎには、該ねじ部材１９を可動シェイブ６が固定シ
ェイブ５から離れる方向（図で右方向）に移動させるよ
うに構成されている。Briefly, as a feature of the present invention, a male threaded portion 18 is formed on the outer circumferential surface of the input shaft 1 on the side opposite to the fixed sheave 5 with respect to the movable shaved 6 in the driving pulley 3.
A cylindrical screw member 19 as a movable member is externally fitted and screwed into 8, and this screw member 19 is relatively rotatable via a bearing 20 to the boss portion 6a of the movable shaver 6 provided in the drive boob 93, and is attached to the shaft. By rotating the threaded portion vi19 relative to the input shaft 1, the threaded member 19 can be screwed together with the movable shaver 6 to move in the axial direction of the input shaft 1, for example. When the screw member 19 is rotated relative to the input shaft 1 in the deceleration direction, the screw member 19 is moved in the direction in which the movable shaver 6 approaches the fixed shaver 5 (leftward in the figure), and vice versa. When the movable shaver 6 is rotated relative to the input shaft 1 in the speed increasing direction, the screw member 19 is moved in a direction in which the movable shaver 6 is separated from the fixed shaver 5 (to the right in the figure).
また、上記入力軸１上には上記ねじ部（１１９を入力軸
１に対して相対回転させる変速切換殿構２１が設けられ
ている。この変速切換！置溝２１は、上記雄ねじ部１８
に対し駆動プーリ３と反対側の入力軸１に回転一体に固
定された第１のＶベルトプーリ２２と、上記従動プーリ
９に対しスプリング受座１５と反対側の出力軸２にベア
リング２３゜２４を介して回転自在に外嵌支持された円
筒状スリーブ２５とを備え、該スリーブ２５にはそのス
プリング受座１５と反対側方向の端部に上記第１のＶベ
ルトプーリ２２よりも小径の第２のＶベルトプーリ２６
が回転一体に固定され、この両Ｖベルトプーリ２２．２
６間にはＶベルト２７が巻ぎ掛けられている。また、上
記スリーブ２５のスプリング受座１５側方向の端部には
上記第２のＶベルトプーリ２６よりも大径の第１の歯付
プーリ２８が回転一体に固定されている。ざらに、上記
入力軸１上のねじ部材１９には上記＠１の歯付プーリ２
８よりも小径の第２の歯付ブー９２９が１Ｍ動不能にか
つベアリング３０を介して相対回転自在に外■支持され
、この第２の歯付プーリ２９と第１の歯付ブー９２８と
の間にはタイミングベルト３１が巻ぎ掛けられており、
以上のベルト伝動構造によってねじ部材１９上の第２の
歯付プーリ２９を入力軸１と同方向にそれよりも速い回
転速度で回転駆動させるようになされている。尚、上記
第１の歯付プーリ２８は、上記ねじ部材１９のねじ送り
により第２の歯付プーリ２９が軸方向に移動してもタイ
ミングベルト３１が外れないように外周のベルト巻掛は
面が広い幅に設定されている。Further, on the input shaft 1, there is provided a gear change change mechanism 21 for rotating the threaded part (119) relative to the input shaft 1.
On the other hand, there is a first V-belt pulley 22 rotatably fixed to the input shaft 1 on the opposite side to the drive pulley 3, and a bearing 23, 24 on the output shaft 2 on the opposite side to the spring seat 15 with respect to the driven pulley 9. The sleeve 25 has a cylindrical sleeve 25 which is rotatably supported externally via the spring seat 15, and the sleeve 25 has a second V-belt pulley having a diameter smaller than that of the first V-belt pulley 22 at the end opposite to the spring seat 15. 2 V belt pulley 26
is fixed to rotate integrally, and both V-belt pulleys 22.2
A V-belt 27 is wound around between the two. Further, a first toothed pulley 28 having a larger diameter than the second V-belt pulley 26 is rotatably fixed to the end of the sleeve 25 on the side of the spring seat 15 . Roughly speaking, the threaded member 19 on the input shaft 1 is connected to the toothed pulley 2 of @1.
A second toothed boob 929 having a diameter smaller than that of the toothed pulley 929 is supported externally through a bearing 30 so as to be immovable and relatively rotatable. A timing belt 31 is wound between them.
The belt transmission structure described above allows the second toothed pulley 29 on the screw member 19 to be driven to rotate in the same direction as the input shaft 1 at a faster rotational speed. Note that the first toothed pulley 28 has a flat outer circumference so that the timing belt 31 does not come off even if the second toothed pulley 29 moves in the axial direction due to screw feeding of the screw member 19. is set to a wide width.
