JP5282748B2 - Belt type continuously variable transmission - Google Patents

Belt type continuously variable transmission Download PDF

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JP5282748B2
JP5282748B2 JP2010053738A JP2010053738A JP5282748B2 JP 5282748 B2 JP5282748 B2 JP 5282748B2 JP 2010053738 A JP2010053738 A JP 2010053738A JP 2010053738 A JP2010053738 A JP 2010053738A JP 5282748 B2 JP5282748 B2 JP 5282748B2
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belt
pulley
sheave
driven
drive
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JP2011185405A (en
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朋亮 ▲柳▼田
勇仁 服部
一昭 石浦
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Toyota Motor Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a belt type continuously variable transmission that can reduce the size and weight of the transmission without reducing the variation width of a variable speed ratio or enlarge the variation width of the variable speed ratio without enlarging the transmission. <P>SOLUTION: The belt type continuously variable transmission 1 includes: a driving pulley 3 comprising a movable sheave 7 and a fixed sheave 8; a driven pulley 5 comprising a movable sheave 9 and a fixed sheave 10; and a transmission belt 6 wound on the respective pulleys 3, 5, wherein the movable sheave 7 and the fixed sheave 10, and the fixed sheave 8 and the movable sheave 9, are arranged facing in a direction of a center distance L. The driving pulley 3 and the driven pulley 5 are formed so that the outer diameter D<SB>7</SB>of the movable sheave 7 is smaller than the outer diameter D<SB>8</SB>of the fixed sheave 8 and that the outer diameter D<SB>9</SB>of the movable sheave 9 is smaller than the outer diameter D<SB>10</SB>of the fixed sheave 10, and the outer peripheral portion 8o of the fixed sheave 8 and the outer peripheral portion 10o of the fixed sheave 10 are overlapped in the direction of the center distance L. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

この発明は、駆動側のプーリと従動側のプーリとの間で、それらの間に巻き掛けられた伝動ベルトを介して動力伝達を行い、かつ変速比を連続的に制御するベルト式無段変速機に関するものである。   This invention is a belt-type continuously variable transmission that performs power transmission between a driving pulley and a driven pulley via a transmission belt wound between them and continuously controls the gear ratio. Related to the machine.

ベルト式無段変速機は、ベルトを巻掛けたプーリの溝幅を変化させることにより、プーリの有効径すなわちベルトが巻き掛かっている半径を変更して変速比を無段階に設定することのできる変速機である。したがって駆動側もしくは入力側のプーリ（プライマリプーリ）、および、従動側もしくは出力側のプーリ（セカンダリプーリ）を、固定シーブとその固定シーブに対して軸線方向に前後動する可動シーブとによって構成し、可動シーブを例えば油圧などを利用して移動させることにより、各プーリの溝幅を変化させて、ベルトの巻き掛かり半径を連続的にすなわち無段階に変更できるように構成されている。   The belt type continuously variable transmission can change the effective diameter of the pulley, that is, the radius around which the belt is wound, by changing the groove width of the pulley around which the belt is wound, thereby setting the transmission ratio steplessly. It is a transmission. Therefore, the drive side or input side pulley (primary pulley) and the driven side or output side pulley (secondary pulley) are constituted by a fixed sheave and a movable sheave that moves back and forth in the axial direction relative to the fixed sheave, By moving the movable sheave using, for example, hydraulic pressure, the groove width of each pulley is changed, and the belt winding radius can be changed continuously, that is, steplessly.

上記のようなベルト式の無段変速機の一例が特許文献１に記載されている。この特許文献１に記載された無段変速機のケース構造は、エンジン側に設置されたプライマリプーリと、このプライマリプーリとの間に巻き掛けられる駆動ベルト（伝動ベルト）を介して連結されるセカンダリプーリとが備えられ、セカンダリプーリのプーリ軸とそのプーリ軸に回動自在に設置された出力軸とを接続・離間させる出力クラッチが、上記のセカンダリプーリの軸端に配置された無段変速機のケース構造であって、出力クラッチを格納する収納部とプライマリプーリのプーリ軸に設置される回転部材を収納する収納部とに互いに連通する開口部が設けられ、その開口部を介して回転部材の外周の一部と出力クラッチの外周の一部とが軸方向に一定の距離をもってオーバーラップするように構成されている。   An example of such a belt-type continuously variable transmission is described in Patent Document 1. The case structure of the continuously variable transmission described in Patent Document 1 includes a primary pulley installed on the engine side and a secondary coupled via a drive belt (transmission belt) wound between the primary pulley. And a continuously variable transmission in which an output clutch for connecting / separating a pulley shaft of a secondary pulley and an output shaft rotatably installed on the pulley shaft is disposed at the shaft end of the secondary pulley. In this case structure, an opening that communicates with each other is provided in a housing portion that houses the output clutch and a housing portion that houses the rotating member installed on the pulley shaft of the primary pulley, and the rotating member is provided through the opening. A part of the outer periphery of the output clutch and a part of the outer periphery of the output clutch are overlapped with each other at a constant distance in the axial direction.

なお、特許文献２には、可動プーリ（可動シーブ）の外径が、固定プーリ（固定シーブ）の外径よりも小さくなるように構成されたＶベルトオートマチック機構に関する発明が記載されている。   Patent Document 2 describes an invention relating to a V-belt automatic mechanism configured such that the outer diameter of a movable pulley (movable sheave) is smaller than the outer diameter of a fixed pulley (fixed sheave).

また、特許文献３の図１，図２等には、入力軸側および出力軸側の各プーリの可動シーブの外径が、それぞれ、各プーリの固定シーブの外径よりも小さくなっている構成が開示されている。   Further, in FIGS. 1 and 2 of Patent Document 3, the outer diameter of the movable sheave of each pulley on the input shaft side and the output shaft side is smaller than the outer diameter of the fixed sheave of each pulley. Is disclosed.

特開２００４−５２８１６号公報JP 2004-52816 A 実用新案登録第３１４２８４７号公報Utility Model Registration No. 3142847 特開平７−１０３３０２号公報JP 7-103302 A

上記の特許文献１では、その特許文献１に記載されたベルト式無段変速機によれば、プライマリプーリ側に設置される回転部材の外周の一部と、セカンダリプーリ側に設置される出力クラッチの外周の一部とが、互いに軸方向に一定の距離をもってオーバーラップするように配置されることにより、出力側の軸受け間スパンを長くすることなく、それらプライマリプーリ側の回転部材とセカンダリプーリ側の出力クラッチとの干渉を防止してクラッチ径の拡大を可能にし、かつ装置全体のコンパクト化を図ることができる、とされている。   In said patent document 1, according to the belt-type continuously variable transmission described in the said patent document 1, a part of outer periphery of the rotating member installed in the primary pulley side, and the output clutch installed in the secondary pulley side Are arranged so as to overlap each other with a certain distance in the axial direction, so that the rotation member on the primary pulley side and the secondary pulley side can be obtained without increasing the span between the bearings on the output side. It is said that the interference with the output clutch can be prevented, the clutch diameter can be increased, and the entire apparatus can be made compact.

一方、上記のようなベルト式無段変速機は、プライマリプーリとセカンダリプーリとの軸間距離を短縮することによっても、変速機本体を小型化あるいは軽量化することができる。したがって、変速機の小型・軽量化を図るためには、例えば上記の特許文献１の図２に示されているように、ベルト式無段変速機のプライマリプーリとセカンダリプーリとの軸間距離は、各プーリの外周部分が互いに干渉しない範囲で可及的に短く設定されるのが望ましい。プライマリプーリとセカンダリプーリとの軸間距離が短縮されることにより、変速機本体を小型・軽量化できるとともに、それらプライマリプーリとセカンダリプーリとの間に巻き掛けられる伝動ベルトに加わる負荷を軽減することもできる。   On the other hand, the belt-type continuously variable transmission as described above can also reduce the size or weight of the transmission body by reducing the distance between the shafts of the primary pulley and the secondary pulley. Therefore, in order to reduce the size and weight of the transmission, for example, as shown in FIG. 2 of Patent Document 1, the distance between the shafts of the primary pulley and the secondary pulley of the belt-type continuously variable transmission is It is desirable that the outer peripheral portions of the pulleys be set as short as possible within a range where they do not interfere with each other. By reducing the distance between the shafts of the primary pulley and the secondary pulley, the transmission main body can be reduced in size and weight, and the load applied to the transmission belt wound between the primary pulley and the secondary pulley can be reduced. You can also.

