JP2620418B2

JP2620418B2 - Transmission

Info

Publication number: JP2620418B2
Application number: JP3054942A
Authority: JP
Inventors: 博文宮田
Original assignee: Bando Chemical Industries Ltd
Current assignee: Bando Chemical Industries Ltd
Priority date: 1991-03-19
Filing date: 1991-03-19
Publication date: 1997-06-11
Anticipated expiration: 2012-06-11
Also published as: JPH0599290A

Description

DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【産業上の利用分野】この発明は、ベルトに対するプー
リの有効径を変えて１対の回転軸間の変速比を変化させ
るようにしたベルト式変速装置の改良に関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a belt-type transmission which changes an effective diameter of a pulley with respect to a belt to change a speed ratio between a pair of rotating shafts.

【０００２】[0002]

【従来の技術】従来より、この種のベルト式変速装置は
伝動装置として広く採用されている。その１例として、
互いに平行に配置された１対の回転軸の各々に、回転軸
に対して回転一体にかつ摺動不能に固定された固定シー
ブと、各軸に可動シーブとの間にＶ字状のベルト溝を形
成するように対向配置されて回転一体にかつ摺動可能に
支持された可動シー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を巻
き掛け、各可変プーリの可動シーブを軸方向に移動させ
て固定シーブに接離させ、両シーブ間のベルト溝に巻き
掛けられるベルトに対する有効半径を変えることによ
り、両回転軸間の変速比を可変制御するようにしたもの
は知られている。2. Description of the Related Art Heretofore, this type of belt type transmission has been widely adopted as a transmission. As one example,
A V-shaped belt groove is provided between each of a pair of rotating shafts arranged in parallel with each other, and a fixed sheave fixed integrally and non-slidably with respect to the rotating shaft and a movable sheave on each shaft. And a variable pulley composed of a movable sheave which is arranged opposite to each other and is rotatably integrated and slidably supported, and a belt is wound between belt grooves of both of the variable pulleys so that each variable pulley is movable. The gear ratio between the two rotating shafts is variably controlled by moving the sheave in the axial direction, moving the sheave into and out of contact with the fixed sheave, and changing the effective radius of the belt wound around the belt groove between the sheaves. Are known.

【０００３】このベルト式変速装置においては、一般的
に、一方の回転軸上の可変プーリを駆動プーリとし、そ
の可動シーブを例えば油圧やカム機構を利用した駆動機
構によって軸方向に移動させることにより、その駆動プ
ーリの有効径を変える一方、他方の回転軸上の可変プー
リは従動プーリとし、その可動シーブをスプリングのば
ね力によって固定シーブ側に付勢して、上記駆動プーリ
の有効径の変化に伴うベルトの位置変動に応じて従動プ
ーリの有効径を自動的に調整するようになされている。In this belt type transmission, generally, a variable pulley on one of the rotating shafts is used as a driving pulley, and the movable sheave is moved in the axial direction by a driving mechanism using, for example, hydraulic pressure or a cam mechanism. The effective diameter of the driving pulley is changed while the variable pulley on the other rotating shaft is a driven pulley, and the movable sheave is urged toward the fixed sheave by the spring force of the spring to change the effective diameter of the driving pulley. The effective diameter of the driven pulley is automatically adjusted in accordance with the change in the position of the belt caused by the rotation.

【０００４】しかし、このように従動プーリの可動シー
ブにスプリングによって付勢力を与える場合には種々の
問題が生じることから、本出願人は、前に、駆動及び従
動プーリの可動シーブ背面側にそれぞれ該可動シーブを
駆動するカム機構を配設し、両カム機構を互いに連動さ
せる変速切換機構を設け、ベルトの緩み側スパンを所定
の押圧力で押圧することにより、互いに同期して逆方向
に開閉する両プーリ間の開閉推力を部分的に相殺し合
い、その残りを変速操作力として、変速操作力を軽減で
きるようにしたものを提案している（特願昭６２―１９
４１１０明細書及び図面参照）。However, in the case where a biasing force is applied to the movable sheave of the driven pulley by a spring as described above, various problems occur. A cam mechanism for driving the movable sheave is provided, a speed changeover mechanism for interlocking both cam mechanisms is provided, and the loose side span of the belt is pressed with a predetermined pressing force to open and close in the opposite direction in synchronization with each other. The present invention proposes a device in which the opening / closing thrust between the two pulleys is partially cancelled, and the remainder is used as a shift operation force to reduce the shift operation force (Japanese Patent Application No. 62-19 / 1987).
4110 specification and drawings).

【０００５】[0005]

【発明が解決しようとする課題】ところで、例えば、車
両においてエンジンにより駆動される補機（例えば発電
用オルタネータ）の回転速度を上記の如きベルト式変速
装置で制御することが注目されている。すなわち、エン
ジンはアイドリング域から高回転域まで広い回転域で回
転するが、変速比をベルト式変速装置で無段階に切り換
えることで、上記のようなエンジンの回転変動に拘ら
ず、補機を略一定の速度で回転させることができる。こ
の場合、変速装置の変速比を制御するアクチュエータと
して、電動モータ、エンジン駆動により発生する作動油
を受ける油圧シリンダ、エンジン回転による遠心力を利
用するカム機構、吸気負圧を導入するダイアフラム装置
等があるが、通常、吸気負圧は、エンジン（ガソリンエ
ンジン）であれば必ず発生し、スロットル弁に対して敏
感に反応し、最大となるのが減速時又はアイドリング時
であり、エンジンの運転中でないと発生しないという特
性を持っていて、車両への適用が容易である等の利点が
あることから、ダイアフラム装置が採用される。By the way, for example, attention has been paid to controlling the rotational speed of an auxiliary device (for example, an alternator for power generation) driven by an engine in a vehicle by the above-mentioned belt type transmission. That is, the engine rotates in a wide rotation range from the idling range to the high rotation range, but by changing the gear ratio steplessly with a belt type transmission, regardless of the engine rotation fluctuation as described above, the auxiliary equipment is substantially It can be rotated at a constant speed. In this case, as an actuator for controlling the transmission ratio of the transmission, an electric motor, a hydraulic cylinder for receiving hydraulic oil generated by engine driving, a cam mechanism using centrifugal force due to engine rotation, a diaphragm device for introducing intake negative pressure, and the like are used. However, normally, the intake negative pressure always occurs in an engine (gasoline engine), reacts sensitively to a throttle valve, and the maximum is at the time of deceleration or idling, and is not during operation of the engine. The diaphragm device is adopted because it has a characteristic that it does not occur, and has advantages such as easy application to a vehicle.

【０００６】しかし、反面では、ダイアフラム装置の出
力は小さいものであり、この出力不足を補うために、ダ
イアフラム装置自体が大型にならざるを得ず、車両への
搭載性で問題がある。これらの点で、変速装置の操作力
はより小さいことが要求されるが、上記提案のもので
も、操作力の低減が十分とは言えず、さらに改良の余地
があった。However, on the other hand, the output of the diaphragm device is small, and in order to compensate for this output shortage, the diaphragm device itself has to be large in size, and there is a problem in mountability on a vehicle. In these respects, it is required that the operating force of the transmission be smaller, but even with the above proposal, the operating force cannot be reduced sufficiently, and there is room for further improvement.

【０００７】すなわち、上記提案のものについて、駆動
側及び従動側にそれぞれ発生する推力の関係を具体的に
示すと図１０のようになり、変速操作力として駆動側の
荷重（駆動側発生推力）から従動側荷重（従動側発生推
力）を引いた差よりも大きな外力を与えることで、変速
操作することができる。従って、両発生推力の差を小さ
くして、駆動側発生推力が従動側発生推力よりも若干大
きい理想状態（図１０のＩ線で示す）にすることが操作
力の大幅な低減に繋がる。しかし、実際には、変速装置
の低速状態（同Ｌ線で示す）、中速状態（同Ｍ線で示
す）及び高速状態（同Ｈ線で示す）のいずれでも常に駆
動側発生推力が従動側発生推力よりもかなり大きくなっ
ており、操作力が依然として大きいことが判る。尚、図
１０のＢ線は駆動側発生推力と従動側発生推力とが等し
いバランス状態を示している。Specifically, the relationship between the thrust generated on the driving side and the thrust generated on the driven side is specifically shown in FIG. 10, and the load on the driving side (driving side generated thrust) is used as the shift operation force. By applying an external force larger than the difference obtained by subtracting the driven-side load (the driven-side generated thrust) from, the shift operation can be performed. Therefore, reducing the difference between the two generated thrusts to make the driving-side generated thrust slightly larger than the driven-side generated thrust in an ideal state (shown by the I line in FIG. 10) leads to a significant reduction in the operating force. However, in practice, the thrust generated on the driving side is always constant in the low speed state (shown by the L line), the medium speed state (shown by the M line), and the high speed state (shown by the H line) of the transmission. It is much larger than the generated thrust, indicating that the operating force is still large. The line B in FIG. 10 indicates a balanced state in which the driving-side generated thrust and the driven-side generated thrust are equal.

【０００８】本発明は斯かる諸点に鑑みてなされたもの
で、その目的は、上記変速装置の操作力をさらに低減す
る手段を講じることで、駆動側発生推力と従動側発生推
力との関係を理想状態に近付け得るようにし、エンジン
の吸気負圧を利用するダイアフラム装置であっても、そ
れを大型化することなく、容易に変速できるようにする
ことにある。The present invention has been made in view of the above-mentioned points, and an object of the present invention is to provide a means for further reducing the operating force of the above-described transmission so that the relationship between the driving-side generated thrust and the driven-side generated thrust is improved. It is an object of the present invention to provide a diaphragm device that can approach an ideal state and that can easily shift gears without increasing the size of a diaphragm device that utilizes negative pressure of intake air of an engine.

【０００９】[0009]

【課題を解決するための手段】上記の目的を達成するた
めに、請求項１の発明では、上記提案の変速装置におい
て、駆動側及び従動側にそれぞれ発生する推力の差が変
速操作力として関与していることに着目し、駆動プーリ
の可動シーブと回転軸とを係止部材及びそれと係合する
傾斜係合溝により相対回転可能に係合させて、両者の相
対回転により新たな推力を発生させ、この推力により駆
動側発生推力を低減してその従動側発生推力との差を小
さくすることにより、操作力を低減するようにした。In order to achieve the above object, according to the first aspect of the present invention, in the proposed transmission, the difference between the thrust generated on the driving side and the thrust generated on the driven side is involved as the shifting operation force. The movable sheave of the drive pulley and the rotating shaft are relatively rotatably engaged by the locking member and the inclined engaging groove engaged with the locking member, and a new thrust is generated by the relative rotation of both. The driving force is reduced by reducing the difference between the driving-side generated thrust and the driven-side generated thrust, thereby reducing the operating force.