そして、上記第２の歯付ブー９２９の一側（駆動プーリ
３側）には板状の押圧リング３２が、他側には同様に板
状の摩擦リング３３がそれぞれ配置され、この押圧リン
グ３２および摩擦リング３３は第２の歯付プーリ２９を
軸方向と平行に摺動自在に貫通する多数のピン３４，３
４．・・・によって一体的に連結されていて、該第２の
歯付プーリ２９と一体的に回転するようになされている
。また、上記ねじ部材１９の外周には上記摩１察リング
３３と一側面で接触可能なリング板状の摩擦部１９ａが
一体形成され、この摩擦部１９ａの他側方には該摩擦部
１９ａの他側面に接触可能な制動板３５が配置され、該
制動板３５は支持部材３６に支持されて入力＄ｌ１１と
平行な方向に１習動するロッド３７の中間部に一体的に
固定されている。該ロッド３７の一端部は上記押圧リン
グ３２と駆動プーリ３の可動シェイク６との間の位置ま
で延び、その先端部には押圧リング３２をローラホール
３８を介して押圧して摩擦リング３３に向かう方向（摩
擦リング３３がねじ部材１９の摩擦部１９ａに接触する
方向）に移動させる押圧部３９が形成されている。一方
、ロッド３７の他端部には入出力ｆｉＩｉ１１，２間の
変速比を高低２段階に切り換える揺動可能な切換レバー
４０がリンク４１を介して連結されており、この切換レ
バー４１の操作によってねじ部材１９を入力軸１に対し
て増速方向または減速方向に相対回転させ、第１図に示
すように、切換レバー４０を高速位置に位置付けたとぎ
には、ねじ部材１９の摩擦部１９ａへ制動板３５を接触
させてその回転を制動し、ねじ部材１９を入力軸１に対
し減速方向に相対回転させることに゛より、該ねじ部材
１９をその入力軸１の雄ねじ部１８との螺合により可動
シェイク６が固定シェイク５に向かう方向にねじ送りし
て、駆動プーリ３の有効半径を増大させる一方、第２図
に示すように、切換レバー４０を低速位置に位置付けた
ときには、ねじ部材１９の摩擦部１９ａに入力軸１より
も速い速度で回転している摩擦リング３３を接触させて
その回転を増速し、ねじ部材１９を入力軸１に対して増
速方向に相対回転させることにより、ねじ部材１９を可
動シェイク６が固定シェイク５から離れる方向にねじ送
りして、駆動プーリ３の有効半径を減少させるように構
成されている。A plate-shaped pressure ring 32 is disposed on one side (drive pulley 3 side) of the second toothed boob 929, and a plate-shaped friction ring 33 is disposed on the other side. The friction ring 33 has a large number of pins 34, 3 slidingly passing through the second toothed pulley 29 parallel to the axial direction.
4. . . , and are configured to rotate together with the second toothed pulley 29. Further, a ring plate-shaped friction portion 19a that can come into contact with the friction ring 33 on one side is integrally formed on the outer periphery of the screw member 19, and the friction portion 19a is formed on the other side of the friction portion 19a. A brake plate 35 that can be contacted on the other side is arranged, and the brake plate 35 is supported by a support member 36 and is integrally fixed to the middle part of a rod 37 that moves once in a direction parallel to the input $l11. . One end of the rod 37 extends to a position between the press ring 32 and the movable shake 6 of the drive pulley 3, and its tip presses the press ring 32 through a roller hole 38 toward the friction ring 33. A pressing portion 39 is formed to move the friction ring 33 in the direction (the direction in which the friction ring 33 contacts the friction portion 19a of the screw member 19). On the other hand, a swingable switching lever 40 is connected to the other end of the rod 37 via a link 41 for switching the gear ratio between the input and output fiIi 11 and 2 into two high and low stages. When the screw member 19 is rotated relative to the input shaft 1 in the speed increasing or decelerating direction and the switching lever 40 is positioned at the high speed position as shown in FIG. By bringing the brake plate 35 into contact to brake the rotation and rotating the screw member 19 relative to the input shaft 1 in the deceleration direction, the screw member 19 is screwed into the male threaded portion 18 of the input shaft 1. The movable shaker 6 screws in the direction toward the fixed shaker 5 to increase the effective radius of the drive pulley 3. On the other hand, as shown in FIG. 2, when the switching lever 40 is positioned at the low speed position, the screw member 19 By bringing the friction ring 33 rotating at a faster speed than the input shaft 1 into contact with the friction portion 19a of the input shaft 1 to increase its rotation speed, the screw member 19 is rotated relative to the input shaft 1 in the speed increasing direction. , the movable shaker 6 screws the screw member 19 in the direction away from the fixed shaker 5 to reduce the effective radius of the drive pulley 3.
次に、上記実施例の作動について説明する。Next, the operation of the above embodiment will be explained.
通常の状態では、入力軸１に螺合されているねじ部材１
９の摩擦部１９ａには制動板３５および摩擦リング３３
のいずれも接触せず、ねじ部材１９は入力軸１と速度差
なしで一体的に回転する。Under normal conditions, the screw member 1 screwed onto the input shaft 1
A brake plate 35 and a friction ring 33 are attached to the friction portion 19a of 9.
The screw member 19 rotates integrally with the input shaft 1 without any speed difference.
また、上記ねし部材１９上の第２の歯付プーリ２９には
入ノＪ軸１の回転が第１あにび第２のＶベルトプーリ２
２．２６間のベルト伝動ならびに第１および第２の歯付
プーリ２８．２９間のベルト伝動によって増速されて伝
達されるので、該第２の歯付プーリ２９およびそれにピ
ン３４．３４．・・・により回転一体に連結された摩１
察リング３３は入力軸１と同方向にそれよりも速い回転
速度で回転している。Further, the rotation of the J-axis 1 is input to the second toothed pulley 29 on the screw member 19, and the second V-belt pulley 2
2.26 and the belt transmission between the first and second toothed pulleys 28.29, the second toothed pulley 29 and the pins 34.34. . . . Rotating integrally connected friction 1
The sensing ring 33 is rotating in the same direction as the input shaft 1 at a faster rotational speed.