そして、プライマリプーリとセカンダリプーリとの軸間距離は、それらプライマリプーリおよびセカンダリプーリの外径を小さくすることによって短縮することができる。しかしながら、プーリの外径を小さくすると、その分、プーリに伝動ベルトが巻き掛かる際のベルトの巻き掛かり半径の変化幅が狭くなる、すなわちベルト式無段変速機で設定し得る変速比の変化幅が狭くなってしまう。   Then, the distance between the shafts of the primary pulley and the secondary pulley can be shortened by reducing the outer diameters of the primary pulley and the secondary pulley. However, if the outer diameter of the pulley is reduced, the change width of the belt wrapping radius when the transmission belt is wound around the pulley is reduced, that is, the change ratio of the gear ratio that can be set by the belt type continuously variable transmission. Becomes narrower.

このように、ベルト式無段変速機で設定可能な変速比の変化幅を縮小することなく、プライマリプーリとセカンダリプーリとの軸間距離を短縮して変速機本体の小型・軽量化を図るためには、もしくは、プライマリプーリとセカンダリプーリとの軸間距離を延長させてベルト式無段変速機本体を大型化することなく、その無段変速機で設定可能な変速比の変化幅を拡大するためには、未だ改良の余地があった。   Thus, to reduce the distance between the shafts of the primary pulley and the secondary pulley and reduce the size and weight of the transmission main body without reducing the range of change of the gear ratio that can be set by the belt type continuously variable transmission. Alternatively, the range of change of the gear ratio that can be set by the continuously variable transmission is increased without increasing the belt-type continuously variable transmission main body by extending the distance between the primary pulley and the secondary pulley. There was still room for improvement.

この発明は上記の技術的課題に着目してなされたものであり、ベルト式無段変速機で設定可能な変速比の変化幅を縮小することなくその変速機本体を小型・軽量化すること、もしくは、ベルト式無段変速機本体を大型化することなくその変速機で設定可能な変速比の変化幅を拡大することができるベルト式無段変速機を提供することを目的とするものである。   The present invention has been made paying attention to the above technical problem, and can reduce the size and weight of the transmission body without reducing the change width of the transmission ratio that can be set by the belt-type continuously variable transmission. Alternatively, it is an object of the present invention to provide a belt type continuously variable transmission capable of expanding a change range of a gear ratio that can be set by the transmission without enlarging a belt type continuously variable transmission main body. .

上記の目的を達成するために、請求項１の発明は、駆動側の回転軸に対してその回転軸線方向に移動可能に取り付けられた駆動側可動シーブと該回転軸線方向に移動不可能に取り付けられた駆動側固定シーブとによって駆動側ベルト巻き掛け溝を構成する駆動プーリと、前記駆動側の回転軸に平行な従動側の回転軸に対してその回転軸線方向に移動可能に取り付けられた従動側可動シーブと該回転軸線方向に移動不可能に取り付けられた従動側固定シーブとによって従動側ベルト巻き掛け溝を構成する従動プーリと、前記駆動プーリと前記従動プーリとに巻き掛けられてそれらの間で動力を伝達する伝動ベルトとを備えているとともに、前記駆動側可動シーブと前記従動側固定シーブとが、および前記駆動側固定シーブと前記従動側可動シーブとが、それぞれ前記各回転軸の軸間距離方向で互いに対向して配置されており、前記各可動シーブを前記回転軸線方向に前後動させて前記各ベルト巻き掛け溝の溝幅を変化させることにより、前記各プーリに対する前記伝動ベルトの巻き掛かり半径を変化させて変速比を連続的に変更するベルト式無段変速機において、前記駆動プーリおよび前記従動プーリは、前記駆動側可動シーブの外径が前記駆動側固定シーブの外径よりも小さく、かつ前記従動側可動シーブの外径が前記従動側固定シーブの外径よりも小さくなるように形成されているとともに、前記駆動側固定シーブの外周部分と前記従動側固定シーブの外周部分とが前記軸間距離方向で互いオーバーラップして配置されていることを特徴とするものである。   In order to achieve the above object, the invention of claim 1 is directed to a drive-side movable sheave attached to a drive-side rotary shaft so as to be movable in the direction of the rotary axis, and to be attached so as to be immovable in the direction of the rotary axis. A drive pulley that forms a drive-side belt winding groove by the drive-side fixed sheave, and a follower that is attached to a follow-up rotation shaft parallel to the drive-side rotation shaft so as to be movable in the direction of the rotation axis. A driven pulley that forms a driven side belt winding groove by a side movable sheave and a driven side fixed sheave that is immovably mounted in the rotational axis direction, and is wound around the driven pulley and the driven pulley. A drive belt that transmits power between the drive side movable sheave and the driven side fixed sheave, and the drive side fixed sheave and the driven side movable sheave. Are arranged opposite to each other in the inter-axis distance direction of the respective rotation shafts, and each movable sheave is moved back and forth in the rotation axis direction to change the groove width of each belt winding groove. Thus, in the belt-type continuously variable transmission that continuously changes the gear ratio by changing the wrapping radius of the transmission belt with respect to each pulley, the drive pulley and the driven pulley are the outer diameters of the drive-side movable sheaves. Is formed so that the outer diameter of the driven-side movable sheave is smaller than the outer diameter of the driven-side fixed sheave, and the outer periphery of the driving-side fixed sheave The portion and the outer peripheral portion of the driven side fixed sheave are arranged so as to overlap each other in the inter-axis distance direction.

また、請求項２の発明は、請求項１の発明において、前記駆動プーリおよび前記従動プーリにおける前記各可動シーブの外径が、それぞれ、前記各可動シーブと前記各固定シーブとが同径であった場合の前記各巻き掛かり半径の最大値の２倍よりも大きいことを特徴とするものである。   According to a second aspect of the present invention, in the first aspect of the invention, the outer diameters of the movable sheaves in the drive pulley and the driven pulley are the same as each of the movable sheaves and the fixed sheaves. It is characterized by being larger than twice the maximum value of the respective wrapping radii.

そして、請求項３の発明は、請求項２の発明において、前記駆動プーリおよび前記従動プーリにおける前記各巻き掛かり半径が、それぞれ前記各ベルト巻き掛け溝が最小となる際に前記各プーリに前記伝動ベルトが巻き掛かった状態で前記各ベルト巻き掛け溝と前記伝動ベルトとが接触する部分の範囲内での最大半径と最小半径とを平均した値であることを特徴とするものである。   According to a third aspect of the present invention, in the second aspect of the present invention, when the wrapping radii of the driving pulley and the driven pulley are set to the minimum when the belt wrapping grooves are minimized, the transmission is transmitted to the pulleys. It is a value obtained by averaging a maximum radius and a minimum radius within a range of a portion where each belt winding groove and the transmission belt are in contact with each other when the belt is wound.

請求項１の発明によれば、駆動プーリおよび従動プーリの各可動シーブが、それら各プーリの各固定シーブよりも小径に形成される。そのため、各可動シーブと各固定シーブとが同じ外径で形成される場合と比較して、各可動シーブの外径が小径化された分だけそれら各可動シーブを軽量化することができる。   According to the first aspect of the present invention, the movable sheaves of the drive pulley and the driven pulley are formed with a smaller diameter than the fixed sheaves of the pulleys. Therefore, compared with the case where each movable sheave and each fixed sheave are formed with the same outer diameter, the weight of each movable sheave can be reduced by the amount that the outer diameter of each movable sheave is reduced.

そして、各可動シーブを小径化させることによって駆動プーリと従動プーリとの間に生じた空間を利用して、駆動側固定シーブの外周部分と従動側固定シーブの外周部分とを各プーリの回転軸同士の軸間距離方向、すなわち各プーリの回転軸の両方に垂直な方向で互いオーバーラップさせる位置に、駆動プーリと従動プーリとが配置される。したがって、各可動シーブの外径が小径化された分、駆動プーリと従動プーリとの軸間距離を短縮することが可能になる。この場合、各プーリに伝動ベルトが巻き掛かる際のベルトの巻き掛かり半径の最大値を規定する各固定シーブの外径は維持されるので、ベルトの巻き掛かり半径の最大値が減少されることがない。言い換えると、ベルトの巻き掛かり半径の変化幅すなわちベルト式無段変速機として設定可能な変速比の変化幅が縮小することはない。そのため、設定可能な変速比の変化幅を縮小することなく、このベルト式無段変速機本体を小型・軽量化することができる。   Then, by utilizing the space created between the driving pulley and the driven pulley by reducing the diameter of each movable sheave, the outer peripheral portion of the driving-side fixed sheave and the outer peripheral portion of the driven-side fixed sheave are connected to the rotation shaft of each pulley. The driving pulley and the driven pulley are arranged at positions where they overlap each other in the inter-axis distance direction, that is, in a direction perpendicular to both the rotation axes of the pulleys. Therefore, the distance between the shafts of the drive pulley and the driven pulley can be shortened by the amount that the outer diameter of each movable sheave is reduced. In this case, since the outer diameter of each fixed sheave that defines the maximum value of the belt winding radius when the transmission belt is wound around each pulley is maintained, the maximum value of the belt winding radius may be reduced. Absent. In other words, the change width of the belt winding radius, that is, the change ratio of the speed change ratio that can be set as the belt-type continuously variable transmission is not reduced. Therefore, the belt type continuously variable transmission main body can be reduced in size and weight without reducing the changeable range of the changeable gear ratio.