【００１０】具体的には、この発明では、互いに平行に
配置された１対の回転軸上にそれぞれ設けられ、各々、
回転軸に回転一体にかつ摺動不能に固定された固定シー
ブ、及び該固定シーブとの間にベルト溝を形成するよう
に、回転軸に軸方向に摺動可能に支持された可動シーブ
からなる駆動及び従動プーリと、これら駆動及び従動プ
ーリのベルト溝間に巻き掛けられたベルトとを備え、各
プーリの可動シーブを相対向する固定シーブに対し接離
させて各プーリのベルトに対する有効半径を変化させる
ことにより、両回転軸間の変速比を可変とした変速装置
が前提である。Specifically, according to the present invention, a plurality of rotating shafts are provided on a pair of rotating shafts arranged in parallel with each other.
A fixed sheave is fixed to the rotating shaft so as to be integrally rotatable and non-slidable, and a movable sheave is slidably supported in the axial direction on the rotating shaft so as to form a belt groove between the fixed sheave and the fixed sheave. A drive and driven pulley, and a belt wound between belt grooves of the drive and driven pulleys. The movable sheave of each pulley is moved toward and away from the opposing fixed sheave to reduce the effective radius of each pulley to the belt. The transmission is premised on changing the transmission ratio between both rotating shafts by changing the transmission ratio.

【００１１】そして、上記駆動及び従動プーリの各可動
シーブ背面側にそれぞれ配置され、各々、端部に傾斜カ
ム面を有しかつ回転軸と同心円筒状の第１カムと、端部
に上記第１カムの傾斜カム面に摺接する摺接部を有しか
つ回転軸と同心円筒状の第２カムとからなり、上記第１
及び第２カムの一方が可動シーブに軸方向に移動一体に
かつ相対回転可能に連結され、他方が回転軸の軸方向に
移動不能にかつ相対回転可能に配置され、両カムの一方
は回転軸回りに回動可能な回動カムとされる一方、他方
は固定体に連結されて回動不能な固定カムとされ、上記
回動カムの固定カムとの相対回転により可動シーブを固
定シーブに接近するように移動させる駆動及び従動側カ
ム機構を設ける。The drive and driven pulleys are respectively arranged on the back side of the movable sheaves, each of which has an inclined cam surface at one end and a cylindrical cam concentric with the rotating shaft, and the other end has the first cam. A first cam having a sliding portion which is in sliding contact with the inclined cam surface of one cam, and having a rotary shaft and a concentric cylindrical second cam;
And one of the second cams is connected to the movable sheave so as to move integrally in the axial direction and so as to be relatively rotatable, and the other is arranged so as to be immovable and relatively rotatable in the axial direction of the rotary shaft, and one of the two cams is The rotating cam is rotatable around, while the other is connected to a fixed body to form a non-rotatable fixed cam. The movable sheave approaches the fixed sheave by the relative rotation of the rotating cam with the fixed cam. And a driving and driven cam mechanism for moving the driven cam.

【００１２】また、上記駆動及び従動プーリの一方の可
動シーブが対向する固定シーブに接近すると他方の可動
シーブが対向する固定シーブから離れるように上記両カ
ム機構の回動カムを互いに連係して回動させて、両回転
軸間の変速比を変化させる変速切換機構を設ける。When one movable sheave of the driving and driven pulley approaches the opposing fixed sheave, the rotating cams of the two cam mechanisms are rotated in conjunction with each other so that the other movable sheave moves away from the opposing fixed sheave. A speed changeover mechanism for changing the speed change ratio between the two rotating shafts.

【００１３】さらに、上記駆動及び従動プーリ間に配置
され、両プーリ間に巻き掛けられるベルトの緩み側スパ
ンを該ベルトが各プーリのベルト溝に食い込むように押
圧するベルト押圧機構を設ける。Further, there is provided a belt pressing mechanism disposed between the driving and driven pulleys and pressing the loose side span of the belt wound between the two pulleys so that the belt bites into the belt groove of each pulley.

【００１４】また、上記駆動側回転軸の外周又は駆動プ
ーリにおける可動シーブのボス部内周の一方に突設され
た係止部材と、他方に回転軸の軸心に対し傾斜して形成
され、上記係止部材に係合する係合溝とからなり、駆動
側回転軸に伝動トルクが働いたときに回転軸の駆動プー
リの可動シーブとの相対回転により、上記ベルト押圧機
構によるベルトの押圧により駆動及び従動プーリの各可
動シーブにそれぞれ発生する駆動側及び従動側推力の差
を低減するように、可動シーブを固定シーブに接近させ
る推力を発生させる駆動側推力発生機構を設けたことを
特徴とする。A locking member protruding from one of the outer periphery of the driving-side rotary shaft or the inner periphery of the boss portion of the movable sheave in the driving pulley; and the other being formed to be inclined with respect to the axis of the rotating shaft. The belt pressing device comprises an engaging groove which engages with the locking member, and when the transmission torque is applied to the drive-side rotating shaft, the rotating shaft rotates relative to the movable sheave of the driving pulley, thereby causing the belt pressing machine to rotate.
Driving and driven pulleys can be set by pressing the belt
Difference between driving and driven thrust generated in dynamic sheave
And a drive-side thrust generating mechanism for generating a thrust for moving the movable sheave closer to the fixed sheave so as to reduce the force.

【００１５】請求項２の発明では、駆動側推力発生機構
を上記請求項１の発明の構成に代えてトルクカムで構成
する。According to a second aspect of the present invention, the drive-side thrust generating mechanism is constituted by a torque cam instead of the structure of the first aspect of the present invention.

【００１６】つまり、この発明では、駆動側推力発生機
構は、駆動側回転軸の外周又は駆動プーリにおける可動
シーブのボス部の一方に回転一体に設けられた摺接部材
と、他方に一体的に設けられ、上記摺接部材に摺接する
カム面を有するトルクカムとからなり、駆動側回転軸に
伝動トルクが働いたときに回転軸の駆動プーリの可動シ
ーブとの相対回転により、ベルト押圧機構によるベルト
の押圧により駆動及び従動プーリの各可動シーブにそれ
ぞれ発生する駆動側及び従動側推力の差を低減するよう
に、可動シーブを固定シーブに接近させる推力を発生さ
せるように構成されている。In other words, in the present invention, the driving-side thrust generating mechanism is provided with a sliding contact member provided integrally with the outer periphery of the driving-side rotating shaft or one of the boss portions of the movable sheave in the driving pulley, and integrally with the other. And a torque cam having a cam surface slidingly contacting the sliding contact member. The belt is driven by a belt pressing mechanism by a relative rotation of a driving pulley of the rotating shaft with a movable sheave when a transmission torque acts on the driving side rotating shaft.
To the movable sheaves of the drive and driven pulleys
To reduce the difference between the driving and driven thrusts that occur.
In addition, a thrust for causing the movable sheave to approach the fixed sheave is generated.

【００１７】請求項３の発明では、推力発生機構を従動
側に設けて従動側発生推力を増大させ、その駆動側発生
推力との差を低減するようにした。According to the third aspect of the present invention, the thrust generating mechanism is provided on the driven side to increase the driven-side generated thrust and reduce the difference from the driving-side generated thrust.

【００１８】すなわち、この発明では、上記請求項１の
発明の変速装置において、駆動側推力発生機構に代え、
従動側回転軸の外周又は従動プーリにおける可動シーブ
のボス部内周の一方に突設された係止部材と、他方に回
転軸の軸心に対し傾斜して形成され、上記係止部材に係
合する係合溝とからなり、従動側回転軸に伝動トルクが
働いたときに回転軸の従動プーリの可動シーブとの相対
回転により、ベルト押圧機構によるベルトの押圧により
駆動及び従動プーリの各可動シーブにそれぞれ発生する
駆動側及び従動側推力の差を低減するように、可動シー
ブを固定シーブから離隔させる推力を発生させる従動側
推力発生機構を備える。That is, according to the present invention, in the transmission according to the first aspect of the present invention, instead of the driving-side thrust generating mechanism,
A locking member protruding from one of the outer circumference of the driven side rotation shaft or the inner circumference of the boss portion of the movable sheave in the driven pulley, and the other locking member is formed to be inclined with respect to the axis of the rotation shaft, and is engaged with the locking member. When the transmission torque acts on the driven rotation shaft, the rotation of the rotation shaft with respect to the movable sheave of the driven pulley causes the belt to be pressed by the belt pressing mechanism.
Generated on each movable sheave of the drive and driven pulleys
A driven thrust generating mechanism for generating a thrust for separating the movable sheave from the fixed sheave so as to reduce a difference between the driving side and the driven side thrust is provided.

【００１９】請求項４の発明では、従動側推力発生機構
を上記請求項３の発明の構成に代えてトルクカムで構成
する。According to a fourth aspect of the present invention, the driven thrust generating mechanism is constituted by a torque cam instead of the third aspect of the invention.

【００２０】すなわち、この発明では、請求項２の発明
の変速装置において、駆動側推力発生機構に代え、従動
側回転軸の外周又は従動プーリにおける可動シーブのボ
ス部の一方に回転一体に設けられた摺接部材と、他方に
一体的に設けられ、上記摺接部材に摺接するカム面を有
するトルクカムとからなり、従動側回転軸に伝動トルク
が働いたときに回転軸の従動プーリの可動シーブとの相
対回転により、ベルト押圧機構によるベルトの押圧によ
り駆動及び従動プーリの各可動シーブにそれぞれ発生す
る駆動側及び従動側推力の差を低減するように、可動シ
ーブを固定シーブから離隔させる推力を発生させる従動
側推力発生機構を備える。That is, according to the present invention, in the transmission according to the second aspect of the present invention, instead of the driving-side thrust generating mechanism, the transmission-side thrust generating mechanism is provided integrally with the outer periphery of the driven-side rotating shaft or one of the boss portions of the movable sheave in the driven pulley. A movable sheave of a driven pulley of the rotary shaft when a transmission torque is applied to the driven rotary shaft when the transmission torque is applied to the driven rotary shaft. Relative to the belt , the belt is pressed by the belt pressing mechanism.
Generated on each movable sheave of the driven and driven pulleys.
And a driven-side thrust generating mechanism for generating a thrust for separating the movable sheave from the fixed sheave so as to reduce the difference between the driving-side and driven-side thrusts .

【００２１】請求項５の発明では、上記請求項１の発明
に、請求項３の発明の構成の従動側推力発生機構を加え
る。According to a fifth aspect of the present invention, a driven thrust generating mechanism having the structure of the third aspect of the present invention is added to the first aspect of the present invention.

【００２２】請求項６の発明では、上記請求項１の発明
に、請求項４の発明の構成の従動側推力発生機構を加え
る。According to a sixth aspect of the present invention, a driven-side thrust generating mechanism having the structure of the fourth aspect of the present invention is added to the first aspect of the present invention.

【００２３】請求項７の発明では、上記請求項２の発明
に、請求項３の発明の構成の従動側推力発生機構を加え
る。According to a seventh aspect of the present invention, a driven-side thrust generating mechanism having the structure of the third aspect of the present invention is added to the second aspect of the present invention.

【００２４】請求項８の発明では、上記請求項２の発明
に、請求項４の発明の構成の従動側推力発生機構を加え
る。According to an eighth aspect of the present invention, a driven-side thrust generating mechanism having the structure of the fourth aspect of the present invention is added to the second aspect of the present invention.