この状態から、例えば入出力軸１，２間の変速比を増大
させて高速モードにするとぎには、切換レバー４０を第
１図に示す如く高速位置に位置付けると、この切換レバ
ー４０の切換操作に伴い、ロッド３７が図で左方向に摺
動し、このロッド３７に連結されている制動板３５がね
じ部材１９外周の摩擦部１９ａに接触してそのねじ部材
１９の回転を制動し、この制動作用によりねじ部材１９
が入力軸１に対して相対的に減速され、この減速方向の
相対回転によりねじ部材１９が入力ｉ！ｌ１ｌ１１上を
駆動プーリ３に向かう方向にねじ送りされ、そのねじ部
材１９にベアリング２０を介して移動一体に連結されて
いる駆動プーリ３の可動シェイブ６が固定シェイブ５に
近付き、駆動プーリ３の有効半径が増大する。また、こ
の駆動プーリ３の有効半径の増大に伴い、Ｖベルト１７
が全体的に駆動プーリ３側に引ぎ奇ぜられるとともに、
このＶベルト１７の移動により従動プーリ９の可動シェ
イブ１２がスプリング１６の付勢力に抗して固定シェイ
ブ１１から離れる方向に移動し、従動プーリ９の有効半
径が減少する。その結果、駆動プーリ３の有効半径が従
動プーリ９よりも大きくなり、入力軸１の回転が増速さ
れて出力軸２に伝達される。From this state, for example, in order to increase the gear ratio between the input and output shafts 1 and 2 to enter the high speed mode, the switching lever 40 is positioned at the high speed position as shown in FIG. Accordingly, the rod 37 slides to the left in the figure, and the braking plate 35 connected to the rod 37 contacts the friction portion 19a on the outer periphery of the screw member 19 to brake the rotation of the screw member 19. Screw member 19 for braking action
is decelerated relative to the input shaft 1, and this relative rotation in the deceleration direction causes the screw member 19 to input i! The movable shave 6 of the drive pulley 3, which is threaded in the direction toward the drive pulley 3 on l1l11 and is movably connected to the screw member 19 via a bearing 20, approaches the fixed shave 5, and the drive pulley 3 becomes effective. Radius increases. In addition, with the increase in the effective radius of this drive pulley 3, the V-belt 17
is pulled toward the drive pulley 3 as a whole, and
This movement of the V-belt 17 causes the movable sheave 12 of the driven pulley 9 to move away from the fixed sheave 11 against the biasing force of the spring 16, and the effective radius of the driven pulley 9 decreases. As a result, the effective radius of the driving pulley 3 becomes larger than that of the driven pulley 9, and the rotation of the input shaft 1 is accelerated and transmitted to the output shaft 2.
一方、逆に、入出力軸１，２間の変速比を低くして低速
モードにするときには、切換レバー４０を第２図に示す
如く低速位置に位置付けると、この切換レバー４０の切
換操作に伴ってロッド３７が図で右方向に摺動し、この
ロツード３７の端部に設けられている押圧部３９がロー
ラボール３８を介して押圧リング３２を押圧し、該押圧
リング３２に多数のピン３４．３４．・・・により一体
的に連結されている摩擦リング３３が上記摩擦部１９ａ
に接触してねじ部材１９を増速方向に駆動し、この駆動
作用によりねじ部材１９が入力軸１に対して相対的に増
速され、この増速方向の相対回転によりねじ部材１９が
入力軸１上を駆動プーリ３から離れる方向にねじ送りさ
れ、駆動プーリ３の可動シェイブ６が固定シェイブ５か
ら離れる方向に移動して駆動プーリ３の有効半径が減少
する。この駆動プーリ３の有効半径の減少に伴い、Ｖベ
ルト１７がスプリング１６の刊勢力によって全体的に従
動ブー９９側に引き寄せられるとともに、このＶベルト
１７の移動により従動プーリ９の可動シェイブ１２が固
定シェイブ１１に接近し、従動プーリ９の有効半径が増
大する。その結果、駆動プーリ３の有効半径が従動ブー
９９よりも小さくなり、入力軸１の回転が減速されて出
力軸２に伝達される。On the other hand, when lowering the gear ratio between the input and output shafts 1 and 2 to enter the low speed mode, the switching lever 40 is positioned at the low speed position as shown in FIG. The rod 37 slides rightward in the figure, and the pressing part 39 provided at the end of the rod 37 presses the pressing ring 32 via the roller ball 38, and a large number of pins 34 are attached to the pressing ring 32. .34. The friction ring 33 integrally connected to the friction portion 19a by...
This driving action causes the screw member 19 to accelerate relative to the input shaft 1, and this relative rotation in the speed increasing direction causes the screw member 19 to move toward the input shaft. 1 in the direction away from the drive pulley 3, the movable shave 6 of the drive pulley 3 moves in the direction away from the fixed shave 5, and the effective radius of the drive pulley 3 decreases. As the effective radius of the drive pulley 3 decreases, the entire V-belt 17 is drawn toward the driven boob 99 by the force of the spring 16, and the movement of the V-belt 17 fixes the movable shaver 12 of the driven pulley 9. Approaching the shave 11, the effective radius of the driven pulley 9 increases. As a result, the effective radius of the drive pulley 3 becomes smaller than the driven boob 99, and the rotation of the input shaft 1 is decelerated and transmitted to the output shaft 2.