あるいは、各可動シーブを小径化させることによって駆動プーリと従動プーリとの間に生じた空間を利用して、各可動シーブに各プーリの軸間距離方向でそれぞれ対向する各固定シーブの外径を大きくすることができる。したがって、各可動シーブの外径が小径化された分、駆動プーリと従動プーリとの軸間距離はそのままで、すなわち駆動プーリと従動プーリとの軸間距離を延長させることなく、各固定シーブの外径を大径化してベルトの巻き掛かり半径の変化幅を広げることができる。そのため、このベルト式無段変速機本体を大型化することなく、設定可能な変速比の変化幅を拡大することができる。   Alternatively, by using the space created between the drive pulley and the driven pulley by reducing the diameter of each movable sheave, the outer diameter of each fixed sheave that faces each movable sheave in the axial distance direction of each pulley is set. Can be bigger. Therefore, as the outer diameter of each movable sheave is reduced, the distance between the shafts of the drive pulley and the driven pulley remains the same, that is, without extending the distance between the shafts of the drive pulley and the driven pulley. The outer diameter can be increased to widen the change range of the belt winding radius. Therefore, the changeable range of the change gear ratio can be expanded without increasing the size of the belt-type continuously variable transmission main body.

また、請求項２の発明によれば、各固定シーブに対してそれぞれ小径化される各可動シーブの外径が、それら各固定シーブと各可動シーブとが同径であった場合のベルトの巻き掛かり半径の最大値の２倍以上の値に設定される。すなわち、各固定シーブに対して各可動シーブの外径がそれぞれ小径化される以前の状態でプーリのベルト巻き掛け溝が最小になった場合に、そのプーリに伝動ベルトが巻き掛かった部分の直径に相当する値よりも小さくならない範囲で、各可動シーブの外径が小さくされる。そのため、各可動シーブの外径を小さくすることによりベルトの巻き掛かり半径の最大値が低下させられることはない。言い換えると、各可動シーブの外径を小さくするためにベルトの巻き掛かり半径の変化幅が縮小されることはない。したがって、各可動シーブを適切に小径化させることができる。   According to the invention of claim 2, the outer diameter of each movable sheave that is reduced in diameter with respect to each fixed sheave is the winding of the belt when the respective fixed sheave and each movable sheave have the same diameter. It is set to a value more than twice the maximum value of the hook radius. That is, when the belt winding groove of the pulley is minimized before the outer diameter of each movable sheave is reduced relative to each fixed sheave, the diameter of the portion where the transmission belt is wound around the pulley The outer diameter of each movable sheave is reduced within a range not smaller than the value corresponding to. Therefore, the maximum value of the belt winding radius is not lowered by reducing the outer diameter of each movable sheave. In other words, in order to reduce the outer diameter of each movable sheave, the change width of the belt winding radius is not reduced. Therefore, each movable sheave can be appropriately reduced in diameter.

そして、請求項３の発明によれば、各固定シーブに対してそれぞれ小径化される各可動シーブの外径が、各ベルト巻き掛け溝が最小になる、すなわちベルトの巻き掛かり半径が最大になる際に各プーリに伝動ベルトが巻き掛かった状態で各ベルト巻き掛け溝と伝動ベルトとが接触する部分の範囲内での最大半径と最小半径とを平均した値の２倍以上の値に設定される。すなわち、各固定シーブに対して各可動シーブの外径がそれぞれ小径化される以前の状態でベルト巻き掛け溝が最小になった場合に、そのプーリに伝動ベルトが巻き掛かって実際に動力伝達を行う部分の平均的な直径に相当する値よりも小さくならない範囲で、各可動シーブの外径が小さくされる。そのため、各可動シーブを適切に小径化させることができる。   According to the third aspect of the present invention, the outer diameter of each movable sheave that is reduced in diameter relative to each fixed sheave is such that each belt winding groove is minimized, that is, the belt winding radius is maximized. When the transmission belt is wound around each pulley, the maximum radius and the minimum radius within the area where each belt winding groove and the transmission belt are in contact with each other are set to a value more than twice the average value. The That is, when the belt winding groove is minimized before the outer diameter of each movable sheave is reduced relative to each fixed sheave, the transmission belt is wound around the pulley and the power is actually transmitted. The outer diameter of each movable sheave is reduced within a range that does not become smaller than the value corresponding to the average diameter of the portion to be performed. Therefore, each movable sheave can be appropriately reduced in diameter.

この発明に係るベルト式無段変速機の構成を示す断面図である。It is sectional drawing which shows the structure of the belt-type continuously variable transmission which concerns on this invention. 図１に示すベルト式無段変速機の構成の詳細を説明するための拡大断面図である。FIG. 2 is an enlarged cross-sectional view for explaining details of the configuration of the belt type continuously variable transmission shown in FIG. 1. 図１に示すベルト式無段変速機の構成の詳細、特に各プーリのオーバーラップ部分を説明するための拡大断面図である。FIG. 2 is an enlarged cross-sectional view for explaining details of the configuration of the belt-type continuously variable transmission shown in FIG. 1, in particular, an overlapping portion of each pulley. ベルト式無段変速機における変速比と芯ずれ量との関係を説明するための図である。It is a figure for demonstrating the relationship between the gear ratio in a belt type continuously variable transmission, and the amount of misalignment. ベルト式無段変速機で芯ずれが生じた場合の伝動ベルト各部の挙動を説明するための模式図である。It is a schematic diagram for demonstrating the behavior of each part of a transmission belt when a center shift occurs in the belt type continuously variable transmission. 図４に示す伝動ベルト各部の挙動の詳細を説明するための拡大図である。It is an enlarged view for demonstrating the detail of the behavior of each part of a transmission belt shown in FIG. 従来のベルト式無段変速機の構成を示す断面図である。It is sectional drawing which shows the structure of the conventional belt-type continuously variable transmission.

つぎに、この発明を具体例を参照して説明する。図１には、この発明を、例えば車両に搭載されるベルト式無段変速機１に適用した例を模式的に示してある。このベルト式無段変速機１は、基本的な構成や動作原理は従来のベルト式無段変速機と同様のものである。すなわち、このベルト式無段変速機１の主要部分は、駆動側の回転軸２、すなわち、例えばエンジン（図示せず）などの駆動力源からトルクが入力される駆動軸２に取り付けられた駆動プーリ（もしくはプライマリプーリ）３と、従動側の回転軸４、すなわち、例えばデファレンシャルギヤ（図示せず）などの出力部材にトルクを出力する従動軸（もしくはセカンダリシャフト）４に取り付けられた従動プーリ（もしくはセカンダリプーリ，出力プーリ）５と、それら駆動プーリ３および従動プーリ５に巻き掛けられる伝動ベルト６とから構成されている。そして、各プーリ３，５に対する伝動ベルト６の巻き掛かり半径を連続的に変化させることにより、変速比を連続的にすなわち無段階に変更するように構成されている。   Next, the present invention will be described with reference to specific examples. FIG. 1 schematically shows an example in which the present invention is applied to, for example, a belt type continuously variable transmission 1 mounted on a vehicle. This belt type continuously variable transmission 1 has the same basic configuration and operating principle as the conventional belt type continuously variable transmission. That is, the main part of the belt-type continuously variable transmission 1 is a drive attached to a drive-side rotary shaft 2, that is, a drive shaft 2 to which torque is input from a drive force source such as an engine (not shown), for example. A pulley (or primary pulley) 3 and a driven pulley (or secondary shaft) 4 that outputs torque to an output member such as a driven rotation shaft 4, that is, for example, a differential gear (not shown). Or a secondary pulley, an output pulley) 5 and a transmission belt 6 wound around the drive pulley 3 and the driven pulley 5. The gear ratio is continuously changed, that is, steplessly changed by continuously changing the wrapping radius of the transmission belt 6 with respect to the pulleys 3 and 5.