【００２５】[0025]

【作用】上記の構成により、請求項１の発明では、駆動
プーリにおける可動シーブのボス部内周に形成される係
合溝は駆動側回転軸の軸心に対し傾斜しているので、変
速装置の伝動時に駆動側回転軸に伝動トルクが働いて、
回転軸が可動シーブと相対回転すると、それに伴い、係
合溝とそれに係合する係止部材との間に、ベルト押圧機
構によるベルトの押圧により駆動及び従動プーリの各可
動シーブにそれぞれ発生する駆動側及び従動側推力の差
を低減するように、可動シーブを固定シーブに接近させ
る推力が発生する。この推力は駆動側発生推力と逆方向
にそれを低減するように作用するので、駆動側発生推力
の従動側発生推力との差が小さくなり、このことで変速
操作力を大幅に低減することができる。According to the above construction, the engagement groove formed in the inner periphery of the boss portion of the movable sheave in the drive pulley is inclined with respect to the axis of the drive-side rotary shaft. Transmission torque acts on the drive side rotating shaft during transmission,
When the rotation shaft rotates relative to the movable sheave, the belt pressing device is moved between the engagement groove and the engagement member engaged therewith.
Driving and driven pulleys can be set by pressing the belt
Difference between driving and driven thrust generated in dynamic sheave
A thrust is generated to move the movable sheave closer to the fixed sheave so as to reduce the force. Since this thrust acts to reduce it in the opposite direction to the drive-side generated thrust, the difference between the drive-side generated thrust and the driven-side generated thrust is reduced, which can significantly reduce the speed change operation force. it can.

【００２６】請求項２の発明では、駆動側回転軸に伝動
トルクが働いて、回転軸が可動シーブと相対回転する
と、それに伴い、トルクカムとそのカム面に摺接する摺
接部材との間に、ベルト押圧機構によるベルトの押圧に
より駆動及び従動プーリの各可動シーブにそれぞれ発生
する駆動側及び従動側推力の差を低減するように、可動
シーブを固定シーブに接近させる推力が発生し、よって
駆動側発生推力と従動側発生推力との差を小さくするこ
とができる。According to the second aspect of the present invention, when the transmission torque acts on the drive-side rotating shaft and the rotating shaft relatively rotates with the movable sheave, the torque cam and the sliding contact member slidingly contacting the cam surface are accordingly caused. For belt pressing by belt pressing mechanism
Generated on each movable sheave of drive and driven pulleys
A thrust that causes the movable sheave to approach the fixed sheave is generated so as to reduce the difference between the driving-side and driven-side thrusts, so that the difference between the driving-side generated thrust and the driven-side generated thrust can be reduced.

【００２７】請求項３の発明では、従動プーリにおける
可動シーブのボス部内周に形成される係合溝は従動側回
転軸の軸心に対し傾斜しているので、変速装置の伝動時
に従動側回転軸に伝動トルクが働いて、回転軸が可動シ
ーブと相対回転すると、それに伴い、係合溝とそれに係
合する係止部材との間に、ベルト押圧機構によるベルト
の押圧により駆動及び従動プーリの各可動シーブにそれ
ぞれ発生する駆動側及び従動側推力の差を低減するよう
に、可動シーブを固定シーブから離隔させる推力が発生
する。この推力は従動側発生推力と同じ方向にそれを増
大するように作用するので、その駆動側発生推力との差
が小さくなり、変速操作力を大幅に低減することができ
る。According to the third aspect of the present invention, the engagement groove formed in the inner periphery of the boss portion of the movable sheave in the driven pulley is inclined with respect to the axis of the driven rotation shaft. When the transmission torque acts on the shaft and the rotation shaft rotates relative to the movable sheave, the belt is pressed by the belt pressing mechanism between the engagement groove and the engagement member engaged therewith.
To the movable sheaves of the drive and driven pulleys
To reduce the difference between the driving and driven thrusts that occur.
Then, a thrust for separating the movable sheave from the fixed sheave is generated. This thrust acts so as to increase it in the same direction as the driven-side generated thrust, so that the difference between the thrust and the driven-side generated thrust is reduced, and the speed-change operating force can be greatly reduced.

【００２８】請求項４の発明では、従動側回転軸に伝動
トルクが働いて、回転軸が可動シーブと相対回転する
と、それに伴い、トルクカムとそのカム面に摺接する摺
接部材との間に、ベルト押圧機構によるベルトの押圧に
より駆動及び従動プーリの各可動シーブにそれぞれ発生
する駆動側及び従動側推力の差を低減するように、可動
シーブを固定シーブから離隔させる推力が発生し、よっ
て駆動側発生推力と従動側発生推力との差を小さくでき
る。According to the fourth aspect of the present invention, when the transmission torque acts on the driven-side rotary shaft and the rotary shaft rotates relative to the movable sheave, the torque cam and the sliding member that slides on the cam surface are accordingly moved. For belt pressing by belt pressing mechanism
Generated on each movable sheave of drive and driven pulleys
A thrust that separates the movable sheave from the fixed sheave is generated so as to reduce the difference between the driving-side and driven-side thrusts, thereby reducing the difference between the driving-side generated thrust and the driven-side generated thrust.

【００２９】請求項５、６、７又は８の発明では、駆動
側においては、上記と同様に、駆動側回転軸に伝動トル
クが働いて回転軸が可動シーブと相対回転すると、ベル
ト押圧機構によるベルトの押圧により駆動及び従動プー
リの各可動シーブにそれぞれ発生する駆動側及び従動側
推力の差を低減するように、可動シーブを固定シーブに
接近させる推力が発生して、駆動側発生推力が低減す
る。また、これと同時に、従動側においては、同様に、
従動側回転軸に伝動トルクが働いて回転軸が可動シーブ
と相対回転すると、上記と同様にベルト押圧機構による
ベルトの押圧により各プーリの可動シーブにそれぞれ発
生する駆動側及び従動側推力の差を低減するように、可
動シーブを固定シーブから離隔させる推力が発生して、
従動側発生推力が増大する。これらの相乗効果により、
駆動側発生推力と従動側発生推力との差がさらに小さく
なり、よって変速操作力をより一層低減することができ
る。According to the fifth, sixth, seventh or eighth aspect of the present invention, when the transmission torque acts on the drive-side rotating shaft to rotate the rotating shaft relative to the movable sheave on the drive side, the bell
Drive and driven pull by belt pressing by
Drive side and driven side generated on each movable sheave
A thrust for moving the movable sheave closer to the fixed sheave is generated so as to reduce the difference in thrust, and the thrust generated on the drive side is reduced. At the same time, on the driven side,
When a transmission torque acts on the driven-side rotating shaft and the rotating shaft rotates relative to the movable sheave , the belt pressing mechanism operates in the same manner as described above.
Pressing the belt releases the movable sheave of each pulley.
A thrust that separates the movable sheave from the fixed sheave is generated so as to reduce the difference between the driving side and the driven side thrust generated,
The driven thrust increases. Due to these synergistic effects,
The difference between the driving-side generated thrust and the driven-side generated thrust is further reduced, so that the shift operation force can be further reduced.

【００３０】[0030]

【実施例】以下、本発明の実施例を図面に基づいて説明
する。Embodiments of the present invention will be described below with reference to the drawings.

【００３１】図３及び図４は本発明の実施例１に係る変
速装置の全体構成を示し、この実施例では、車両の補機
駆動用の変速装置として使用している。両図において、
１は一方の回転軸としての駆動軸で、図外の車載エンジ
ンに駆動連結されている。２は他方の回転軸としての従
動軸で、図外の補機（例えば発電用オルタネータ）に駆
動連結されている。両軸１，２は互いに平行に配置され
ている。FIGS. 3 and 4 show the overall structure of the transmission according to the first embodiment of the present invention. In this embodiment, the transmission is used as a transmission for driving auxiliary equipment of a vehicle. In both figures,
Reference numeral 1 denotes a drive shaft as one rotation shaft, which is drivingly connected to a vehicle-mounted engine (not shown). Reference numeral 2 denotes a driven shaft as the other rotating shaft, which is drivingly connected to an auxiliary machine (not shown) (for example, an alternator for power generation). Both shafts 1 and 2 are arranged parallel to each other.

【００３２】上記駆動軸１には駆動プーリ３が設けられ
ている。この駆動プーリ３は、駆動軸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
シーブ５と、該固定シーブ５に対向するように駆動軸１
にボス部６ａにて摺動可能に結合されたフランジ状の可
動シーブ６とからなり、これら両シーブ５，６間には断
面Ｖ字状のベルト溝７が形成されている。The drive shaft 1 is provided with a drive pulley 3. The drive pulley 3 includes a flange-shaped fixed sheave 5 fixed to the drive shaft 1 by a key 4 so as to rotate integrally and non-slidably, and a drive shaft 1 so as to face the fixed sheave 5.
And a movable sheave 6 in the form of a flange slidably connected by a boss 6a. A belt groove 7 having a V-shaped cross section is formed between the sheaves 5 and 6.

【００３３】一方、上記従動軸２上には従動プーリ８が
設けられている。この従動プーリ８は、上記駆動プーリ
３と同様の構成であり、従動軸２にキー９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ーブ
１０と、該固定シーブ１０に上記駆動軸１上の駆動プー
リ３における固定シーブ５に対する可動シーブ６の対向
方向と逆方向でもって対向するように従動軸２にボス部
１１ａにて摺動可能にかつ回転一体にキー１２により結
合されたフランジ状の可動シーブ１１とからなり、両シ
ーブ１０，１１間にはベルト溝１３が形成されている。
そして、上記駆動プーリ３のベルト溝７と従動プーリ８
のベルト溝１３との間にはＶベルトＢが巻き掛けられて
おり、駆動及び従動プーリ３，８の各可動シーブ６，１
１をそれぞれ固定シーブ５，１０に対して接離させて各
プーリ３，８のプーリ径（ＶベルトＢに対する有効半
径）を変更する。例えば駆動プーリ３の可動シーブ６を
固定シーブ５に接近させ、かつ従動プーリ８の可動シー
ブ１１を固定シーブ１０から離隔させたときには、駆動
プーリ３のプーリ径を従動プーリ８よりも大きくするこ
とにより、駆動軸１の回転を従動軸２に増速して伝達す
る。一方、逆に、駆動プーリ３の可動シーブ６を固定シ
ーブ５から離隔させ、かつ従動プーリ８の可動シーブ１
１を固定シーブ１０に接近させたときには、駆動プーリ
３のプーリ径を小にし、従動プーリ８のプーリ径を大き
くすることにより、駆動軸１の回転を減速して従動軸２
に伝えるようになされている。On the other hand, a driven pulley 8 is provided on the driven shaft 2. The driven pulley 8 has the same configuration as the driving pulley 3. The driven pulley 8 has a flange-shaped fixed sheave 10 that is fixed to the driven shaft 2 by a key 9 so as to rotate integrally and non-slidably. The driven shaft 2 is slidably connected to the driven shaft 2 at the boss portion 11a and rotated integrally with the driven shaft 2 by the key 12 so as to face the fixed sheave 5 in the driving pulley 3 on the shaft 1 in a direction opposite to the opposite direction. The movable sheave 11 has a flange shape, and a belt groove 13 is formed between the sheaves 10 and 11.
The belt groove 7 of the driving pulley 3 and the driven pulley 8
A V-belt B is wound around the belt groove 13 of each of the movable sheaves 6, 1 of the driving and driven pulleys 3, 8.
The pulleys 1 are brought into contact with and separated from the fixed sheaves 5 and 10, respectively, and the pulley diameters (effective radii for the V belt B) of the pulleys 3 and 8 are changed. For example, when the movable sheave 6 of the driving pulley 3 is moved closer to the fixed sheave 5 and the movable sheave 11 of the driven pulley 8 is separated from the fixed sheave 10, the diameter of the driving pulley 3 is made larger than that of the driven pulley 8. The rotation of the drive shaft 1 is transmitted to the driven shaft 2 at an increased speed. On the other hand, on the other hand, the movable sheave 6 of the driving pulley 3 is separated from the fixed sheave 5, and the movable sheave 1 of the driven pulley 8 is moved.
1 is brought closer to the fixed sheave 10, the pulley diameter of the drive pulley 3 is reduced and the pulley diameter of the driven pulley 8 is increased, so that the rotation of the drive shaft 1 is reduced and the driven shaft 2 is driven.
It is made to tell.