したがって、この場合、入力軸１に螺合支持されたねじ
部材１９外周の摩擦部１９ａに摩擦リング３３または制
動板３５を接触させてねじ部材１９を減速または増速さ
せることにより、入力軸１とねじ部（Ａ１９とを相対回
転させて、この両者の相対回転により、駆動プーリ３の
可動シェイブ６を軸方向に移動させるため、可動シェイ
ブ６に対する駆動＠造が極めて簡単になり、その制御も
容易になる。Therefore, in this case, the friction ring 33 or the brake plate 35 is brought into contact with the friction portion 19a on the outer periphery of the screw member 19 that is threadably supported on the input shaft 1 to decelerate or increase the speed of the screw member 19. The screw portion (A19) is relatively rotated, and the relative rotation between the two moves the movable shaver 6 of the drive pulley 3 in the axial direction, so the drive for the movable shaver 6 is extremely simple, and its control is also easy. become.
しかも、入力軸１とそれに支持されたねじ部材１９との
相対回転を利用して可動シェイブ６を移動させるので、
可動シェイブ６の駆動源として従来の如き高価なサーボ
モータ等が不要であり、よって安価に製作することかで
きる。Moreover, since the movable shaver 6 is moved using the relative rotation between the input shaft 1 and the screw member 19 supported by the input shaft 1,
There is no need for a conventional expensive servo motor or the like as a drive source for the movable shaver 6, and the movable shaver 6 can be manufactured at low cost.
（第２実施例）
第３図および第４図は本発明の第２実施例を示しく尚、
第１図および第２図と同じ部分については同じ符号を付
してその詳細な説明は省略する）、ねじ部材１９′を入
力軸１に対して相対回転させる変速切換は構２１′を遊
星歯車（幾構で構成したものでおる。(Second Embodiment) FIGS. 3 and 4 show a second embodiment of the present invention.
(The same parts as in FIGS. 1 and 2 are denoted by the same reference numerals, and detailed explanations thereof are omitted.) For the gear change that rotates the screw member 19' relative to the input shaft 1, the mechanism 21' is connected to the planetary gear. (It is made up of several parts.
すなわら、本実施例では、ねじ部材１９′ に対して駆
動プーリ３と反対側の入力軸１上には遊星歯車機構４２
が取り付けられている。この遊星歯車機構４２は、入力
軸１にキー４３により回転一体にかつ囲動不能に固定さ
れたサンギヤ４４と、該サンギヤ４４に半部にて噛み合
う複数のピニオン４５，４５．・・・（１個のみ図示す
る）を担持するピニオンキャリア４６とからなり、上記
サンギヤ４４とねじ部材１９′との間の入力軸１上には
上記各ピニオン４５の残り半部に噛み合う出力ギヤ４７
がベアリング４８を介して回転自在に支持され、該出ツ
ノギヤ４７はねじ部材１９′に対し、出力ギヤ４７に固
定したピン４９をねじ部’ｒ；’ｉ １９′に穿設した
ピン挿通孔１９′ ｂに摺動自在に嵌合せしめて回転一
体にかつ接離可能に連結されている。一方、上記ピニオ
ンキャリア４６の外周にはギヤ部４６ａが形成され、該
ギヤ部４６ａには切換レバー４０’の軸部４０’ａに一
体に結合したギヤ５０が噛み合わされており、切換レバ
ー４０′の切換操作によりピニオンキャリア４６の各ピ
ニオン４５をサンギヤ４４上で相対的に回転移動させる
ことにより、入力軸１と一体のサンギヤ４４を出力ギヤ
４７つまりねじ部材１９′に対して相対回転させるよう
にした変速切換殿構２１′が構成されている。That is, in this embodiment, a planetary gear mechanism 42 is provided on the input shaft 1 on the opposite side of the drive pulley 3 with respect to the screw member 19'.
is installed. This planetary gear mechanism 42 includes a sun gear 44 which is rotatably and non-movably fixed to the input shaft 1 by a key 43, and a plurality of pinions 45, 45. ... (only one is shown), and an output gear that meshes with the remaining half of each pinion 45 on the input shaft 1 between the sun gear 44 and the screw member 19'. 47
is rotatably supported via a bearing 48, and the output horn gear 47 has a pin 49 fixed to the output gear 47 attached to the threaded member 19' through a pin insertion hole 19 formed in the threaded part 'r;'i 19'. 'b is slidably fitted and connected to rotate integrally and to be releasable. On the other hand, a gear portion 46a is formed on the outer periphery of the pinion carrier 46, and a gear 50 integrally coupled to the shaft portion 40'a of the switching lever 40' is meshed with the gear portion 46a. By rotating each pinion 45 of the pinion carrier 46 relatively on the sun gear 44 through a switching operation, the sun gear 44 integrated with the input shaft 1 is rotated relative to the output gear 47, that is, the screw member 19'. A transmission switching mechanism 21' is constructed.