具体的には、このベルト式無段変速機１は、駆動軸２に対してその回転軸線方向Ａに移動可能に取り付けられた可動シーブ７と駆動軸２に対して回転軸線方向Ａに移動不可能に取り付けられた固定シーブ８とによってベルト巻き掛け溝３ｖを構成する駆動プーリ３と、駆動軸２に対して平行に配置された従動軸４に対してその回転軸線方向Ｂに移動可能に取り付けられた可動シーブ９と従動軸４に対して回転軸線方向Ｂに移動不可能に取り付けられた固定シーブ１０とによってベルト巻き掛け溝５ｖを構成する従動プーリ５と、それら駆動プーリ３および従動プーリ５に巻き掛けられて、各プーリ３，５の間でトルクを伝達する伝動ベルト６とから構成されている。   Specifically, the belt-type continuously variable transmission 1 is movable in the rotational axis direction A with respect to the drive shaft 2 and the movable sheave 7 attached to the drive shaft 2 so as to be movable in the rotational axis direction A. A drive pulley 3 that forms a belt winding groove 3v by a fixed sheave 8 that can be attached, and a driven shaft 4 that is arranged parallel to the drive shaft 2 so as to be movable in the rotational axis direction B. The driven sheave 5 that forms the belt winding groove 5v by the movable sheave 9 and the fixed sheave 10 that is attached to the driven shaft 4 so as not to move in the rotation axis direction B, and the drive pulley 3 and the driven pulley 5 And a transmission belt 6 that transmits torque between the pulleys 3 and 5.

また、駆動プーリ３と従動プーリ５とは、各可動シーブ７，９と各固定シーブ８，１０とが、それぞれ各プーリ３，５の各回転軸２，４同士の軸間距離Ｌ方向で互いに対向するように配置されている。言い換えると、各回転軸２，４同士の軸間距離Ｌ方向、すなわち駆動軸２および従動軸４の両方に垂直な方向において、駆動プーリ３の可動シーブ７と従動プーリ５の固定シーブ１０とが対向し、かつ駆動プーリ３の固定シーブ８と従動プーリ５の可動シーブ９とが対向するように、駆動プーリ３と従動プーリ５とが配置されている。   In addition, the drive pulley 3 and the driven pulley 5 are configured such that the movable sheaves 7 and 9 and the fixed sheaves 8 and 10 are in the direction of the inter-axis distance L between the rotation shafts 2 and 4 of the pulleys 3 and 5, respectively. It arrange | positions so that it may oppose. In other words, the movable sheave 7 of the drive pulley 3 and the fixed sheave 10 of the driven pulley 5 are in the direction of the distance L between the rotary shafts 2 and 4, that is, in the direction perpendicular to both the drive shaft 2 and the driven shaft 4. The driving pulley 3 and the driven pulley 5 are arranged so as to face each other and the fixed sheave 8 of the driving pulley 3 and the movable sheave 9 of the driven pulley 5 face each other.

上記のように駆動プーリ３は、駆動軸２の外周に一体的に形成もしくは固定された固定シーブ８と、駆動軸２の回転軸線方向Ａに移動できるように構成された可動シーブ７とを有している。また、これら固定シーブ８と可動シーブ７との対向面間に、すなわち固定シーブ８のテーパ面８ａと可動シーブ７のテーパ面７ａとの間に、Ｖ字形状のベルト巻き掛け溝３ｖが形成されている。そして、可動シーブ７を駆動軸３の回転軸線方向Ａに前後動させ（図１での左右方向に動作させ）、その可動シーブ７と固定シーブ８とを接近・離隔させる油圧アクチュエータ１１が設けられている。   As described above, the drive pulley 3 has the fixed sheave 8 integrally formed or fixed on the outer periphery of the drive shaft 2 and the movable sheave 7 configured to be movable in the rotation axis direction A of the drive shaft 2. doing. Further, a V-shaped belt winding groove 3v is formed between the opposed surfaces of the fixed sheave 8 and the movable sheave 7, that is, between the tapered surface 8a of the fixed sheave 8 and the tapered surface 7a of the movable sheave 7. ing. A hydraulic actuator 11 is provided for moving the movable sheave 7 back and forth in the rotational axis direction A of the drive shaft 3 (operating in the left-right direction in FIG. 1), and moving the movable sheave 7 and the fixed sheave 8 closer to or away from each other. ing.

一方、従動プーリ５は、従動軸４の外周に一体的に形成もしくは固定された固定シーブ１０と、従動軸４の回転軸線方向Ｂに移動できるように構成された可動シーブ９とを有している。また、これら固定シーブ１０と可動シーブ９との対向面間に、すなわち固定シーブ１０のテーパ面１０ａと可動シーブ９のテーパ面９ａとの間に、Ｖ字形状のベルト巻き掛け溝５ｖが形成されている。そして、可動シーブ９を従動軸４の回転軸線方向Ｂに前後動させ（図１での左右方向に動作させ）、その可動シーブ９と固定シーブ１０とを接近・離隔させる油圧アクチュエータ１２が設けられている。   On the other hand, the driven pulley 5 has a fixed sheave 10 integrally formed or fixed on the outer periphery of the driven shaft 4 and a movable sheave 9 configured to be movable in the rotational axis direction B of the driven shaft 4. Yes. Further, a V-shaped belt winding groove 5v is formed between the opposed surfaces of the fixed sheave 10 and the movable sheave 9, that is, between the tapered surface 10a of the fixed sheave 10 and the tapered surface 9a of the movable sheave 9. ing. The movable sheave 9 is moved back and forth in the rotational axis direction B of the driven shaft 4 (operated in the left-right direction in FIG. 1), and a hydraulic actuator 12 is provided to move the movable sheave 9 and the fixed sheave 10 closer to and away from each other. ing.

上記のように構成された駆動プーリ３のベルト巻き掛け溝３ｖ、および従動プーリ５のベルト巻き掛け溝５ｖに、伝動ベルト６が巻き掛けられている。この伝動ベルト６は、例えば図２に示すようなエレメント１３を、多数それぞれ向きを揃えて環状に配列し、これをリング１４で結束して構成されている。エレメント１３は、例えば金属製の板片状の部材であって、その幅方向（図２での左右方向）における左右の両側面がエレメント１３を正面から見た状態でいわゆるＶ字状に傾斜した面として形成されていて、各プーリ３，５のＶ字形状の各ベルト巻き掛け溝３ｖ，５ｖに嵌り込むようになっている。リング１４は、例えば金属製の帯状の環状部材により形成されている。したがって、伝動ベルト６は、Ｖ字形状の各ベルト巻き掛け溝３ｖ，５ｖが形成された各プーリ３，５に巻き掛けられるＶベルトとして構成されている。   The transmission belt 6 is wound around the belt winding groove 3v of the drive pulley 3 and the belt winding groove 5v of the driven pulley 5 configured as described above. The transmission belt 6 is configured by, for example, arranging a large number of elements 13 as shown in FIG. The element 13 is, for example, a metal plate-like member, and both left and right side surfaces in the width direction (left and right direction in FIG. 2) are inclined in a so-called V shape with the element 13 viewed from the front. It is formed as a surface and is fitted into the V-shaped belt winding grooves 3v and 5v of the pulleys 3 and 5, respectively. The ring 14 is formed of, for example, a metal band-shaped annular member. Accordingly, the transmission belt 6 is configured as a V-belt that is wound around the pulleys 3 and 5 in which the V-shaped belt winding grooves 3v and 5v are formed.

このように、ベルト式無段変速機１は、互いに平行に配置された駆動プーリ３および従動プーリ５のそれぞれが、各固定シーブ８，１０と、油圧アクチュエータ１１，１２によってそれぞれ回転軸線方向Ａ，Ｂに前後動させられる各可動シーブ７，９とによって構成されている。したがって各プーリ３，５の各ベルト巻き掛け溝３ｖ，５ｖの幅が、各可動シーブ７，９を回転軸線方向Ａ，Ｂに移動させることにより変化し、それに伴って各プーリ３，５に巻掛けた伝動ベルト６の巻き掛かり半径（各プーリ３，５の有効半径）が連続的に変化し、変速比が無段階に変化するようになっている。   Thus, in the belt type continuously variable transmission 1, the driving pulley 3 and the driven pulley 5 arranged in parallel to each other are respectively connected to the rotation shedding directions A, A by the fixed sheaves 8 and 10 and the hydraulic actuators 11 and 12, respectively. The movable sheaves 7 and 9 are moved back and forth by B. Accordingly, the widths of the belt winding grooves 3v and 5v of the pulleys 3 and 5 are changed by moving the movable sheaves 7 and 9 in the rotation axis directions A and B, and accordingly, the pulleys 3 and 5 are wound around the pulleys 3 and 5. The wrapping radius (the effective radius of each pulley 3, 5) of the applied transmission belt 6 is continuously changed, and the gear ratio is continuously changed.