【００３４】上記駆動軸１上には、駆動プーリ３におけ
る可動シーブ６を固定シーブ５に対して接離させるため
の駆動側カム機構１４が設けられている。このカム機構
１４は、可動シーブ６のボス部６ａ上にベアリング１５
を介して相対回転可能にかつ軸方向に移動一体に外嵌合
支持された第１カムとしての円筒カム１６を有する。こ
のカム１６はその駆動プーリ３と反対側端面に１対の傾
斜カム面１６ａ，１６ａが円周方向に等角度間隔（１８
０°間隔）をあけて形成され、外周には回動レバー１７
が回動一体に突設されている。A drive cam mechanism 14 for moving the movable sheave 6 of the drive pulley 3 toward and away from the fixed sheave 5 is provided on the drive shaft 1. The cam mechanism 14 has a bearing 15 on the boss 6a of the movable sheave 6.
And a cylindrical cam 16 as a first cam which is rotatably rotatable and axially movable and integrally fitted with the outer cam. This cam 16 has a pair of inclined cam surfaces 16a, 16a on its end face opposite to the drive pulley 3 at equal angular intervals (18) in the circumferential direction.
0 ° interval), and a rotating lever 17
Are provided so as to rotate integrally.

【００３５】また、駆動軸１の他端外周には第２カムと
しての円筒状ローラ取付台１８がベアリング（図示せ
ず）を介して駆動軸１に対し相対回転可能に配置されて
いる。このローラ取付台１８の外周にはその半径方向に
延びる２つのピン１９，１９が直径方向に対向して一体
的に取り付けられている。各ピン１９のヘッド側はロー
ラ取付台１８から突出していて、その突出部分に、上記
カム１６の各カム面１６ａに当接して転動するカム用ロ
ーラ２０（摺接部）が回転可能に支持されている。Further, a cylindrical roller mount 18 as a second cam is disposed on the outer periphery of the other end of the drive shaft 1 via a bearing (not shown) so as to be rotatable relative to the drive shaft 1. Two pins 19, 19 extending in the radial direction are integrally mounted on the outer periphery of the roller mount 18 so as to oppose each other in the radial direction. The head side of each pin 19 protrudes from the roller mount 18, and a cam roller 20 (sliding contact portion) that rolls in contact with each cam surface 16 a of the cam 16 is rotatably supported on the protruding portion. Have been.

【００３６】さらに、図４に示すように、上記ローラ取
付台１８の外周には取付フランジ２１が一体に突設さ
れ、該フランジ２１の先端はピン２２を介して例えば車
体等の固定体（図示せず）に連結されていて、ローラ取
付台１８が駆動軸１に対し軸方向に移動不能にかつ回転
不能に固定されている。Further, as shown in FIG. 4, a mounting flange 21 is integrally provided on the outer periphery of the roller mounting base 18, and the front end of the flange 21 is fixed via a pin 22 to a fixed body such as a vehicle body (see FIG. 4). (Not shown), and the roller mount 18 is fixed to the drive shaft 1 so as not to move in the axial direction and to rotate.

【００３７】一方、従動軸２上には、従動プーリ８の可
動シーブ１１を固定シーブ１０に対して接離させるため
の従動側カム機構２３が設けられている。この従動側カ
ム機構２３は、上記駆動側カム機構１４と同様の構成
で、可動シーブ１１のボス部１１ａ上にベアリング２４
を介して回転可能にかつ摺動不能に外嵌合支持された第
１カムとしての円筒カム２５を有し、このカム２５の従
動プーリ８と反対側端面には１対の傾斜カム面２５ａ，
２５ａが形成され、その外周には回動レバー２６が回動
一体に取り付けられている。回動レバー２６の先端には
連結部材２７がボルト２８，２８により取り付けられ、
その連結部材２７の先端は、エンジンの吸気負圧で作動
する図外のダイアフラム装置（アクチュエータ）に連結
されている。また、上記従動軸２の他端外周にはベアリ
ング（図示せず）を介してローラ取付台２９（第２カ
ム）が支持され、該ローラ取付台２９の外周には取付フ
ランジ３０が一体に突設され、該フランジ３０の先端は
図４に示す如くピン３１を介して固定体に連結されてお
り、ローラ取付台２９は固定体に固定されて軸方向に移
動不能にかつ回転不能とされている。このローラ取付台
２９の外周にはその半径方向に延びる１対のピン３２，
３２が円周方向に等間隔をあけて取り付けられ、該各ピ
ン３２のローラ取付台２９からの突出部分には上記カム
２５の各カム面２５ａに当接するカム用ローラ３３（摺
接部）が回転可能に支持されている。On the other hand, a driven cam mechanism 23 for moving the movable sheave 11 of the driven pulley 8 toward and away from the fixed sheave 10 is provided on the driven shaft 2. The driven cam mechanism 23 has the same configuration as the drive cam mechanism 14, and has a bearing 24 on the boss 11a of the movable sheave 11.
And a cylindrical cam 25 as a first cam rotatably and non-slidably supported via an external fitting. The cam 25 has a pair of inclined cam surfaces 25a,
A rotation lever 26 is attached to the outer periphery of the rotation lever 25a. A connecting member 27 is attached to the tip of the rotating lever 26 by bolts 28, 28,
The distal end of the connecting member 27 is connected to a diaphragm device (actuator) (not shown) which operates by the negative pressure of the intake air of the engine. A roller mount 29 (second cam) is supported on the outer periphery of the other end of the driven shaft 2 via a bearing (not shown), and a mounting flange 30 is integrally formed on the outer periphery of the roller mount 29. The tip of the flange 30 is connected to a fixed body via a pin 31 as shown in FIG. 4, and the roller mount 29 is fixed to the fixed body so that it cannot move in the axial direction and cannot rotate. I have. A pair of pins 32 extending in the radial direction is provided on the outer periphery of the roller mount 29,
32 are mounted at equal intervals in the circumferential direction, and a cam roller 33 (sliding contact portion) that comes into contact with each cam surface 25a of the cam 25 is provided at a protruding portion of each pin 32 from the roller mount 29. It is rotatably supported.

【００３８】そして、上記駆動側カム機構１４の回動レ
バー１７先端にはリンクボール３４が回動可能に支持さ
れている。該リンクボール３４には直棒状のリンク３５
の一端が螺合締結されている。このリンク３５は従動軸
２側に延びていて、その他端は上記連結部材２７にリン
クボール３６を介して従動軸２と平行の回転中心をもっ
て回転可能に連結されている。上記リンクボール３４，
３６及びリンク３５により変速切換機構３７が構成され
ており、ダイアフラム装置の切換操作に応じて、変速切
換機構３７で各カム機構１４，２３における円筒カム１
６，２５を互いに連係して可動シーブ６，１１のボス部
６ａ，１１ａ周りに回動させ、そのカム面１６ａ，２５
ａ上でカム用ローラ２０，３３を転動させることによ
り、可動シーブ６，１１を軸方向に移動させて固定シー
ブ５，１０に対し互いに相反して接離させ、そのベルト
溝７，１３の有効半径つまりプーリ３，８のプーリ径を
可変とし、駆動及び従動軸１，２間の変速比を変化させ
るようにしている。A link ball 34 is rotatably supported at the tip of the rotation lever 17 of the driving cam mechanism 14. The link ball 34 has a straight rod-shaped link 35.
Is screwed together. The link 35 extends toward the driven shaft 2, and the other end is rotatably connected to the connecting member 27 via a link ball 36 with a rotation center parallel to the driven shaft 2. The link ball 34,
A transmission switching mechanism 37 is constituted by the link 36 and the link 35, and the cylindrical cam 1 in each of the cam mechanisms 14, 23 is controlled by the transmission switching mechanism 37 in accordance with the switching operation of the diaphragm device.
6, 25 are rotated around the bosses 6a, 11a of the movable sheaves 6, 11 so that their cam surfaces 16a, 25
The movable sheaves 6 and 11 are moved in the axial direction by rolling the cam rollers 20 and 33 on the movable sheave a so that the movable sheaves 6 and 11 are opposed to and separated from the fixed sheaves 5 and 10, respectively. The effective radius, that is, the pulley diameters of the pulleys 3 and 8 are made variable so that the gear ratio between the drive and driven shafts 1 and 2 is changed.