したがって、本実施例の場合、切換レバー４０′が非操
作状態にあって、遊星歯車機構４２のピニオンギヤリア
４６が停止しているときには、サンギヤ４４の回転は入
力軸１に対し位置が停止している各ピニオン４５を介し
て出力ギヤ４７に伝達され、このことによりサンギヤ４
４つまり入力軸１と出力ギヤ４７つまりねじ部材１９′
との回転速度は同一となり、ねじ部材１９′は入力軸
１上を軸方向に移動せず、よって人出り軸１，２間の変
速比は一定に保たれる。Therefore, in the case of this embodiment, when the switching lever 40' is in the non-operated state and the pinion gear rear 46 of the planetary gear mechanism 42 is stopped, the rotation of the sun gear 44 is stopped in its position relative to the input shaft 1. is transmitted to the output gear 47 via each pinion 45, which causes the sun gear 4
4, that is, the input shaft 1 and the output gear 47, that is, the screw member 19'
The rotational speeds of the input shafts 1 and 2 are the same, and the screw member 19' does not move in the axial direction on the input shaft 1, so that the gear ratio between the input shafts 1 and 2 is kept constant.
そして、第３図に示すように、切換レバー４０′を高速
位置に切り換えると、この切換操作に伴い、切換レバー
４０’のギヤ５０に噛み合う上記遊星歯車機構４２のピ
ニオンキャリア４６が入力軸１の回転方向と逆方向に回
動して各ピニオン４５の位置が入力軸１に対して回動し
、この各ピニオン４５の位置の移動によりその移動分だ
けサンギヤ４４と出力ギヤ４７との回転数に差が生じて
ねじ部材１９′が入力ｆｉＩｌ１１に対し減速方向に相
対回転し、このことによりねじ部材１９′が該ねじ部材
１９′ にピン４９により連結されている可動シェイブ
６と共に図で左方向に移動して駆動プーリ３の有効半径
が増大し、入出力１ｆ１１１，２間の変速比か増大する
。Then, as shown in FIG. 3, when the switching lever 40' is switched to the high speed position, the pinion carrier 46 of the planetary gear mechanism 42 that meshes with the gear 50 of the switching lever 40' is moved to the input shaft 1. The position of each pinion 45 rotates in the opposite direction to the rotation direction, and the position of each pinion 45 rotates with respect to the input shaft 1. As the position of each pinion 45 moves, the rotational speed of sun gear 44 and output gear 47 increases by the amount of the movement. Due to the difference, the screw member 19' rotates relative to the input fiIl11 in the deceleration direction, which causes the screw member 19' to move to the left in the figure together with the movable shaver 6 connected to the screw member 19' by a pin 49. As it moves, the effective radius of the drive pulley 3 increases, and the gear ratio between the input and output 1f111 and 1f2 increases.
一方、第４図に示すように、切換レバー４０’を低速位
置に切り換えたとぎには、上記遊星歯車機構４２のピニ
オンキャリア４６は上記高速モード時とｌは逆方向に回
動して、ねじ部材１９′が入力軸１に対して増速方向に
相対回転し、このことによって可動シェイブ６が固定シ
ェイブ５から離れる方向に移動して駆動プーリ３の有効
半径が減少し、入出力軸１，２間の変速比が減少する。On the other hand, as shown in FIG. 4, when the switching lever 40' is switched to the low speed position, the pinion carrier 46 of the planetary gear mechanism 42 rotates in the opposite direction to the high speed mode, and the pinion carrier 46 rotates in the opposite direction to the high speed mode. The member 19' rotates relative to the input shaft 1 in the speed increasing direction, which causes the movable shaver 6 to move away from the stationary shaver 5 and reduce the effective radius of the drive pulley 3, causing the input and output shafts 1, The gear ratio between the two decreases.
よって、本実施例でも上記第１実施例と同様の作用効果
を奏することができる。Therefore, this embodiment can also provide the same effects as the first embodiment.
尚、上記各実施例では、入力軸１に雄ねじ部１８を直接
形成して該雄ねじ部１８にねじ部材１９゜１９′を螺合
するようにしているが゛、第５図に拡大して示すように
、入力軸１′に外周に雄ねじ部５１ａを有する補助ねじ
部材５１を一体的に固定し、該補助ねじ部材５１に駆動
プーリ３の可動シェイブ６に軸方向に移動一体に連結さ
れるねじ部材１９″を螺合するようにしてもよい。第５
図中、５２は駆動プーリ３のベルト溝８底部に相当する
入力軸１′上に設けられたベアリングで、駆動プーリ３
の有効半径が最小になったとぎにベルト満８底部に移動
するＶベルト１７を支持するものである。In each of the above embodiments, the male threaded portion 18 is directly formed on the input shaft 1, and the threaded member 19° 19' is screwed into the male threaded portion 18, but this is shown enlarged in FIG. , an auxiliary screw member 51 having a male threaded portion 51a on the outer periphery is integrally fixed to the input shaft 1', and a screw is integrally connected to the auxiliary screw member 51 so as to be movable in the axial direction with the movable shaver 6 of the drive pulley 3. The member 19'' may be screwed together.Fifth
In the figure, 52 is a bearing provided on the input shaft 1' corresponding to the bottom of the belt groove 8 of the drive pulley 3.
This supports the V-belt 17, which moves to the bottom when the effective radius of the belt becomes the minimum.