なお、この具体例では、従動プーリ５における油圧アクチュエータ１２には、ベルト式無段変速機１に入力されるトルクに応じた油圧（ライン圧もしくはその補正圧）が供給されている。したがって、従動プーリ５における各シーブ９，１０が伝動ベルト６を挟み付けることにより、伝動ベルト６に張力が付与され、各プーリ３，５と伝動ベルト６との挟圧力（接触圧力）が確保されるようになっている。言い換えれば、挟圧力に応じたトルク容量が設定される。これに対して、駆動プーリ３における油圧アクチュエータ１１には、設定するべき変速比に応じた圧油が供給され、目標とする変速比に応じた溝幅もしくは有効半径に設定するようになっている。   In this specific example, the hydraulic actuator 12 in the driven pulley 5 is supplied with hydraulic pressure (line pressure or its correction pressure) corresponding to the torque input to the belt type continuously variable transmission 1. Therefore, when the sheaves 9 and 10 in the driven pulley 5 pinch the transmission belt 6, tension is applied to the transmission belt 6, and a clamping pressure (contact pressure) between the pulleys 3 and 5 and the transmission belt 6 is secured. It has become so. In other words, the torque capacity corresponding to the clamping pressure is set. On the other hand, the hydraulic actuator 11 in the drive pulley 3 is supplied with pressure oil corresponding to the gear ratio to be set, and is set to the groove width or effective radius corresponding to the target gear ratio. .

前述したように、上記のように構成されたベルト式無段変速機１では、変速機本体を小型・軽量化するため、あるいは伝動ベルト６に加わる負荷を軽減するために、駆動プーリ３と従動プーリ５との軸間距離Ｌが、各プーリ３，５の外周部分が互いに干渉しない程度に可及的に短く設定されるのが望ましい。例えば図７に示すように、従来の構成のベルト式無段変速機１０１では、駆動プーリ３０の可動シーブ７０および固定シーブ８０と、従動プーリ５０の可動シーブ９０および固定シーブ１００とが、それぞれ、駆動プーリ３０と従動プーリ５０との軸間距離Ｌ０方向で互いに対向して配置されるとともに、それら駆動プーリ３０の最大外径Ｄ３０を規定する外周部分と、従動プーリ５０の最大外径Ｄ５０を規定する外周部分とが干渉しない範囲で、軸間距離Ｌ０が可及的に短くなるように構成されている。そのため、軸間距離Ｌ０を更に短縮するためには、設定可能な変速比の変化幅を犠牲にして、駆動プーリ３０の外径あるいは従動プーリ５０の外径を小さくしなければならなかった。 As described above, in the belt type continuously variable transmission 1 configured as described above, in order to reduce the size and weight of the transmission main body or reduce the load applied to the transmission belt 6, the drive pulley 3 and the driven pulley are driven. It is desirable that the distance L between the shafts with the pulley 5 is set as short as possible so that the outer peripheral portions of the pulleys 3 and 5 do not interfere with each other. For example, as shown in FIG. 7, in the belt-type continuously variable transmission 101 of the conventional configuration, the movable sheave 70 and the fixed sheave 80 of the drive pulley 30 and the movable sheave 90 and the fixed sheave 100 of the driven pulley 50 are respectively The driving pulley 30 and the driven pulley 50 are arranged to face each other in the inter-axis distance L 0 direction, and an outer peripheral portion that defines the maximum outer diameter D 30 of the driving pulley 30 and the maximum outer diameter D of the driven pulley 50. The inter-axis distance L 0 is configured to be as short as possible within a range that does not interfere with the outer peripheral portion that defines 50 . Therefore, in order to further shorten the inter-shaft distance L 0 , the outer diameter of the drive pulley 30 or the outer diameter of the driven pulley 50 must be reduced at the expense of the changeable speed ratio change width.

そこで、この発明におけるベルト式無段変速機１は、設定可能な変速比の変化幅を縮小することなく変速機本体を小型・軽量化するために、もしくは、変速機本体を大型化することなく設定可能な変速比の変化幅を拡大するために、駆動プーリ３および従動プーリ５における各可動シーブ７，９が、それら駆動プーリ３および従動プーリ５における各固定シーブ８，１０よりも外径が小さくなるように形成されている。   Therefore, the belt-type continuously variable transmission 1 according to the present invention can reduce the size and weight of the transmission main body without reducing the change width of the settable gear ratio, or without increasing the size of the transmission main body. In order to expand the changeable range of the changeable gear ratio, the movable sheaves 7 and 9 in the drive pulley 3 and the driven pulley 5 have an outer diameter larger than that of the fixed sheaves 8 and 10 in the drive pulley 3 and the driven pulley 5. It is formed to be smaller.

すなわち、図１，図２に示すように、駆動プーリ３は、可動シーブ７の外径Ｄ７が固定シーブ８の外径Ｄ８よりも小さくなるように形成されている。また、従動プーリ５は、可動シーブ９の外径Ｄ９が固定シーブ１０の外径Ｄ１０よりも小さくなるように形成されている。 That is, as shown in FIGS. 1 and 2, the drive pulley 3 is formed such that the outer diameter D 7 of the movable sheave 7 is smaller than the outer diameter D 8 of the fixed sheave 8. The driven pulley 5 is formed so that the outer diameter D 9 of the movable sheave 9 is smaller than the outer diameter D 10 of the fixed sheave 10.

具体的には、駆動プーリ３における可動シーブ７の外径Ｄ７は、可動シーブ７と固定シーブ８とが同じ外径であった場合に、それら可動シーブ７と固定シーブ８とによって構成されるベルト巻き掛け溝３ｖの溝幅が最小になる際の伝動ベルト６の巻き掛かり半径Ｒ３の２倍以上の値となるように、固定シーブ８に対して小径化されている。 Specifically, the outer diameter D 7 of the movable sheave 7 in the drive pulley 3 is configured by the movable sheave 7 and the fixed sheave 8 when the movable sheave 7 and the fixed sheave 8 have the same outer diameter. as the groove width of the belt winding grooves 3v is wound takes more than twice the value of the radius R 3 of the transmission belt 6 when a minimum, and is smaller in diameter relative to the fixed sheave 8.

同様に、従動プーリ５における可動シーブ９の外径Ｄ９は、可動シーブ９と固定シーブ１０とが同じ外径であった場合に、それら可動シーブ９と固定シーブ１０とによって構成されるベルト巻き掛け溝５ｖの溝幅が最小になる際の伝動ベルト６の巻き掛かり半径Ｒ５の２倍以上の値となるように、固定シーブ１０に対して小径化されている。 Similarly, the outer diameter D 9 of the movable sheave 9 in the driven pulley 5 is a belt winding constituted by the movable sheave 9 and the fixed sheave 10 when the movable sheave 9 and the fixed sheave 10 have the same outer diameter. as the groove width of the hanging groove 5v is wound takes more than twice the value of the radius R 5 of the transmission belt 6 when a minimum, and is smaller in diameter with respect to the fixed sheave 10.

これら各巻き掛かり半径Ｒ３，Ｒ５は、それぞれ、上記のように各ベルト巻き掛け溝３ｖ，５ｖが最小になる際に各プーリ３，５に伝動ベルト６が巻き掛かっている部分の半径、すなわち有効半径を示すものであり、言い換えると、巻き掛かり部分の各有効半径の最大値Ｒ３，Ｒ５である。 These winding radii R 3 and R 5 are the radii of the portions where the transmission belt 6 is wound around the pulleys 3 and 5 when the belt winding grooves 3v and 5v are minimized as described above. That is, it indicates the effective radius, in other words, the maximum value R 3 , R 5 of each effective radius of the winding portion.

より具体的には、特に図２に示すように、巻き掛かり半径Ｒ３は、上記のようにベルト巻き掛け溝３ｖが最小となる際に、駆動プーリ３に伝動ベルト６が巻き掛かった状態で、ベルト巻き掛け溝３ｖと伝動ベルト６とが接触する部分の範囲内での最大半径Ｒ３maxと最小半径Ｒ３minとを平均した値として規定されるものである。すなわち、巻き掛かり半径Ｒ３は、
Ｒ３＝（Ｒ３max＋Ｒ３min）／２
として表すことができる。 More specifically, as particularly shown in FIG. 2, the radius R 3 takes winding, when the belt winding grooves 3v as described above is minimized, in a state where the transmission belt 6 is applied around the driving pulley 3 The maximum radius R 3max and the minimum radius R 3min within the range of the portion where the belt winding groove 3v and the transmission belt 6 are in contact are defined as an average value. That is, the radius R 3 takes winding,
R 3 = (R 3max + R 3min ) / 2
Can be expressed as

