JP2006153046A - V-belt, element for v-belt, and pulley for v-belt - Google Patents

V-belt, element for v-belt, and pulley for v-belt Download PDF

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JP2006153046A
JP2006153046A JP2004340635A JP2004340635A JP2006153046A JP 2006153046 A JP2006153046 A JP 2006153046A JP 2004340635 A JP2004340635 A JP 2004340635A JP 2004340635 A JP2004340635 A JP 2004340635A JP 2006153046 A JP2006153046 A JP 2006153046A
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belt
pulley
friction
sheave
portions
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JP4525910B2 (en
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Tatsuya Matsunami
辰哉 松波
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Toyota Motor Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G5/00—V-belts, i.e. belts of tapered cross-section
    • F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several parts
    • F16G5/163—V-belts, i.e. belts of tapered cross-section consisting of several parts with means allowing lubrication

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a V-belt, an element for the V-belt, and a pulley for the V-belt constituting a compact belt type continuously variable transmission capable of corresponding to high torque and reducing its weight. <P>SOLUTION: Each top part 24 of each projecting part 22 in a friction part 13 on both sides in the direction of width is eccentric on a shaft axis side of the pulley. Consequently, friction force between the friction part 13 and a sheave face when the element moves onto the shaft axis side of the pulley for the pulley is larger than friction force between the friction part 13 and the sheave face when the element moves onto an outer peripheral side of the pulley for the pulley. As a result, it is sufficient with small nipping force by a pair of sheaves, and it is unnecessary to increase rigidity of the pulley even when corresponding to high torque to constitute the compact belt type continuously variable transmission being light in weight. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、Ｖベルト、Ｖベルト用エレメント及びＶベルト用プーリに関して、特に、ベルト式無段変速機に用いられるＶベルト、Ｖベルト用エレメント及びＶベルト用プーリに関する。   The present invention relates to a V-belt, a V-belt element, and a V-belt pulley, and more particularly to a V-belt, a V-belt element, and a V-belt pulley used in a belt-type continuously variable transmission.

従来から、車両に搭載される自動変速機としてベルト式無段変速機（ＣＶＴ）が知られている。一般に、ベルト式無段変速機は、入力側プーリと出力側プーリとにＶベルト（金属製無端ベルト）が巻回されて、油圧によって各プーリの各シーブを各プーリの軸心方向へ駆動して各プーリの溝幅を変化させることで各プーリの有効径を制御して、入力側軸と出力側軸との回転数比、即ち変速比を連続的に無段階で変化させる。このようなベルト式無段変速機に用いられるＶベルトは、板状に形成された複数個のエレメントが相互に板厚方向へ整列されて、各エレメントの両肩部に金属製のフープが掛けられて各エレメントが結束されることで構成される。そして、このようなＶベルトは、各エレメントの基部の幅方向（各プーリの軸心方向）両側面に、同一軸心上に設けられた各シーブの対向する各シーブ面に接触させる接触面が形成される。ところで、上記ベルト式無段変速機は、従来、出力が比較的小さいエンジンに組み合わされていた。   Conventionally, a belt type continuously variable transmission (CVT) is known as an automatic transmission mounted on a vehicle. Generally, in a belt type continuously variable transmission, a V belt (metal endless belt) is wound around an input pulley and an output pulley, and each sheave of each pulley is driven in the axial direction of each pulley by hydraulic pressure. Thus, the effective diameter of each pulley is controlled by changing the groove width of each pulley, and the rotation speed ratio between the input side shaft and the output side shaft, that is, the gear ratio is continuously changed continuously. A V-belt used in such a belt-type continuously variable transmission has a plurality of plate-shaped elements aligned in the plate thickness direction, and metal hoops are hung on both shoulders of each element. And each element is bundled. Such a V-belt has contact surfaces that are brought into contact with respective sheave surfaces facing each sheave provided on the same axial center on both side surfaces of the base portion of each element (axial direction of each pulley). It is formed. By the way, the belt type continuously variable transmission has been conventionally combined with an engine having a relatively small output.