また、上記各実施例では、ねじ部＋Ｊ’１９．１９′を
入力軸１に対して減速方向に相対回転させると、ねじ部
材１９．１９’が駆動プーリ３から離れる方向にねじ送
りされるように構成されているが、ねじの向きを逆にす
ることにより、ねじ部材のパノＪ軸に対する減速方向の
相対回転に伴ってねじ部材が駆動プーリに近付く方向に
ねじ送りされるようにしてもよいのはいうまでもないこ
とである。Furthermore, in each of the above embodiments, when the threaded portion +J'19.19' is rotated relative to the input shaft 1 in the deceleration direction, the threaded member 19.19' is threaded in the direction away from the drive pulley 3. However, by reversing the direction of the screw, the screw member may be screw-fed in the direction closer to the drive pulley as the screw member rotates relative to the pano J axis in the deceleration direction. It goes without saying that.
さらに、上記各実施例では、入力軸１上に設（プられる
駆動プーリ３の可動シェイブ６をねじ部材１９．１９’
によって移動させるようにしたが、逆に、出力軸２上
の従動プーリ９にあける可動シェイブ１２をねじ送りし
て移動させるようにしてもよく、上記各実施例と同様の
作用効果を秦することができる。Further, in each of the above embodiments, the movable shaver 6 of the drive pulley 3 installed on the input shaft 1 is connected to the screw member 19, 19'.
However, conversely, the movable shaver 12 formed in the driven pulley 9 on the output shaft 2 may be moved by screw feeding, and the same effect as in each of the above embodiments can be obtained. Can be done.
（第３実施例）
第６図および第７図は第３実施例を示し、この実施例で
は、上記第２実施例の構成において、駆動プーリ３の可
動シェイブ６をねじ部材１９′のねじ送りによって軸方
向に移動させるのではなく、カム機構によって移動させ
るように変更したものでおる。(Third Embodiment) FIGS. 6 and 7 show a third embodiment. In this embodiment, in the structure of the second embodiment, the movable shaver 6 of the drive pulley 3 is moved by the screw feed of the screw member 19'. Instead of being moved in the axial direction by a cam mechanism, it is moved by a cam mechanism.
すなわち、駆動プーリ３にあける可動シ１イブ６のボス
部６ａには移動部材としての円筒状の従動カム５１が回
転一体に外嵌合されている。また、上記可動シェイブ６
に対し固定シェイブ５と反対側の入力軸１上には上記第
２実施例と同様の遊星歯車は構４２が設けられ、該遊星
歯車機構４２の出力ギヤ４７′ は上記従動カム５１を
押圧する駆動カムを構成している。そして、第７図に詳
示するように、上記駆動カムつまり出力ギヤ４７′およ
び従動カム５１は各々相手側に向かう方向に突出するカ
ム部４７’ ａ、５１ａを備え、これらカム部４７’
ａ、５１ａは筒体を中間位置で斜めに切断分割したと
きの各分割部分と同様の形状に設けられ、各カム部４７
’ ａ、５１ａの先端には互いにカム接触する傾斜カ
ム面４７’ ｂ、５１ｂが形成されており、切換レバ
ー４０’の操作により遊星歯車機構４２の出力ギヤ４７
′（駆動カム〉を入力軸１回りに相対的に回動ざゼて、
その従動カム５１との相対回転差によってカム部４７′
ａ先端の傾斜カム面４７′ ｂで従動カム５１のカム部
５１ａ先端の傾斜カム面５１ｂを押圧することにより、
その従動カム５１を駆動プーリ３の可動シェイブ６と共
に入力軸１の軸方向に移動させて、駆動プーリ３の有効
半径を増大変化させるように構成されている。That is, a cylindrical driven cam 51 as a moving member is externally fitted onto the boss portion 6a of the movable sheave 6 provided in the drive pulley 3 so as to rotate integrally therewith. In addition, the movable shave 6
On the other hand, a planetary gear mechanism 42 similar to that of the second embodiment is provided on the input shaft 1 on the opposite side from the fixed shave 5, and the output gear 47' of the planetary gear mechanism 42 presses the driven cam 51. It constitutes a drive cam. As shown in detail in FIG. 7, the drive cam, that is, the output gear 47' and the driven cam 51 each have cam portions 47'a and 51a that protrude toward the other side, and these cam portions 47'
a, 51a are provided in the same shape as each divided portion when the cylinder is cut and divided diagonally at an intermediate position, and each cam portion 47
Slanted cam surfaces 47'b and 51b that come into cam contact with each other are formed at the tips of 'a' and 51a, and the output gear 47 of the planetary gear mechanism 42 is switched by operating the switching lever 40'.
'(Drive cam) is rotated relatively around the input shaft,
Due to the relative rotation difference with the driven cam 51, the cam portion 47'
By pressing the inclined cam surface 47'b at the tip of the cam portion 51a of the driven cam 51 with the inclined cam surface 47'b at the tip a,
The driven cam 51 is moved in the axial direction of the input shaft 1 together with the movable shaver 6 of the drive pulley 3 to increase and change the effective radius of the drive pulley 3.