同様に、巻き掛かり半径Ｒ５は、上記のようにベルト巻き掛け溝５ｖが最小となる際に、従動プーリ５に伝動ベルト６が巻き掛かった状態で、ベルト巻き掛け溝５ｖと伝動ベルト６とが接触する部分の範囲内での最大半径Ｒ５maxと最小半径Ｒ５minとを平均した値として規定されるものである。すなわち、巻き掛かり半径Ｒ５は、
Ｒ５＝（Ｒ５max＋Ｒ５min）／２
として表すことができる。 Similarly, the radius R 5 takes winding, when the belt winding grooves 5v as described above is minimized, in a state where the transmission belt 6 is applied around the driven pulley 5, the belt winding grooves 5v and the transmission belt 6 Is defined as an average value of the maximum radius R 5max and the minimum radius R 5min within the range of the portion in contact with each other. That is, the radius R 5 takes winding,
R 5 = (R 5max + R 5min) / 2
Can be expressed as

したがって、駆動プーリ３における可動シーブ７の外径Ｄ７は、
（Ｒ３max＋Ｒ３min）≦Ｄ７＜Ｄ８
の条件を満たすように、固定シーブ８に対して小径化される。その場合、可動シーブ７の外径Ｄ７は可及的に小さくするのが効果的であるので、この図２に示す具体例では、可動シーブ７の外径Ｄ７は、
Ｄ７＝（Ｒ３max＋Ｒ３min）＝２・Ｒ３
として設定されている。このことは言い換えると、固定シーブ８に対して可動シーブ７の外径Ｄ７を小径化させる際には、伝動ベルト６の巻き掛かり半径Ｒ３すなわち駆動プーリ３のベルト巻き掛かり部分の有効半径の最大値Ｒ３は、その値が維持される、もしくはその値が小さくなることはない、と言うことができる。 Therefore, the outer diameter D 7 of the movable sheave 7 in the drive pulley 3 is
(R 3max + R 3min ) ≦ D 7 <D 8
The diameter of the fixed sheave 8 is reduced so as to satisfy the following condition. In that case, since the outer diameter D 7 of the movable sheave 7 is effective to reduce as much as possible, in the specific example shown in FIG. 2, the outer diameter D 7 of the movable sheave 7,
D 7 = (R 3max + R 3min ) = 2 · R 3
Is set as In other words, when the outer diameter D 7 of the movable sheave 7 is made smaller than the fixed sheave 8, the winding radius R 3 of the transmission belt 6, that is, the effective radius of the belt winding portion of the drive pulley 3 is reduced. the maximum value R 3, the value is maintained, or it is not the value decreases, it can be said that.

同様に、従動プーリ５における可動シーブ９の外径Ｄ９は、
（Ｒ５max＋Ｒ５min）≦Ｄ９＜Ｄ１０
の条件を満たすように、固定シーブ１０に対して小径化される。その場合、可動シーブ９の外径Ｄ９は可及的に小さくするのが効果的であるので、この図２に示す具体例では、可動シーブ９の外径Ｄ９は、
Ｄ９＝（Ｒ５max＋Ｒ５min）＝２・Ｒ５
として設定されている。このことは言い換えると、固定シーブ１０に対して可動シーブ９の外径Ｄ９を小径化させる際には、伝動ベルト６の巻き掛かり半径Ｒ５すなわち従動プーリ５のベルト巻き掛かり部分の有効半径の最大値Ｒ５は、その値が維持される、もしくはその値が小さくなることはない、と言うことができる。 Similarly, the outer diameter D 9 of the movable sheave 9 in the driven pulley 5,
(R 5max + R 5min) ≦ D 9 <D 10
The diameter of the fixed sheave 10 is reduced so as to satisfy the following condition. In that case, since the outer diameter D 9 of the movable sheave 9 is effective to reduce as much as possible, in the specific example shown in FIG. 2, the outer diameter D 9 of the movable sheave 9,
D 9 = (R 5max + R 5min ) = 2 · R 5
Is set as In other words, when the outer diameter D 9 of the movable sheave 9 is reduced with respect to the fixed sheave 10, the winding radius R 5 of the transmission belt 6, that is, the effective radius of the belt winding portion of the driven pulley 5 is reduced. the maximum value R 5, its value is maintained, or is never smaller the value, it can be said that.

このように、駆動プーリ３および従動プーリ５の各可動シーブ７，９が、それら各プーリ３，５の各固定シーブ８，１０よりも小径に形成される。そのため、各可動シーブ７，９と各固定シーブ８，１０とが同じ外径で形成される場合と比較して、各可動シーブ７，９の外径Ｄ７，Ｄ９が小径化された分だけ、それら各可動シーブ７，９を軽量化することができ、ひいてはこのベルト式無段変速機１の軽量化を図ることができる。 In this manner, the movable sheaves 7 and 9 of the driving pulley 3 and the driven pulley 5 are formed with a smaller diameter than the fixed sheaves 8 and 10 of the pulleys 3 and 5. Therefore, compared to the case where the movable sheaves 7 and 9 and the fixed sheaves 8 and 10 are formed with the same outer diameter, the outer diameters D 7 and D 9 of the movable sheaves 7 and 9 are reduced. Therefore, it is possible to reduce the weight of each of the movable sheaves 7 and 9 and to reduce the weight of the belt type continuously variable transmission 1.

さらに、この発明におけるベルト式無段変速機１は、上記のように駆動プーリ３および従動プーリ５が、それぞれ、各可動シーブ７，９の外径Ｄ７，Ｄ９が各固定シーブ８，１０の外径Ｄ８，Ｄ１０よりも小さくなるように形成されているとともに、図１、および図３に拡大して示すように、駆動プーリ３の固定シーブ８の外周部分８ｏと従動プーリ５の固定シーブ１０の外周部分１０ｏとが、各回転軸２，４の軸間距離Ｌ方向で互いオーバーラップするように、駆動プーリ３および従動プーリ５が配置されている。 Further, in the belt type continuously variable transmission 1 according to the present invention, as described above, the driving pulley 3 and the driven pulley 5 have the outer diameters D 7 and D 9 of the movable sheaves 7 and 9 respectively fixed to the fixed sheaves 8 and 10. Are formed so as to be smaller than the outer diameters D 8 and D 10 , and as shown in an enlarged manner in FIGS. 1 and 3, the outer peripheral portion 8 o of the fixed sheave 8 of the driving pulley 3 and the driven pulley 5 The drive pulley 3 and the driven pulley 5 are arranged so that the outer peripheral portion 10o of the fixed sheave 10 overlaps with each other in the direction of the inter-axis distance L between the rotary shafts 2 and 4.

上記のように、各プーリ３，５の各可動シーブ７，９が、各固定シーブ８，１０よりも小径に形成されることにより、各可動シーブ７，９と、それら各可動シーブ７，９に各回転軸２，４の軸間距離Ｌ方向でそれぞれ対向する各固定シーブ１０，８との間に、スペースが生じる。すなわち、駆動プーリ３の可動シーブ７と従動プーリ５の固定シーブ１０とが、各回転軸２，４の軸間距離Ｌ方向で対向する部分、および、従動プーリ５の可動シーブ９と駆動プーリ３の固定シーブ８とが、各回転軸２，４の軸間距離Ｌ方向で対向する部分には、各可動シーブ７，９がそれぞれ各固定シーブ８，１０に対して小径化された分だけスペースが生じる。   As described above, each movable sheave 7, 9 of each pulley 3, 5 is formed with a smaller diameter than each fixed sheave 8, 10, so that each movable sheave 7, 9 and each of these movable sheaves 7, 9 A space is created between each of the rotating sheaves 2 and 4 and the fixed sheaves 10 and 8 facing each other in the direction of the inter-axis distance L. That is, the movable sheave 7 of the drive pulley 3 and the fixed sheave 10 of the driven pulley 5 are opposed to each other in the inter-axis distance L direction of the rotary shafts 2 and 4, and the movable sheave 9 of the driven pulley 5 and the drive pulley 3. The portion of the movable sheaves 7 and 9 that is opposed to the fixed sheaves 8 in the direction of the inter-axis distance L between the rotary shafts 2 and 4 has a space corresponding to the diameter of the movable sheaves 7 and 9 that is reduced relative to the fixed sheaves 8 and 10, respectively. Occurs.

したがって、上記のようにして生じたスペースを埋めるように、駆動プーリ３と従動プーリ５と互いに近づけて配置することにより、それら駆動プーリ３と従動プーリ５との距離、すなわち駆動軸２と従動軸４との間の軸間距離Ｌを短縮することができる。その結果、このベルト式無段変速機１の体格を小型化し、またそれに伴ってこのベルト式無段変速機１の重量を軽量化することができる。なおその場合、前述したように、各固定シーブ８，１０に対して各可動シーブ７，９をそれぞれ小径化させる際には、各プーリ３，５の有効半径の最大値Ｒ３，Ｒ５が小さくなることはないので、このベルト式無段変速機１で設定可能な変速比の変化幅が縮小することはない。 Therefore, by disposing the drive pulley 3 and the driven pulley 5 close to each other so as to fill the space generated as described above, the distance between the drive pulley 3 and the driven pulley 5, that is, the drive shaft 2 and the driven shaft. The distance L between the axes 4 can be shortened. As a result, the size of the belt type continuously variable transmission 1 can be reduced, and the weight of the belt type continuously variable transmission 1 can be reduced accordingly. In the case that, as described above, when causing reduced diameter of each of the movable sheaves 7 and 9 respectively are each fixed sheave 8 and 10, the maximum value R 3, R 5 the effective radius of each pulley 3, 5 Since it does not become smaller, the change width of the gear ratio that can be set by the belt type continuously variable transmission 1 is not reduced.