【００３９】また、図４に示すように、上記駆動及び従
動プーリ３，８間には、両プーリ３，８間に張られたベ
ルトＢの１対のスパンＢ₁，Ｂ₂のうち駆動プーリ３の
駆動力が従動プーリ８に伝達されるときの緩み側スパン
Ｂ₂をその背面から押圧するベルト押圧機構４０が配設
され、この押圧機構４０によりベルトＢに張力を与える
ことでベルト推力を発生する。ベルト押圧機構４０は、
図１に示すように、ボス部４２ａが上記駆動プーリ３に
おける固定シーブ５のボス部５ａ上にベアリング４１，
４１を介して揺動可能に支持されたアーム４２と、該ア
ーム４２の先端部に駆動軸１と平行に取り付けられた軸
４３と、この軸４３にベアリング４４，４４を介して回
転可能に支承されたローラ４５とを備えている。そし
て、図示しないが、上記アーム４２の中間部と固定体と
の間には、アーム４２をローラ４５がベルト緩み側スパ
ンＢ₂背面を押圧するように図３で反時計回り方向に回
動付勢するばねが伸装され、このばねの付勢力は、上記
ローラ４５がベルトＢの緩み側スパンＢ₁を、該緩み側
スパンＢ₁に発生する最大張力よりも大きい張力で押圧
するように設定されており、この張力によりベルト推力
を発生させるようにしている。As shown in FIG. 4, between the driving and driven pulleys 3 and 8, the driving pulley of the pair of spans B ₁ and B ₂ of the belt B stretched between the pulleys 3 and 8 is provided. 3 of the driving force is a belt pressing mechanism 40 for pressing the slack side span B ₂ from its back surface arranged as it is transmitted to the driven pulley 8, a belt thrust by giving tension by the pressing mechanism 40 to the belt B Occur. The belt pressing mechanism 40 includes:
As shown in FIG. 1, the boss portion 42a is provided on the boss portion 5a of the fixed sheave 5 in the drive pulley 3 with the bearing 41,
An arm 42 swingably supported via 41, a shaft 43 attached to the tip of the arm 42 in parallel with the drive shaft 1, and a rotatable support for the shaft 43 via bearings 44, 44. Roller 45 provided. Then, although not shown, between the intermediate portion and the fixed body of the arm 42 is attached rotates counterclockwise in FIG. 3 so that the arms 42 are rollers 45 for pressing the belt slack side span B ₂ back energized springs is ShinSo, biasing force of the spring is set so that the roller 45 is a slack side span B ₁ of the belt B, and pressed by a tension greater than the maximum tension occurring in the moderate viewing side span B ₁ The belt tension is generated by this tension.

【００４０】さらに、この発明の特徴として、図１に示
すように、駆動軸１に伝動トルクが働いたときに、ベル
ト押圧機構４０によるベルトＢの押圧により駆動及び従
動プーリ３，８の各可動シーブ６，１１にそれぞれ発生
する駆動側及び従動側推力Ｆ1 ，Ｆ2 の差を低減するよ
うに、駆動プーリ３の可動シーブ６を固定シーブ５に接
近させる推力Ｆを発生させる駆動側推力発生機構５０が
構成されている。すなわち、駆動軸１外周において、可
動シーブ６の摺動範囲には係止部材としての１対の係止
ピン５１，５１が駆動軸１の直径方向に対向して突設さ
れている。一方、可動シーブ６のボス部６ａ内周には上
記係止ピン５１，５１にそれぞれ係合する１対の係合溝
５２，５２が凹設され、この各係合溝５２と係止ピン５
１，５１との係合により可動シーブ６が駆動軸１に対し
摺動可能にかつ所定角度だけ相対回転可能に連結されて
いる。上記各係合溝５２は、図２に示すように駆動軸１
の軸心に対し傾斜して形成されており、この係合溝５２
の傾斜により、駆動軸１に伝動トルクが働いたときに、
可動シーブ６を駆動軸１と所定角度だけ相対回転させ
て、この相対回転により、ベルト押圧機構４０によるベ
ルトＢの押圧により駆動及び従動プーリ３，８の各可動
シーブ６，１１にそれぞれ発生する駆動側及び従動側推
力Ｆ1 ，Ｆ2 の差を低減するように、可動シーブ６を固
定シーブ５に接近させる推力Ｆを発生させるようにして
いる。[0040] Further, as a feature of the invention, as shown in FIG. 1, when the transmission torque is exerted on the drive shaft 1, Bell
The belt B is pressed and driven by the
Generated on each movable sheave 6,11 of the moving pulley 3,8
The difference between the driving and driven thrusts F1 and F2 is reduced.
Thus, the drive-side thrust generating mechanism 50 that generates the thrust F that causes the movable sheave 6 of the drive pulley 3 to approach the fixed sheave 5 is configured. That is, on the outer periphery of the drive shaft 1, a pair of locking pins 51, 51 as locking members are provided in the sliding range of the movable sheave 6 so as to protrude in the diametric direction of the drive shaft 1. On the other hand, on the inner periphery of the boss 6a of the movable sheave 6, a pair of engaging grooves 52, 52 for engaging with the locking pins 51, 51, respectively, are recessed.
The movable sheave 6 is connected to the drive shaft 1 so as to be slidable and relatively rotatable by a predetermined angle by engaging with the drive shaft 1. Each of the engagement grooves 52 is, as shown in FIG.
The engagement groove 52 is formed to be inclined with respect to the axis of the engagement groove 52.
When the transmission torque acts on the drive shaft 1 due to the inclination of
The movable sheave 6 is rotated relative to the drive shaft 1 by a predetermined angle, and the relative rotation causes the belt
The driven and driven pulleys 3 and 8 can be moved by pressing the
Drive side and driven side thrust generated in sheaves 6 and 11 respectively
A thrust F for causing the movable sheave 6 to approach the fixed sheave 5 is generated so as to reduce the difference between the forces F1 and F2 .

【００４１】尚、図１では、駆動軸１の軸心の右側を低
速状態で、また左側を高速状態でそれぞれ示している。In FIG. 1, the right side of the axis of the drive shaft 1 is shown in a low-speed state, and the left side is shown in a high-speed state.

【００４２】また、図１及び図２中、５３は上記係止ピ
ン５１に回転可能に支持されたローラで、係合溝５２の
側面に接触して転動する。1 and 2, reference numeral 53 denotes a roller rotatably supported by the locking pin 51, which rolls by contacting the side surface of the engaging groove 52.

【００４３】また、上記ベルト押圧機構４０のローラ４
５は、上記駆動及び従動軸１，２と平行な方向に移動す
るＶベルトＢの外周面に常時接触するように軸方向の長
さが長いものに形成されている。The roller 4 of the belt pressing mechanism 40
Reference numeral 5 is formed to have a long axial length so as to always contact the outer peripheral surface of the V-belt B moving in a direction parallel to the driving and driven shafts 1 and 2.

【００４４】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 described.

【００４５】エンジンの動力を補機に伝達する駆動状態
においては、ベルト押圧機構４０におけるばねの付勢力
によりアーム４２が図４で反時計回り方向に付勢され、
その先端のローラ４５がベルトＢの緩み側スパンＢ₁背
面を押圧し、この押圧によりベルトＢに張力が付与され
る。この張力は緩み側スパンＢ₂に発生する最大張力よ
りも大きいため、このベルト張力によりベルトＢのプー
リ３，８に対するくさび効果が生じて推力が発生し、こ
の推力により駆動プーリ３から従動プーリ８にベルトＢ
を介して動力が伝達される。In the driving state in which the power of the engine is transmitted to the auxiliary machine, the arm 42 is urged counterclockwise in FIG. 4 by the urging force of the spring of the belt pressing mechanism 40.
The tip of the roller 45 presses the slack side span B ₁ back of the belt B, the tension in the belt B by the pressing is applied. Therefore tension is greater than the maximum tension occurring in the slack side span B _2, the thrust is generated by the wedge effect by the belt tension on the pulley 3,8 of the belt B is generated, the driven pulley 8 from the driving pulley 3 by the thrust Belt B
Power is transmitted via the.

【００４６】そして、例えば、エンジンの回転を減速し
て補機に伝達する低速状態（図５（ａ）参照）とすると
きには、ダイアフラム装置の作動により変速切換機構３
７を切換操作して連結部材２７を低速位置(Lo)に位置付
ける。この連結部材２７は従動側カム機構２３における
カム２５外周の回動レバー２６に連結されているので、
上記低速位置(Lo)への切換操作に伴い、上記カム２５が
そのカム面２５ａ上で各カム用ローラ３３を転動させな
がら従動プーリ８の可動シーブ１１のボス部１１ａ周り
に一方向に回動する。これにより、上記カム面２５ａが
ローラ３３に押されて、カム２５が図３で下方向に従動
軸２上を移動し、該カム２５にベアリング２４を介して
移動一体の可動シーブ１１が同方向に移動して固定シー
ブ１０に接近する。このことにより従動プーリ８が閉じ
てそのプーリ径が増大し、このプーリ径の増大によりＶ
ベルトＢが従動プーリ８側に引き寄せられる。Then, for example, when the engine is decelerated to be in a low-speed state in which the rotation is transmitted to the auxiliary machine (see FIG. 5A), the shift switching mechanism 3 is operated by the operation of the diaphragm device.
7 is switched to position the connecting member 27 at the low speed position (Lo). Since the connecting member 27 is connected to the rotating lever 26 on the outer periphery of the cam 25 in the driven side cam mechanism 23,
With the switching operation to the low speed position (Lo), the cam 25 rotates in one direction around the boss portion 11a of the movable sheave 11 of the driven pulley 8 while rolling each cam roller 33 on its cam surface 25a. Move. As a result, the cam surface 25a is pressed by the roller 33, and the cam 25 moves on the driven shaft 2 in the downward direction in FIG. 3, and the movable sheave 11, which is integrally moved with the cam 25 via the bearing 24, moves in the same direction. To approach the fixed sheave 10. As a result, the driven pulley 8 closes and its pulley diameter increases.
The belt B is drawn to the driven pulley 8 side.

【００４７】また、上記連結部材２７にはリンク３５及
びリンクボール３４，３６を介して回動レバー１７が駆
動連結されているため、上記低速位置(Lo)への切換えに
伴い、上記従動プーリ８の可動シーブ１１の動きに同期
して、駆動側カム機構１４のカム１６が駆動軸１上を上
記従動側カム機構２３のカム２５と同じ一方向に回動す
る。このカム１６の回動によりカム用ローラ２０に対す
る押圧がなくなる。このため、上記従動プーリ８側に移
動するベルトＢの張力により、カム１６及びそれにベア
リング１５を介して連結されている可動シーブ６は固定
シーブ５から離れる方向（図３で下方向）に駆動軸１上
を移動し、この両シーブ５，６の離隔により駆動プーリ
３が開いてプーリ径が減少する。これらの結果、駆動プ
ーリ３のプーリ径が従動プーリ８よりも小さくなり、駆
動軸１の回転が減速されて従動軸２に伝達される。Further, since the rotating lever 17 is drivingly connected to the connecting member 27 via the link 35 and the link balls 34, 36, the driven pulley 8 is switched with the switching to the low speed position (Lo). The cam 16 of the drive side cam mechanism 14 rotates on the drive shaft 1 in the same direction as the cam 25 of the driven side cam mechanism 23 in synchronization with the movement of the movable sheave 11. The rotation of the cam 16 eliminates the pressing on the cam roller 20. For this reason, the cam 16 and the movable sheave 6 connected thereto via the bearing 15 are driven by the tension of the belt B moving toward the driven pulley 8 in a direction away from the fixed sheave 5 (downward in FIG. 3). 1, the drive pulley 3 is opened due to the separation between the sheaves 5 and 6, and the pulley diameter decreases. As a result, the pulley diameter of the drive pulley 3 becomes smaller than that of the driven pulley 8, and the rotation of the drive shaft 1 is reduced and transmitted to the driven shaft 2.