したがって、この実施例においては、切換レバー４０′
の操作により遊星歯車間＠４２のピニオンキャリア４６
が入力軸１の回転方向と逆方向に回動して各ピニオン４
５の位置が入力！１ＩＩｌ１１に対して回動し、この各
ピニオン４５の位置の移動によりその移動部だけサンギ
ヤ４４と出力ギヤ４７′との回転数、つまり該ナンキャ
４４に入力軸１を介して回転一体に連結された駆動プー
リ３の可動シェイブ６および従動カム５１と上記出カギ
１１７４７′により構成される駆動カムとの回転数に差
が牛し、この回転差により各カム部４７’ ａ、５１
ａ先端の傾斜カム面４７’ ｂ、５１ｂ同士て接触し
ている従動カム５１が押圧されまたはＶベルト１７の張
力により引き戻されて出ツノギヤ４７′（駆動カム）に
対し接離するように入力軸１上を移動し、この従動カム
５１に移動一体に連結されている駆動プーリ３の可動シ
ェイブ６が同方向に移動して固定シェイブ５に対し接離
し、このことにより駆動プーリ３のベルト濶８の間隔つ
まり有効半径が増減変更される。Therefore, in this embodiment, the switching lever 40'
Pinion carrier 46 between planetary gears @ 42 by operation of
rotates in the opposite direction to the rotation direction of the input shaft 1, and each pinion 4
Position 5 is input! 1IIl11, and by the movement of the position of each pinion 45, only the moving part changes the rotational speed of the sun gear 44 and output gear 47', that is, the number of revolutions of the sun gear 44 and the output gear 47', which are rotationally integrally connected to the Nan gear 44 via the input shaft 1. There is a difference in the rotational speed between the movable shaver 6 and the driven cam 51 of the drive pulley 3 and the drive cam constituted by the output key 11747', and this rotational difference causes each cam portion 47'a, 51
The input shaft is moved so that the driven cam 51, which is in contact with the inclined cam surface 47' at the tip of a, b and 51b, is pressed or pulled back by the tension of the V-belt 17 and moves toward and away from the protruding horn gear 47' (drive cam). The movable shave 6 of the driving pulley 3, which is movably connected to the driven cam 51, moves in the same direction and approaches and separates from the fixed shave 5, thereby causing the belt grip 8 of the driving pulley 3 to move in the same direction. The interval, or effective radius, is increased or decreased.
よって、この実施例の場合、上記第２実施例と同様の作
用効果を奏することができる。加えて、ねじ部材１９′
を使用する場合に比へ、遊星歯車１１４２のピニオンキ
ャリア４６つまり切換レバー４０′ を小さく回動させ
て駆動プーリ３の可動シェイブ６を同等の量だけ移動さ
せることができ、しかもカム機構によって潤滑部分を簡
略化できる利点がおる。Therefore, in the case of this embodiment, the same effects as in the second embodiment can be achieved. In addition, the screw member 19'
In contrast, when using the pinion carrier 46 of the planetary gear 1142, that is, the switching lever 40', the movable sheave 6 of the drive pulley 3 can be moved by the same amount by slightly rotating the pinion carrier 46 of the planetary gear 1142, and the lubricated part can be moved by the cam mechanism. This has the advantage of simplifying the process.
尚、本発明では、変速切換ハ椙として、上記各実施例の
如き構造のものの他、各種の公知の変速手段が採用可能
である。In the present invention, various known speed change means can be employed as the speed change switch, in addition to those having the structure as in each of the above-mentioned embodiments.
（発明の効果）
以上説明したように、本発明によると、回転軸上におけ
る可変プーリの可動シェイブに軸方向に移動一体に連結
され、回転軸との相対回転によりねじ送り等されて軸方
向に移動７′ｉＪ能な移動部材を設け、この移動部材を
変速切換機構ににつて回転軸に対し相対回転させ、可動
シェイブを軸方向に移動させて固定シェイブに対し接離
させ、両シェイブ間に巻き掛けられるベルト部材に対す
る有効半径を可変調整するようにしたことにより、回転
軸とそれに支持された移動部材との相対回転を効果的に
利用して可変ブー１ノの可動シ■イブを軸方向に移動さ
せることができ、可変プーリにおける可動シェイブの駆
動構造が極めて筒単になり、その制御も容易になるとと
もに、従来のようなザーボモータ等が不要で安価に製作
することができるものである。(Effects of the Invention) As explained above, according to the present invention, the variable pulley is integrally connected to the movable shaver on the rotating shaft so as to be movable in the axial direction, and is moved in the axial direction by screw feeding or the like by relative rotation with the rotating shaft. A movable member capable of moving 7'iJ is provided, and this movable member is rotated relative to the rotating shaft by the speed change switching mechanism, and the movable shaver is moved in the axial direction to move toward and away from the fixed shaver, and the movable shaver is moved toward and away from the fixed shaver. By variably adjusting the effective radius of the belt member around which it is wound, the relative rotation between the rotating shaft and the movable member supported by it is effectively used to move the movable sheave of the variable boot 1 in the axial direction. The drive structure of the movable shaver in the variable pulley becomes extremely simple, and its control becomes easy. It also eliminates the need for conventional servo motors and can be manufactured at low cost.