これに対して、駆動軸２と従動軸４との間の軸間距離Ｌはそのままで、上記のようにして生じたスペースを埋めるように、各プーリ３，５における各固定シーブ８，１０の外径Ｄ８，Ｄ１０を大きくした場合は、各プーリ３，５の有効半径の最大値Ｒ３，Ｒ５を大きくすることができる。その結果、このベルト式無段変速機１で設定可能な変速比の変化幅を拡大することができる。 On the other hand, the distance L between the drive shaft 2 and the driven shaft 4 remains the same, and the fixed sheaves 8 and 10 in the pulleys 3 and 5 are filled so as to fill the space generated as described above. When the outer diameters D 8 and D 10 are increased, the maximum effective values R 3 and R 5 of the pulleys 3 and 5 can be increased. As a result, it is possible to expand the range of change of the gear ratio that can be set by the belt type continuously variable transmission 1.

図４，図５，図６に、このベルト式無段変速機１における変速比γと、各プーリ３，５に対する伝動ベルト６の芯ずれ量との関係、および、ベルト式無段変速機１で芯ずれが生じた場合の伝動ベルト６各部の挙動について示してある。図４に示すように、ベルト式無段変速機１では、変速比γが最大の場合（γ＝γmax）および変速比γが最小の場合（γ＝γmin）に、その芯ずれ量が最も多くなるように設定されている。そして、図４，図５に示すように、それら最大変速比γmaxの場合の芯ずれと、最小変速比γminの場合の芯ずれとは、共に同じ方向に発生するようになっている。   4, 5, and 6 show the relationship between the speed ratio γ in the belt-type continuously variable transmission 1 and the misalignment amount of the transmission belt 6 with respect to the pulleys 3 and 5, and the belt-type continuously variable transmission 1. The behavior of each part of the transmission belt 6 when misalignment occurs is shown. As shown in FIG. 4, the belt type continuously variable transmission 1 has the largest misalignment when the speed ratio γ is maximum (γ = γmax) and when the speed ratio γ is minimum (γ = γmin). It is set to be. 4 and 5, the misalignment in the case of the maximum gear ratio γmax and the misalignment in the case of the minimum gear ratio γmin both occur in the same direction.

したがって、芯ずれが最も多く発生する最大変速比γmaxもしくは最小変速比γminの場合には、図６に示すように、プーリ３（もしくは５）に対して伝動ベルト６におけるエレメント１３のベルト幅方向（図４，図５での左右方向）の中心が、可動シーブ９（もしくは７）側（図４，図５での右側）にずれる芯ずれが発生する。このとき、エレメント１３が可動シーブ９（もしくは７）側に芯ずれすることに伴い、伝動ベルト６における各リング１４は、固定シーブ１０（もしくは８）側（図４，図５での左側）に相対移動することになる。その結果、リング１４の側端部が、エレメント１３の首部１３ａと固定シーブ１０（もしくは８）のテーパー面１０ａ（もしくは８ａ）とに当接するもしくは当接する方向に移動する。   Therefore, in the case of the maximum speed ratio γmax or the minimum speed ratio γmin where the misalignment occurs most, as shown in FIG. 6, the belt width direction of the element 13 in the transmission belt 6 (or 5) with respect to the pulley 3 (or 5) ( A misalignment occurs in which the center in the left-right direction in FIGS. 4 and 5 is shifted to the movable sheave 9 (or 7) side (the right side in FIGS. 4 and 5). At this time, as the element 13 is misaligned to the movable sheave 9 (or 7) side, each ring 14 in the transmission belt 6 is moved to the fixed sheave 10 (or 8) side (left side in FIGS. 4 and 5). It will move relative. As a result, the side end portion of the ring 14 abuts on the neck portion 13a of the element 13 and the tapered surface 10a (or 8a) of the fixed sheave 10 (or 8), or moves in the abutment direction.

仮に、駆動プーリ３および従動プーリ５における各固定シーブ８，１０が、各可動シーブ７，９に対して小径化されたとすると、上記のように最大変速比γmaxもしくは最小変速比γminの状態で芯ずれが生じ、固定シーブ１０（もしくは８）のテーパー面１０ａ（もしくは８ａ）に伝動ベルト６のリング１４の側端部が当接する際に、固定シーブ１０（もしくは８）からリング１４が脱落してしまう可能性が生じてしまう。すなわち、最大変速比γmaxもしくは最小変速比γminの状態で芯ずれが生じた際に、プーリ３（もしくは５）からの伝動ベルト６のリング１４の脱落防止に寄与するのは、各固定シーブ８，１０であり、各可動シーブ７，９は、そのリング１４の脱落防止には関与していない。そのため、この発明では、各固定シーブ８，１０を小径化するのではなく、駆動プーリ３および従動プーリ５における各可動シーブ７，９が、各固定シーブ８，１０に対して小径化されている。   If the fixed sheaves 8 and 10 in the driving pulley 3 and the driven pulley 5 are reduced in diameter relative to the movable sheaves 7 and 9, the core is maintained in the state of the maximum speed ratio γmax or the minimum speed ratio γmin as described above. When the side end of the ring 14 of the transmission belt 6 comes into contact with the tapered surface 10a (or 8a) of the fixed sheave 10 (or 8), the ring 14 is dropped from the fixed sheave 10 (or 8). The possibility to end up arises. That is, when the center deviation occurs in the state of the maximum speed ratio γmax or the minimum speed ratio γmin, each fixed sheave 8, which contributes to preventing the ring 14 of the transmission belt 6 from falling off the pulley 3 (or 5). 10. Each movable sheave 7, 9 is not involved in preventing the ring 14 from falling off. Therefore, in the present invention, the diameters of the fixed sheaves 8 and 10 are not reduced, but the movable sheaves 7 and 9 in the drive pulley 3 and the driven pulley 5 are reduced in diameter relative to the fixed sheaves 8 and 10. .

以上のように、この発明に係るベルト式無段変速機１によれば、駆動プーリ３および従動プーリ５の各可動シーブ７，９が、それぞれ、それら各プーリ３，５の各固定シーブ８，１０よりも小径に形成される。そして、各可動シーブ７，９を小径化させることによって駆動プーリ３と従動プーリ５との間に生じた空間を利用して、駆動プーリ３側の固定シーブ８の外周部分８ｏと、従動プーリ５側の固定シーブ１０の外周部分１０ｏとを、各プーリ３，５の軸間距離Ｌ方向、すなわち各プーリ３，５の各回転軸２，４の両方に垂直な方向で互いオーバーラップさせる位置に、それら駆動プーリ３と従動プーリ５とが配置される。したがって、各可動シーブ７，９の外径Ｄ７，Ｄ９が小径化された分、駆動プーリ３と従動プーリ５との軸間距離Ｌを短縮することが可能になる。 As described above, according to the belt-type continuously variable transmission 1 according to the present invention, the movable sheaves 7 and 9 of the driving pulley 3 and the driven pulley 5 are respectively connected to the fixed sheaves 8 of the pulleys 3 and 5. The diameter is smaller than 10. Then, by using the space generated between the drive pulley 3 and the driven pulley 5 by reducing the diameter of each movable sheave 7, 9, the outer peripheral portion 8 o of the fixed sheave 8 on the drive pulley 3 side and the driven pulley 5. The outer peripheral portion 10o of the fixed sheave 10 on the side is overlapped with each other in the direction of the inter-axis distance L of the pulleys 3 and 5, that is, in the direction perpendicular to both the rotation shafts 2 and 4 of the pulleys 3 and 5. The drive pulley 3 and the driven pulley 5 are arranged. Therefore, amount that the outer diameter D 7, D 9 of the movable sheave 7 and 9 is smaller in diameter, it is possible to shorten the inter-axis distance L between the drive pulley 3 and the driven pulley 5.