【００４８】また、逆に、エンジンの回転を増速して補
機に伝達する高速状態（図５（ｂ）参照）では、ダイア
フラム装置の作動により連結部材２７を高速位置(Hi)に
位置付ける。この切換えに伴い、上記駆動側カム機構１
４のカム１６がそのカム面１６ａ上でカム用ローラ２０
を転動させながら駆動プーリ３における可動シーブ６の
ボス部６ａ周りに他方向に回動する。このカム１６の回
動によりカム面１６ａがカム用ローラ２０に押されて図
３で上方向に駆動軸１上を移動し、可動シーブ６も同方
向に移動して固定シーブ５に接近し、このことにより駆
動プーリ３が閉じてプーリ径が増大する。このプーリ径
の増大によりＶベルトＢが駆動プーリ３側に引き寄せら
れる。On the contrary, in a high-speed state in which the rotation of the engine is accelerated and transmitted to the auxiliary machine (see FIG. 5B), the connection member 27 is positioned at the high-speed position (Hi) by the operation of the diaphragm device. With this switching, the drive side cam mechanism 1
4 on the cam surface 16a.
Is rotated around the boss 6a of the movable sheave 6 in the drive pulley 3 in the other direction while rolling. Due to the rotation of the cam 16, the cam surface 16a is pushed by the cam roller 20 to move upward on the drive shaft 1 in FIG. 3, and the movable sheave 6 also moves in the same direction to approach the fixed sheave 5, As a result, the drive pulley 3 closes and the pulley diameter increases. Due to the increase in the pulley diameter, the V-belt B is drawn to the drive pulley 3 side.

【００４９】また、上記可動シーブ６の動きに同期し
て、従動側カム機構２３のカム２５が該従動軸２上を上
記カム１６と同じ他方向に回動し、このカム２５の回動
によりカム用ローラ３３に対する押圧がなくなり、ベル
トＢの張力により従動プーリ８の可動シーブ１１がカム
２５と共に固定シーブ１０から離れる方向（図３で上方
向）に従動軸２上を移動する。この両シーブ１０，１１
の離隔により従動プーリ８が開いてそのプーリ径が減少
する。その結果、駆動プーリ３のプーリ径が従動プーリ
８よりも大きくなり、駆動軸１の回転が増速されて従動
軸２に伝達される。In synchronization with the movement of the movable sheave 6, the cam 25 of the driven cam mechanism 23 rotates on the driven shaft 2 in the same other direction as the cam 16. The pressing of the cam roller 33 is stopped, and the movable sheave 11 of the driven pulley 8 moves along with the cam 25 on the driven shaft 2 in a direction away from the fixed sheave 10 (upward in FIG. 3) due to the tension of the belt B. These sheaves 10, 11
, The driven pulley 8 opens, and the diameter of the pulley decreases. As a result, the pulley diameter of the drive pulley 3 becomes larger than that of the driven pulley 8, and the rotation of the drive shaft 1 is accelerated and transmitted to the driven shaft 2.

【００５０】この場合、ＶベルトＢの緩み側スパンＢ₁
の背面をベルト押圧機構２５のローラ４５によって押圧
付勢することにより、該ＶベルトＢに張力が与えられ、
この張力によりベルト推力Ｆ1 ，Ｆ2 が発生するととも
に、駆動及び従動プーリ３，８の双方における可動シー
ブ６，１１を変速切換機構３７による機械的な駆動によ
って軸方向に移動させるので、図６に示すように、駆動
及び従動プーリ３，８でそれぞれ発生する発生推力Ｆ1
，Ｆ2 （Ｆ1 ＞Ｆ2 ）は方向が逆になり、この両発生
推力Ｆ1 ，Ｆ2 が部分的に互いに相殺し合い、残りが操
作力となる。そして、駆動プーリ３における可動シーブ
６は駆動軸１に対し係合溝５２の係止ピン５１との係合
により結合され、可動シーブ６のボス部６ａ内周に形成
される係合溝５２は駆動軸１の軸心に対し傾斜している
ので、伝動時に駆動軸１に伝動トルクが働いて駆動軸１
が可動シーブ６と相対回転したとき、それに伴い、係合
溝５２と係止ピン５１との間に可動シーブ６を固定シー
ブ５に接近させる推力Ｆが発生する。この推力Ｆは図６
に示す如く上記駆動側発生推力Ｆ1 とは逆方向にそれを
低減するように作用するので、その分だけ駆動側発生推
力Ｆ1 の従動側発生推力Ｆ2 との差が小さくなり、両発
生推力Ｆ1 ，Ｆ2 の関係は図１０に示す理想状態に近付
く。従って、両推力Ｆ1 ，Ｆ2 の差である変速操作力を
大幅に低減できることになり、出力の小さいダイアフラ
ム装置であっても変速操作をスムーズに行うことがで
き、ダイアフラム装置やその他の制御機器のコンパクト
化を図ることができる。尚、上記実施例では、係止ピン
５１を駆動軸１に、また係合溝５２を可動シーブ６にそ
れぞれ設けたが、逆に、係止ピン５１を可動シーブ６
に、また係合溝５２を駆動軸１にそれぞれ設けるように
してもよい。In this case, the loose side span B ₁ of the V belt B
Is pressed by the roller 45 of the belt pressing mechanism 25 to apply tension to the V-belt B,
This tension generates belt thrusts F1 and F2, and also causes the movable sheaves 6, 11 in both the driving and driven pulleys 3, 8 to move in the axial direction by mechanical driving by the speed changeover mechanism 37, as shown in FIG. Thus, the generated thrust F1 generated by the driving and driven pulleys 3 and 8, respectively.
, F2 (F1> F2) have opposite directions, the two generated thrusts F1 and F2 partially cancel each other, and the rest is the operating force. The movable sheave 6 of the drive pulley 3 is coupled to the drive shaft 1 by engaging the engagement pin 52 of the engagement groove 52, and the engagement groove 52 formed on the inner periphery of the boss 6 a of the movable sheave 6 is Since the drive shaft 1 is inclined with respect to the axis of the drive shaft 1, a transmission torque acts on the drive shaft 1 during transmission so that the drive shaft 1
Is relatively rotated with the movable sheave 6, a thrust F for causing the movable sheave 6 to approach the fixed sheave 5 is generated between the engagement groove 52 and the locking pin 51. This thrust F is shown in FIG.
As shown in FIG. 5, the force generated in the opposite direction to the drive-side generated thrust F1 acts so as to reduce the difference between the drive-side generated thrust F1 and the driven-side generated thrust F2. The relationship of F2 approaches the ideal state shown in FIG. Therefore, the speed change operation force, which is the difference between the two thrusts F1 and F2, can be greatly reduced, and the speed change operation can be smoothly performed even with a diaphragm device having a small output, and the size of the diaphragm device and other control devices can be reduced. Can be achieved. In the above embodiment, the locking pin 51 is provided on the drive shaft 1 and the engaging groove 52 is provided on the movable sheave 6.
Alternatively, the engagement grooves 52 may be provided in the drive shaft 1 respectively.

【００５１】図７及び図８は実施例２を示し、駆動側推
力発生機構５０′の構造を変えたものである。尚、図１
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。FIGS. 7 and 8 show the second embodiment, in which the structure of the driving-side thrust generating mechanism 50 'is changed. FIG.
The same parts as those described above are denoted by the same reference numerals, and detailed description thereof will be omitted.

【００５２】この実施例では、駆動軸１の可動シーブ６
側の端部外周にはその半径方向に延びる２つのピン５
３，５３が直径方向に対向して一体的に取り付けられて
いる。各ピン５３のヘッド側は駆動軸１から突出してい
て、その突出部分に摺接部材としてのローラ５４が回転
可能に支持されている。一方、駆動プーリ３における可
動シーブ６のボス部６ａの背面側端部にはボス部６ａと
同心円筒状のトルクカム５５が一体的に取り付けられて
いる。このトルクカム５５の背面側端部には上記ローラ
５４，５４をそれぞれ転動状態で摺接係合させる１対の
カム面５５ａ，５５ａが直径方向に対向して切欠形成さ
れている。この各カム面５５ａは、図８に示すようにト
ルクカム５５（駆動軸１）の軸心に対して傾斜してお
り、このトルクカム５５のカム面５５ａとローラ５４と
の係合により、上記実施例と同様に、駆動軸１に伝動ト
ルクが働いたときに駆動軸１の可動シーブ６とを相対回
転させて、ベルト押圧機構４０によるベルトＢの押圧に
より駆動及び従動プーリ３，８の各可動シーブ６，１１
にそれぞれ発生する駆動側及び従動側推力Ｆ1 ，Ｆ2 の
差を低減するように、可動シーブ６を固定シーブ５に接
近させる推力Ｆを発生させるようになっている。この実
施例での他の構成は実施例１と同様である。In this embodiment, the movable sheave 6 of the drive shaft 1
Two pins 5 extending in the radial direction are provided on the outer periphery of the side end.
3, 53 are integrally mounted so as to face each other in the diametrical direction. The head side of each pin 53 protrudes from the drive shaft 1, and a roller 54 as a sliding contact member is rotatably supported on the protruding portion. On the other hand, a torque cam 55 concentrically cylindrical with the boss 6a is attached to an end of the drive pulley 3 on the back side of the boss 6a of the movable sheave 6. A pair of cam surfaces 55a, 55a for slidably engaging the rollers 54, 54 in a rolling state, respectively, are cut out at the rear end of the torque cam 55 so as to face each other in the diametrical direction. As shown in FIG. 8, each of the cam surfaces 55a is inclined with respect to the axis of the torque cam 55 (drive shaft 1). Similarly, when the transmission torque acts on the drive shaft 1, the movable sheave 6 of the drive shaft 1 is relatively rotated with respect to the belt B by the belt pressing mechanism 40.
The movable sheaves 6, 11 of the driving and driven pulleys 3 , 8
Of the drive-side and driven-side thrusts F1 and F2 respectively generated in
To reduce the difference, a thrust F for causing the movable sheave 6 to approach the fixed sheave 5 is generated. Other configurations in this embodiment are the same as those in the first embodiment.

【００５３】したがって、この実施例においては、駆動
プーリ３における可動シーブ６はトルクカム５５に一体
化され、このトルクカム５５のカム面５５ａ，５５ａは
それぞれ駆動軸１に支持したローラ５４，５４に係合さ
れ、上記カム面５５ａはトルクカム５５の軸心に対し傾
斜しているので、伝動時に駆動軸１に伝動トルクが働い
て駆動軸１が可動シーブ６と相対回転すると、トルクカ
ム５５とローラ５４との間に可動シーブ６を固定シーブ
５に接近させる推力Ｆが発生する。この推力Ｆは上記実
施例１と同様に、駆動側発生推力Ｆ1 とは逆方向にそれ
を低減するように作用するので、駆動側発生推力Ｆ1 の
従動側発生推力Ｆ2 との差が小さくなる。よって、両推
力Ｆ1 ，Ｆ2 の差である変速操作力を大幅に低減するこ
とができる。Therefore, in this embodiment, the movable sheave 6 of the drive pulley 3 is integrated with the torque cam 55, and the cam surfaces 55a, 55a of the torque cam 55 engage the rollers 54, 54 supported on the drive shaft 1, respectively. Since the cam surface 55a is inclined with respect to the axis of the torque cam 55, the transmission torque acts on the drive shaft 1 during transmission and the drive shaft 1 rotates relative to the movable sheave 6, so that the torque cam 55 and the roller 54 During this time, a thrust F for causing the movable sheave 6 to approach the fixed sheave 5 is generated. This thrust F acts to reduce the thrust F1 in the opposite direction to the thrust F1 generated on the driving side, as in the first embodiment, so that the difference between the thrust F1 generated on the driving side and the thrust F2 generated on the driven side becomes small. Therefore, the speed change operation force, which is the difference between the two thrusts F1 and F2, can be greatly reduced.