第１図および第２図は本発明の第１実施例を示すもので
、第１図は高速モード時における変速装買の全体構成図
、第２図は同低速モード時の全体構成図である。第３図
および第４図はそれぞれ第２実施例における第１図およ
び第２図相当図で必る。第５図はねじ部材の変形例を示
す拡大断面図でおる。第６図は第３実施例を示す要部拡
大断面図、第７図はカム機構の詳細構造を示す正面図で
ある。
１．１′・・・入力軸、２・・・出力軸、３・・・駆動
プーリ、５・・・固定シェイブ、６・・・可動シェイブ
、９・・・従動プーリ、１７・・・Ｖベルト、１９．１
９’ 、１９″・・・ねじ部材、１９ａ・・・摩ｉ寮部
、２１．２１’・・・変速切換渫Ｈ，５，３３・・・摩
１寮リング、３５・・・制動仮、４０．４０’ ・・・
切換レバー、４２・・・遊星歯車Ｒ肴、４４′・・・出
力ギヤ（駆動カム）、５１・・・従動カム。Figures 1 and 2 show a first embodiment of the present invention; Figure 1 is an overall configuration diagram of the transmission equipment in high speed mode, and Figure 2 is an overall configuration diagram of the transmission equipment in low speed mode. . 3 and 4 correspond to FIGS. 1 and 2 in the second embodiment, respectively. FIG. 5 is an enlarged sectional view showing a modified example of the screw member. FIG. 6 is an enlarged cross-sectional view of the main part showing the third embodiment, and FIG. 7 is a front view showing the detailed structure of the cam mechanism. 1.1'... Input shaft, 2... Output shaft, 3... Drive pulley, 5... Fixed shave, 6... Movable shave, 9... Driven pulley, 17... V Belt, 19.1
9', 19''...Screw member, 19a...Miryo part, 21.21'...Speed change switch H, 5, 33...Mariyo ring, 35...Brake temporary, 40.40'...
Switching lever, 42... Planetary gear R side, 44'... Output gear (drive cam), 51... Followed cam.
Claims (1)
定シェイブと、回転軸に軸方向に摺動自在にかつ回転一
体に支持された可動シェイブとを備え、上記可動シェイ
ブを固定シェイブに対し接離させて両シェイブ間に巻き
掛けられるベルト部材に対する有効半径を可変とした可
変プーリ装置において、上記回転軸上に支持されるとと
もに、上記可動シェイブに軸方向に移動一体にかつ回転
自在に連結され、回転軸との相対回転により軸方向に移
動可能な移動部材と、該移動部材を回転軸に対して相対
回転させる変速切換機構とを設けたことを特徴とする可
変プーリ装置。(1) A fixed shave that is rotatably and non-slidably fixed to a rotating shaft, and a movable shave that is slidably and rotatably supported to the rotating shaft in the axial direction, and the movable shave is fixed to the rotating shaft. In a variable pulley device that has a variable effective radius for a belt member that is wound between both shavers while moving toward and away from the shaft, the pulley device is supported on the rotating shaft, and is movable integrally with and rotatable in the axial direction of the movable shaver. A variable pulley device comprising: a moving member connected to the rotary shaft and movable in the axial direction by relative rotation with the rotating shaft; and a speed change switching mechanism that rotates the moving member relative to the rotating shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62045979A JPH0612142B2 (en) | 1986-10-16 | 1987-02-28 | Variable pulley device |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61-246083 | 1986-10-16 | ||
| JP24608386 | 1986-10-16 | ||
| JP62045979A JPH0612142B2 (en) | 1986-10-16 | 1987-02-28 | Variable pulley device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63225753A true JPS63225753A (en) | 1988-09-20 |
| JPH0612142B2 JPH0612142B2 (en) | 1994-02-16 |
Family
ID=26386076
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62045979A Expired - Fee Related JPH0612142B2 (en) | 1986-10-16 | 1987-02-28 | Variable pulley device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0612142B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6383102B1 (en) * | 1999-07-21 | 2002-05-07 | Tokyo Automatic Machinery Co., Ltd. | Belt pressing mechanism for continuously variable transmission |
| US6398680B1 (en) * | 2000-06-09 | 2002-06-04 | Tokyo Automatic Machinery Co., Ltd. | Continuously variable transmission |
| JP2006511764A (en) * | 2002-12-23 | 2006-04-06 | ファン ドールネズ トランスミッシー ビー．ブイ． | Continuously variable transmission |
| CN101818792A (en) * | 2009-02-28 | 2010-09-01 | 本田技研工业株式会社 | The V variable v-belt drive |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6171526U (en) * | 1984-10-17 | 1986-05-15 |
-
1987
- 1987-02-28 JP JP62045979A patent/JPH0612142B2/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6171526U (en) * | 1984-10-17 | 1986-05-15 |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6383102B1 (en) * | 1999-07-21 | 2002-05-07 | Tokyo Automatic Machinery Co., Ltd. | Belt pressing mechanism for continuously variable transmission |
| US6398680B1 (en) * | 2000-06-09 | 2002-06-04 | Tokyo Automatic Machinery Co., Ltd. | Continuously variable transmission |
| US6669589B2 (en) * | 2000-06-09 | 2003-12-30 | Tokyo Automatic Machinery Co., Ltd. | Continuously variable transmission |
| JP2006511764A (en) * | 2002-12-23 | 2006-04-06 | ファン ドールネズ トランスミッシー ビー．ブイ． | Continuously variable transmission |
| CN101818792A (en) * | 2009-02-28 | 2010-09-01 | 本田技研工业株式会社 | The V variable v-belt drive |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0612142B2 (en) | 1994-02-16 |
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