この場合、各プーリ３，５に伝動ベルト６が巻き掛かる際の伝動ベルト６の巻き掛かり半径の最大値Ｒ３，Ｒ５を規定する各固定シーブ８，１０の外径Ｄ８，Ｄ１０は維持されるので、ベルトの巻き掛かり半径の最大値が減少されることがない。すなわち、伝動ベルト６の巻き掛かり半径の変化幅、言い換えるとベルト式無段変速機１として設定可能な変速比の変化幅が縮小することはない。そのため、設定可能な変速比の変化幅を縮小することなく、このベルト式無段変速機１を小型・軽量化することができる。 In this case, the outer diameters D 8 and D 10 of the fixed sheaves 8 and 10 that define the maximum wrapping radii R 3 and R 5 of the transmission belt 6 when the transmission belt 6 is wound around the pulleys 3 and 5 are: Since this is maintained, the maximum value of the wrapping radius of the belt is not reduced. That is, the change width of the wrapping radius of the transmission belt 6, in other words, the change width of the transmission ratio that can be set as the belt-type continuously variable transmission 1 is not reduced. Therefore, the belt-type continuously variable transmission 1 can be reduced in size and weight without reducing the changeable range of the changeable gear ratio.

もしくは、各可動シーブ７，９を小径化させることによって駆動プーリ３と従動プーリ５との間に生じた空間を利用して、それら各可動シーブ７，９に各プーリ３，５の軸間距離Ｌ方向でそれぞれ対向する各固定シーブ８，１０の外径Ｄ８，Ｄ１０を大きくすることができる。その結果、各可動シーブ７，９の外径Ｄ７，Ｄ９が小径化された分、駆動プーリ３と従動プーリ５との軸間距離Ｌを維持しつつ、すなわち軸間距離Ｌを延長させることなく、各固定シーブ８，１０の外径Ｄ８，Ｄ１０を大径化して伝動ベルト６の巻き掛かり半径の変化幅を広げることができる。そのため、このベルト式無段変速機１を大型化することなく、設定可能な変速比の変化幅を拡大することができる。 Alternatively, by using the space generated between the driving pulley 3 and the driven pulley 5 by reducing the diameter of each movable sheave 7, 9, the distance between the axes of the pulleys 3, 5 is set in each movable sheave 7, 9. The outer diameters D 8 and D 10 of the fixed sheaves 8 and 10 facing each other in the L direction can be increased. As a result, as the outer diameters D 7 and D 9 of the movable sheaves 7 and 9 are reduced, the distance L between the driving pulley 3 and the driven pulley 5 is maintained, that is, the distance L between the axes is extended. The outer diameters D 8 and D 10 of the fixed sheaves 8 and 10 can be increased without increasing the winding radius of the transmission belt 6. Therefore, the changeable range of the changeable gear ratio can be expanded without increasing the size of the belt type continuously variable transmission 1.

１…ベルト式無段変速機、 ２…駆動軸（駆動側の回転軸）、 ３…駆動プーリ、 ３ｖ…ベルト巻き掛け溝（駆動側ベルト巻き掛け溝）、 ４…従動軸（従動側の回転軸）、 ５…従動プーリ、 ５ｖ…ベルト巻き掛け溝（従動側ベルト巻き掛け溝）、 ６…伝動ベルト、 ７…可動シーブ（駆動側可動シーブ）、 ８…固定シーブ（駆動側固定シーブ）、 ９…可動シーブ（従動側可動シーブ）、 １０…固定シーブ（従動側固定シーブ）、 Ａ，Ｂ…回転軸線方向、 Ｄ７…駆動側可動シーブの外径、 Ｄ８…駆動側固定シーブの外径、 Ｄ９…従動側可動シーブの外径、 Ｄ１０…従動側固定シーブの外径、 Ｌ…軸間距離。 DESCRIPTION OF SYMBOLS 1 ... Belt type continuously variable transmission, 2 ... Drive shaft (drive side rotation shaft), 3 ... Drive pulley, 3v ... Belt winding groove (drive side belt winding groove), 4 ... Drive shaft (driven side rotation) Shaft), 5 ... driven pulley, 5v ... belt winding groove (driven belt winding groove), 6 ... transmission belt, 7 ... movable sheave (drive side movable sheave), 8 ... fixed sheave (drive side fixed sheave), 9 ... movable sheave (driven side movable sheave), 10 ... fixed sheave (driven side fixed sheave), a, B ... rotational axis direction, the outer diameter of D 7 ... drive side movable sheave, D 8 ... outside the drive side fixed sheave diameter, D 9 ... outer diameter of the driven side movable sheave, D 10 ... outer diameter of the driven-side fixed sheave, L ... distance between the axes.

Claims (3)

駆動側の回転軸に対してその回転軸線方向に移動可能に取り付けられた駆動側可動シーブと該回転軸線方向に移動不可能に取り付けられた駆動側固定シーブとによって駆動側ベルト巻き掛け溝を構成する駆動プーリと、前記駆動側の回転軸に平行な従動側の回転軸に対してその回転軸線方向に移動可能に取り付けられた従動側可動シーブと該回転軸線方向に移動不可能に取り付けられた従動側固定シーブとによって従動側ベルト巻き掛け溝を構成する従動プーリと、前記駆動プーリと前記従動プーリとに巻き掛けられてそれらの間で動力を伝達する伝動ベルトとを備えているとともに、前記駆動側可動シーブと前記従動側固定シーブとが、および前記駆動側固定シーブと前記従動側可動シーブとが、それぞれ前記各回転軸の軸間距離方向で互いに対向して配置されており、前記各可動シーブを前記回転軸線方向に前後動させて前記各ベルト巻き掛け溝の溝幅を変化させることにより、前記各プーリに対する前記伝動ベルトの巻き掛かり半径を変化させて変速比を連続的に変更するベルト式無段変速機において、
前記駆動プーリおよび前記従動プーリは、
前記駆動側可動シーブの外径が前記駆動側固定シーブの外径よりも小さく、かつ前記従動側可動シーブの外径が前記従動側固定シーブの外径よりも小さくなるように形成されているとともに、
前記駆動側固定シーブの外周部分と前記従動側固定シーブの外周部分とが前記軸間距離方向で互いオーバーラップして配置されていることを特徴とするベルト式無段変速機。 A drive-side belt winding groove is constituted by a drive-side movable sheave attached to the drive-side rotation shaft so as to be movable in the direction of the rotation axis and a drive-side fixed sheave attached so as not to be movable in the direction of the rotation axis. And a driven movable sheave attached to the driven side rotating shaft parallel to the driving side rotating shaft so as to be movable in the direction of the rotating axis, and attached so as to be immovable in the direction of the rotating axis. A driven pulley that constitutes a driven-side belt winding groove by a driven-side fixed sheave, a drive belt that is wound around the drive pulley and the driven pulley and transmits power between them, and The drive-side movable sheave and the driven-side fixed sheave, and the drive-side fixed sheave and the driven-side movable sheave are each in the inter-axis distance direction of the respective rotary shafts. And the movable sheave is moved back and forth in the direction of the rotational axis to change the groove width of each belt winding groove, whereby the winding radius of the transmission belt with respect to each pulley is increased. In a belt-type continuously variable transmission that changes the gear ratio continuously by changing it,
The drive pulley and the driven pulley are:
The outer diameter of the drive-side movable sheave is smaller than the outer diameter of the drive-side fixed sheave, and the outer diameter of the driven-side movable sheave is smaller than the outer diameter of the driven-side fixed sheave. ,
A belt type continuously variable transmission, wherein an outer peripheral portion of the driving side fixed sheave and an outer peripheral portion of the driven side fixed sheave are arranged so as to overlap each other in the inter-axis distance direction. 前記駆動プーリおよび前記従動プーリにおける前記各可動シーブの外径は、それぞれ、前記各可動シーブと前記各固定シーブとが同径であった場合の前記各巻き掛かり半径の最大値の２倍よりも大きいことを特徴とする請求項１に記載のベルト式無段変速機。   The outer diameter of each movable sheave in the drive pulley and the driven pulley is greater than twice the maximum value of each winding radius when each movable sheave and each fixed sheave have the same diameter. The belt-type continuously variable transmission according to claim 1, wherein the belt-type continuously variable transmission is large. 前記駆動プーリおよび前記従動プーリにおける前記各巻き掛かり半径は、それぞれ前記各ベルト巻き掛け溝が最小となる際に前記各プーリに前記伝動ベルトが巻き掛かった状態で前記各ベルト巻き掛け溝と前記伝動ベルトとが接触する部分の範囲内での最大半径と最小半径とを平均した値であることを特徴とする請求項２に記載のベルト式無段変速機。   The winding radii of the driving pulley and the driven pulley are set so that the belt winding groove and the transmission are in a state where the transmission belt is wound around the pulley when the belt winding groove is minimized. 3. The belt-type continuously variable transmission according to claim 2, wherein the belt-type continuously variable transmission has a value obtained by averaging a maximum radius and a minimum radius within a range of a portion in contact with the belt.
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