【００５４】尚、この実施例においても、トルクカム５
５及びローラ５４を駆動軸１と可動シーブ６との間で逆
転させてもよい。In this embodiment, the torque cam 5
The roller 5 and the roller 54 may be reversed between the drive shaft 1 and the movable sheave 6.

【００５５】上記各実施例では、推力発生機構５０を駆
動側に設けているが、従動側に設けることもできる。こ
の推力発生機構を従動側に設けるには、上記実施例１の
係止ピン５１及びそれと係合する係合溝５２と同様の構
成の従動側推力発生機構、又は実施例２のトルクカム５
５を有する構成と同様の従動側推力発生機構のいずれか
を従動プーリ８の可動シーブ１１と従動軸２との間に介
在させ、この従動側推力発生機構により、従動軸２に伝
動トルクが働いたときに従動軸２と従動プーリ８の可動
シーブ１１との相対回転により、該可動シーブ１１を固
定シーブ１０から離隔させる推力Ｆ′を発生させるよう
にすればよい。In each of the above embodiments, the thrust generating mechanism 50 is provided on the driving side, but may be provided on the driven side. In order to provide the thrust generating mechanism on the driven side, the driven side thrust generating mechanism having the same configuration as the locking pin 51 and the engaging groove 52 engaged with the locking pin 51 of the first embodiment, or the torque cam 5 of the second embodiment.
5 is interposed between the movable sheave 11 of the driven pulley 8 and the driven shaft 2, and a transmission torque acts on the driven shaft 2 by the driven thrust generating mechanism. When the driven shaft 2 and the movable sheave 11 of the driven pulley 8 rotate relative to each other, a thrust F ′ for separating the movable sheave 11 from the fixed sheave 10 may be generated.

【００５６】こうして従動側推力発生機構を設けること
により、変速装置の伝動時に従動軸２に伝動トルクが働
いて、従動軸２が可動シーブ１１と相対回転すると、係
合溝とそれに係合する係止ピンとの間、又はトルクカム
とローラとの間に、ベルト押圧機構４０によるベルトＢ
の押圧により駆動及び従動プーリ３，８の各可動シーブ
６，１１にそれぞれ発生する駆動側及び従動側推力Ｆ1
，Ｆ2 の差を低減するように、可動シーブ１１を固定
シーブ１０から離隔させる推力Ｆ′が発生する。この推
力Ｆ′は、上記実施例１，２の如く駆動側発生推力Ｆ1
と逆方向にそれを低減するように作用するのではなく、
図９に示すように従動側発生推力Ｆ2 と同方向にそれを
増大するように作用する。従って、このときでも駆動側
及び従動側の発生推力Ｆ1 ，Ｆ2 間の差は小さくなり、
変速操作力を大幅に低減することができる。By providing the driven-side thrust generating mechanism in this way, when the transmission shaft operates to transmit torque to the driven shaft 2 during transmission of the transmission and the driven shaft 2 rotates relative to the movable sheave 11, the engaging groove and the engaging member engaged therewith are formed. Between the stop pin or the torque cam and the roller, the belt B by the belt pressing mechanism 40.
Movable sheaves of the driven and driven pulleys 3 and 8 by pressing
Drive-side and driven-side thrusts F1 generated at 6 and 11, respectively.
, F2, the thrust F 'for separating the movable sheave 11 from the fixed sheave 10 is generated. This thrust F 'is equal to the driving-side generated thrust F1 as in the first and second embodiments.
Rather than acting to reduce it in the opposite direction,
As shown in FIG. 9, the thrust F2 acts to increase the thrust in the same direction as the driven thrust F2. Therefore, even in this case, the difference between the generated thrusts F1 and F2 on the driving side and the driven side becomes small,
The shifting operation force can be greatly reduced.

【００５７】さらには、推力発生機構を駆動側及び従動
側の双方に設けてもよい。この場合、上記実施例１又は
２の構成に、上記説明した従動側推力発生機構を組み合
わせることとなる。この組合せは下記の表１の〜に
示すように４通りあり、スペースや製造コスト等に応じ
て適宜選択すればよい。Further, the thrust generating mechanism may be provided on both the driving side and the driven side. In this case, the driven thrust generating mechanism described above is combined with the configuration of the first or second embodiment. There are four types of this combination as shown in Table 1 below, which may be appropriately selected according to space, manufacturing cost, and the like.

【００５８】[0058]

【表１】 [Table 1]

【００５９】このように駆動側及び従動側にそれぞれ推
力発生機構を設けると、相乗効果が得られる。つまり、
駆動側においては、駆動軸１の駆動プーリ３の可動シー
ブ６との相対回転により該可動シーブ６を固定シーブ５
に接近させる推力Ｆが発生し、駆動側発生推力Ｆ1 が低
減する。これと同時に、従動側においては、従動軸２の
従動プーリ８の可動シーブ１１との相対回転によって可
動シーブ１１を固定シーブ１０から離隔させる推力Ｆ′
が発生して従動側発生推力Ｆ2 が増大することとなり、
これらの相乗的な作用により駆動側発生推力Ｆ1 と従動
側発生推力Ｆ2との差をさらに小さくして、変速操作力
をより一層低減できる利点がある。By providing a thrust generating mechanism on each of the driving side and the driven side, a synergistic effect can be obtained. That is,
On the driving side, the movable sheave 6 is fixed to the fixed sheave 5 by the relative rotation of the drive shaft 1 and the movable sheave 6 of the drive pulley 3.
Is generated, and the driving-side generated thrust F1 is reduced. At the same time, on the driven side, the thrust F ′ for separating the movable sheave 11 from the fixed sheave 10 by the relative rotation of the driven shaft 2 and the movable sheave 11 of the driven pulley 8.
Is generated and the driven-side generated thrust F2 increases,
By these synergistic effects, there is an advantage that the difference between the driving-side generated thrust F1 and the driven-side generated thrust F2 can be further reduced, and the shift operation force can be further reduced.

【００６０】尚、上記実施例では、車両の補機を変速駆
動する変速装置に適用した場合であるが、本発明は、そ
れ以外に例えば農業機械やその他の機械における変速装
置に適用することができるのは勿論のことである。In the above embodiment, the present invention is applied to a transmission that drives an auxiliary device of a vehicle at a variable speed. However, the present invention can be applied to a transmission for an agricultural machine or another machine. Of course you can.

【００６１】[0061]

【発明の効果】以上説明したように、請求項１又は２の
発明では、ベルト式変速装置の駆動側に推力発生機構を
設け、この推力発生機構により、伝動時に駆動側回転軸
に伝動トルクが働いて回転軸が駆動プーリの可動シーブ
と相対回転すると、可動シーブを固定シーブに接近させ
る推力を発生させて、駆動側発生推力を低減させるよう
にした。また、請求項３又は４の発明では、従動側に推
力発生機構を設け、伝動時に従動側回転軸に伝動トルク
が働いて回転軸が従動プーリの可動シーブと相対回転す
ると、可動シーブを固定シーブから離隔させる推力を発
生させて、駆動側発生推力を低減するようにした。さら
に、請求項５、６、７又は８の発明では、駆動側におい
て、上記と同様に駆動プーリの可動シーブを固定シーブ
に接近させる推力を発生させて、駆動側発生推力を低減
する一方、従動側においては、従動プーリの可動シーブ
を固定シーブから離隔させる推力を発生して、従動側発
生推力を増大させるようにした。従って、これらの発明
によると、駆動側発生推力と従動側発生推力との差を小
さくでき、変速操作力を大幅に低減することができ、車
両の補機を変速装置で変速しながらエンジンで駆動する
場合に、その変速をエンジンの吸気負圧を利用した出力
の小さいダイアフラム装置で制御することができ、実用
性の高い効果が得られる。As described above, according to the first or second aspect of the present invention, a thrust generating mechanism is provided on the driving side of the belt-type transmission, and the thrust generating mechanism applies a transmitting torque to the driving-side rotary shaft during transmission. When the rotating shaft rotates relative to the movable sheave of the drive pulley, a thrust for moving the movable sheave closer to the fixed sheave is generated, thereby reducing the thrust generated on the drive side. Further, in the invention according to claim 3 or 4, a thrust generating mechanism is provided on the driven side, and when a transmission torque acts on the driven side rotating shaft during transmission and the rotating shaft relatively rotates with the movable sheave of the driven pulley, the movable sheave is fixed. A thrust is generated so as to be separated from the motor, thereby reducing the thrust generated on the driving side. Further, in the invention according to claim 5, 6, 7 or 8, on the driving side, a thrust for causing the movable sheave of the driving pulley to approach the fixed sheave is generated in the same manner as described above to reduce the thrust generated on the driving side, and On the side, a thrust for separating the movable sheave of the driven pulley from the fixed sheave is generated to increase the thrust generated on the driven side. Therefore, according to these inventions, the difference between the driving-side generated thrust and the driven-side generated thrust can be reduced, the shift operation force can be significantly reduced, and the auxiliary equipment of the vehicle is driven by the engine while shifting with the transmission. In this case, the shift can be controlled by a diaphragm device having a small output utilizing the intake negative pressure of the engine, and a highly practical effect can be obtained.

[Brief description of the drawings]

【図１】実施例１において駆動プーリ及びその周辺の構
造を示す拡大断面図である。FIG. 1 is an enlarged cross-sectional view illustrating a structure of a driving pulley and a periphery thereof in a first embodiment.

【図２】ピンと係合溝との関係を示す平面図である。FIG. 2 is a plan view showing a relationship between a pin and an engagement groove.

【図３】変速装置の全体構成を示す断面図である。FIG. 3 is a cross-sectional view showing the entire configuration of the transmission.

【図４】変速装置の全体構成を示す正面図である。FIG. 4 is a front view showing the entire configuration of the transmission.

【図５】変速装置の低速状態及び高速状態を模式的に示
す説明図である。FIG. 5 is an explanatory diagram schematically showing a low speed state and a high speed state of the transmission.

【図６】発生推力と駆動側発生機構により発生した推力
との関係を示す図である。FIG. 6 is a diagram illustrating a relationship between a generated thrust and a thrust generated by a driving-side generating mechanism.

【図７】実施例２を示す図１相当図である。FIG. 7 is a diagram corresponding to FIG. 1 showing a second embodiment.

【図８】トルクカムの展開図である。FIG. 8 is a development view of a torque cam.

【図９】発生推力と従動側発生機構により発生した推力
との関係を示す図である。FIG. 9 is a diagram showing a relationship between a generated thrust and a thrust generated by a driven-side generating mechanism.

【図１０】駆動側及び従動側発生推力の関係を示す特性
図である。FIG. 10 is a characteristic diagram illustrating a relationship between a driving-side and a driven-side generated thrust.

[Explanation of symbols]

１…駆動軸（回転軸）２…従動軸（回転軸）３…駆動プーリ５…固定シーブ６…可動シーブ６ａ…ボス部７…ベルト溝８…従動プーリ１０…固定シーブ１１…可動シーブ１１ａ…ボス部１３…ベルト溝１４…駆動側カム機構１６…円筒カム（第１カム）１６ａ…カム面１８…ローラ取付台（第２カム）２０…ローラ（摺接部）２３…従動側カム機構２５…円筒カム（第１カム）２５ａ…カム面２９…ローラ取付台（第２カム）３３…ローラ（摺接部）３７…変速切換機構４０…ベルト押圧機構５０，５０′…駆動側推力発生機構５１…係止ピン（係止部材）５２…係合溝５４…ローラ（摺接部材）５５…トルクカム５５ａ…カム面Ｂ…ベルトＢ1 …緩み側スパンＦ，Ｆ′…推力発生機構により発生した推力Ｆ1 …駆動側発生推力Ｆ2 …従動側発生推力 DESCRIPTION OF SYMBOLS 1 ... Drive shaft (rotating shaft) 2 ... Follower shaft (rotating shaft) 3 ... Drive pulley 5 ... Fixed sheave 6 ... Movable sheave 6a ... Boss part 7 ... Belt groove 8 ... Driven pulley 10 ... Fixed sheave 11 ... Movable sheave 11a ... Boss part 13: Belt groove 14: Drive side cam mechanism 16: Cylindrical cam (first cam) 16a: Cam surface 18: Roller mount (second cam) 20: Roller (sliding contact part) 23: Driven side cam mechanism 25 ... Cylindrical cam (first cam) 25a ... Cam surface 29 ... Roller mount (second cam) 33 ... Roller (sliding contact part) 37 ... Shift switching mechanism 40 ... Belt pressing mechanism 50,50 '... Drive side thrust generating mechanism 51: locking pin (locking member) 52: engaging groove 54: roller (sliding member) 55: torque cam 55a: cam surface B: belt B1: loose side span F, F ': thrust generated by the thrust generating mechanism F1… drive side Generated thrust F2… driven thrust

Claims

(57) [Claims]

1. A fixed sheave provided on a pair of rotating shafts arranged in parallel with each other and fixed to the rotating shaft so as to rotate integrally and non-slidably, and a belt between the fixed sheaves A drive and driven pulley comprising a movable sheave supported slidably in the axial direction on the rotating shaft so as to form a groove, and a belt wound around a belt groove of the drive and driven pulley, In the transmission, in which the movable sheave of each of the pulleys is moved toward and away from the fixed sheave facing each other to change the effective radius of each pulley with respect to the belt, the transmission ratio between the two rotating shafts is variable. Each of the pulleys is disposed on the back side of each movable sheave, each of which has an inclined cam surface at an end thereof and which is in contact with the inclined cam surface of the first cam at the end and a cylindrical first concentric cylindrical cam. With sliding contact And a second cam concentric with the rotating shaft. One of the first and second cams is connected to the movable sheave in the axial direction so as to be integrally movable and relatively rotatable, and the other is in the axial direction of the rotating shaft. The two cams are arranged so as to be immovable and relatively rotatable, and one of the two cams is a rotatable cam rotatable around a rotation axis, and the other is connected to a fixed body to be a non-rotatable fixed cam. A drive and driven cam mechanism that moves the movable sheave closer to the fixed sheave by relative rotation of the rotating cam with the fixed cam, and the other when one movable sheave of the drive and driven pulley approaches the opposed fixed sheave. A gear changeover mechanism for changing the gear ratio between the two rotating shafts by rotating the rotating cams of the two cam mechanisms in cooperation with each other so that the movable sheave of the movable sheave moves away from the opposed fixed sheave; and the drive and driven pulley. Placed between A belt pressing mechanism for pressing the loose side span of the belt wound between the two pulleys so that the belt bites into the belt groove of each pulley; and an outer periphery of the driving side rotating shaft or a boss portion of a movable sheave in the driving pulley. A locking member protruded on one side of the circumference and an engaging groove formed on the other side so as to be inclined with respect to the axis of the rotating shaft and engaged with the locking member, and a transmission torque acts on the rotating shaft. Relative to the movable sheave of the driving pulley of the rotating shaft when the belt is pressed by the belt pressing mechanism.
Generated on each movable sheave of the driven and driven pulleys.
A transmission-side thrust generating mechanism for generating a thrust for bringing the movable sheave closer to the fixed sheave so as to reduce the difference between the driving-side and driven-side thrusts .

2. A fixed sheave provided on a pair of rotating shafts arranged in parallel with each other and fixed to the rotating shaft so as to rotate integrally and non-slidably, and a belt between the fixed sheaves A drive and driven pulley comprising a movable sheave slidably in an axial direction on a rotating shaft so as to form a groove; and a belt wound between belt grooves of the drive and driven pulley; By moving the movable sheave of the pulley toward and away from the opposing fixed sheave and changing the effective radius of each pulley with respect to the belt, the transmission ratio between the two rotating shafts can be varied. A first cam which is disposed on the back side of the movable sheave and has an inclined cam surface at an end and which is concentric with the rotary shaft, and a sliding contact portion which slides on an end with the inclined cam surface of the first cam; Having a rotating shaft And one of the first and second cams is connected to the movable sheave so as to be integrally movable and relatively rotatable in the axial direction, and the other is not movable in the axial direction of the rotating shaft. And one of the two cams is a rotatable cam rotatable about a rotation axis, and the other is connected to a fixed body to be a non-rotatable fixed cam. A driving and driven cam mechanism for moving the movable sheave so as to approach the fixed sheave by relative rotation with the fixed cam, and a movable sheave when one of the driving and driven pulleys approaches the opposing fixed sheave. A speed changeover mechanism for changing the speed ratio between the two rotating shafts by rotating the rotating cams of the two cam mechanisms in cooperation with each other so as to separate from the opposed fixed sheave, and disposed between the driving and driven pulleys And both A belt pressing mechanism for pressing the loose side span of the belt wound between the belts so that the belt bites into the belt groove of each pulley; and one of the outer periphery of the driving side rotating shaft or the boss portion of the movable sheave in the driving pulley. A drive pulley for the rotating shaft when a transmission torque is applied to the rotating shaft, comprising: a sliding contact member provided integrally with the rotating member; and a torque cam integrally provided on the other side and having a cam surface slidingly contacting the sliding contact member. Relative to the movable sheave of the belt , the belt pressing mechanism
Each movable sheave of driving and driven pulleys
To reduce the difference between the driving and driven thrusts
A transmission-side thrust generating mechanism for generating a thrust for bringing the movable sheave closer to the fixed sheave.

3. The transmission according to claim 1, wherein, instead of the driving-side thrust generating mechanism, a locking member protruding from one of an outer periphery of the driven-side rotary shaft or an inner periphery of a boss portion of the movable sheave in the driven pulley; On the other hand, an engaging groove is formed to be inclined with respect to the axis of the rotating shaft, and engages with the locking member. The engaging groove is formed with a movable sheave of a driven pulley of the rotating shaft when a transmission torque acts on the rotating shaft. By relative rotation, it is driven and driven by belt pressing by belt pressing mechanism.
Side generated on each movable sheave of driven and driven pulleys
And a driven-side thrust generating mechanism for generating a thrust for separating the movable sheave from the fixed sheave so as to reduce a difference between the driven-side thrust and a driven-side thrust .

4. The transmission according to claim 2, wherein a sliding contact member provided integrally with the outer periphery of the driven-side rotary shaft or one of the boss portions of the movable sheave in the driven pulley, instead of the driving-side thrust generating mechanism. A torque cam having a cam surface which is integrally provided on the other side and slidably contacts the sliding contact member. The belt rotates by a relative rotation of the driven pulley of the rotary shaft with the movable sheave when a transmission torque is applied to the rotary shaft. By pressing the belt by the pressing mechanism
Generated on each movable sheave of the drive and driven pulleys
A transmission device comprising a driven thrust generating mechanism for generating a thrust for separating a movable sheave from a fixed sheave so as to reduce a difference between a driving side and a driven side thrust .

5. The transmission according to claim 1, wherein one of an outer periphery of the driven-side rotating shaft or an inner periphery of a boss portion of the movable sheave of the driven pulley is provided on one side, and the other is provided on an axis of the rotating shaft. And an engagement groove that is formed to be inclined with respect to the engaging member, and is formed by an engagement groove that engages with the locking member. When a transmission torque is applied to the rotation shaft, the rotation of the rotation shaft with respect to the movable sheave of the driven pulley causes the belt pressing mechanism to rotate. Driven by belt pressure
Side generated on each movable sheave of driven and driven pulleys
And a driven-side thrust generating mechanism for generating a thrust for separating the movable sheave from the fixed sheave so as to reduce a difference in the driven-side thrust.

6. The transmission according to claim 1, wherein one of a boss portion of a movable sheave on the outer periphery of the driven-side rotary shaft or a driven pulley is provided integrally with a sliding contact member rotatably provided on the other side. A torque cam having a cam surface that slides on the sliding contact member, and when the transmission torque acts on the rotation shaft, the rotation of the rotation shaft with respect to the movable sheave of the driven pulley causes the belt pressing mechanism to press the belt.
Generated on each movable sheave of the drive and driven pulleys
A transmission device comprising a driven thrust generating mechanism for generating a thrust for separating a movable sheave from a fixed sheave so as to reduce a difference between a driving side and a driven side thrust .

7. The transmission according to claim 2, wherein the engaging member protrudes from one of an outer periphery of the driven-side rotary shaft or an inner periphery of a boss portion of the movable sheave in the driven pulley, and the other end is provided with an axial center of the rotating shaft. formed by against inclined consists engagement groove which engages with the engaging member, the relative rotation of the movable sheave of the driven pulley of the rotary shaft when the transmission torque is exerted on the rotating shaft, by the belt pressing mechanism Driven by belt pressure
Side generated on each movable sheave of driven and driven pulleys
And a driven-side thrust generating mechanism for generating a thrust for separating the movable sheave from the fixed sheave so as to reduce a difference in the driven-side thrust.

8. The transmission according to claim 2, wherein the sliding contact member is provided integrally with the outer periphery of the driven rotation shaft or one of the boss portions of the movable sheave in the driven pulley, and is provided integrally with the other. A torque cam having a cam surface that slides on the sliding contact member, and when the transmission torque acts on the rotation shaft, the rotation of the rotation shaft with respect to the movable sheave of the driven pulley causes the belt pressing mechanism to press the belt.
Generated on each movable sheave of the drive and driven pulleys
A transmission device comprising a driven thrust generating mechanism for generating a thrust for separating a movable sheave from a fixed sheave so as to reduce a difference between a driving side and a driven side thrust .