ところが、ベルト式無段変速機は、車両の対環境性能、並びに走行性能を向上させることができるため、近年、高出力（高トルク）型エンジンと組み合わせることが要望されている。そこで、特許文献１に記載のエレメントでは、板状エレメントのうちプーリ壁面との接触面であるエレメント側面に板厚方向に一致又は近似する方向の突部及び溝部を交互に設けると共に、プーリ壁面と接触する突部表面を凹凸に形成して、エレメント壁面とプーリ壁面との間の摩擦力を効率的に得るようにしている。しかしながら、高出力型エンジンにベルト式無段変速機を組み合わせる場合、即ち、Ｖベルトによって高トルクを伝達する場合には、フープの張力が増大してエレメントが各プーリに対してプーリ軸心側へ押し込まれる力が大きくなるため、一対のシーブによってＶベルトを挟み込む力（以下、挟圧力と称する。）を高めて、Ｖベルトが各プーリに対してプーリ軸心側へ入り込むことを防ぐ必要がある。   However, since the belt type continuously variable transmission can improve the environmental performance and the running performance of the vehicle, in recent years, it has been demanded to be combined with a high output (high torque) type engine. Therefore, in the element described in Patent Document 1, protrusions and grooves in a direction that matches or approximates the plate thickness direction are alternately provided on the side surface of the element that is a contact surface with the pulley wall surface among the plate-like elements, and the pulley wall surface and The surface of the projecting portion that comes into contact is formed with irregularities so that the frictional force between the element wall surface and the pulley wall surface is efficiently obtained. However, when a belt type continuously variable transmission is combined with a high output type engine, that is, when high torque is transmitted by a V-belt, the tension of the hoop increases and the element moves toward the pulley axis with respect to each pulley. Since the force to be pushed increases, it is necessary to increase the force for sandwiching the V-belt by the pair of sheaves (hereinafter referred to as the clamping pressure) to prevent the V-belt from entering the pulley axis with respect to each pulley. .

さらに、Ｖベルトによって高トルクを伝達する場合には、高められたＶベルトの挟圧力に対応させて各プーリの剛性を高めて、当該プーリの破損を防ぐ必要がある。しかしながら、各プーリの剛性を高めるためには、各プーリの肉厚を増やす等の対策を施す必要があり、変速機が重量化、且つ大型化されると共に製造コストが増大される。
特開平１０−１１５３４９号公報（段落番号００２９〜００３５、図１） Further, when high torque is transmitted by the V-belt, it is necessary to increase the rigidity of each pulley in accordance with the increased clamping pressure of the V-belt and prevent the pulley from being damaged. However, in order to increase the rigidity of each pulley, it is necessary to take measures such as increasing the thickness of each pulley, which increases the weight and size of the transmission and increases the manufacturing cost.
JP-A-10-115349 (paragraph numbers 0029 to 0035, FIG. 1)

そこで本発明は、上記事情に鑑みてなされたもので、第１の目的は、高トルクに対応可能なベルト式無段変速機が、軽量、且つコンパクトに構成されるＶベルトを提供することにある。
また、第２の目的は、高トルクに対応可能なベルト式無段変速機が、軽量、且つコンパクトに構成されるＶベルト用エレメントを提供することにある。
さらに、第３の目的は、高トルクに対応可能なベルト式無段変速機が、軽量、且つコンパクトに構成されるＶベルト用プーリを提供することにある。 Therefore, the present invention has been made in view of the above circumstances, and a first object is to provide a V-belt in which a belt-type continuously variable transmission capable of handling high torque is configured to be lightweight and compact. is there.
A second object is to provide a V-belt element in which a belt-type continuously variable transmission capable of handling high torque is configured to be lightweight and compact.
A third object is to provide a V-belt pulley in which a belt-type continuously variable transmission capable of handling high torque is configured to be lightweight and compact.

上記第１の目的を達成するために、本発明のうち請求項１に記載の発明は、溝幅が可変であるプーリの一対のシーブ面によってベルト幅方向両側の摩擦部が挟圧されるＶベルトであって、該Ｖベルトの摩擦部は、Ｖベルトがプーリに対してプーリ軸心側へ移動する時のシーブ面との間の摩擦力が、Ｖベルトがプーリに対してプーリ外周側へ移動する時のシーブ面との間の摩擦力よりも大きく設定されることを特徴とする。   In order to achieve the first object, according to the first aspect of the present invention, the friction portions on both sides in the belt width direction are clamped by a pair of sheave surfaces of a pulley having a variable groove width. The friction portion of the V-belt has a frictional force between the V-belt and the sheave surface when the V-belt moves toward the pulley axis with respect to the pulley. It is characterized by being set larger than the frictional force between the sheave surface when moving.

上記第１の目的を達成するために、本発明のうち請求項２に記載の発明は、溝幅が可変であるプーリの一対のシーブ面によって挟圧されるＶベルトのベルト幅方向両側の摩擦部に、ベルト長さ方向へ延びる凸部と凹部とが交互に設けられるＶベルトであって、該Ｖベルトの凸部は、シーブ面に接触させる頂部がプーリ軸心側へ偏倚されて形成されることを特徴とする。
請求項３に記載の発明は、請求項２に記載のＶベルトにおいて、Ｖベルトの各摩擦部が凸部と凹部とが交互に設けられる波形に形成されて、凸部の頂部は、プーリ軸心側の曲率がプーリ外周側の曲率よりも小さく形成されることを特徴とする。
請求項４に記載の発明は、請求項１〜３のいずれかに記載のＶベルトにおいて、ベルト式無段変速機に用いられることを特徴とする。 In order to achieve the first object, the invention according to claim 2 of the present invention is characterized in that the friction on both sides in the belt width direction of the V-belt sandwiched between a pair of sheave surfaces of a pulley having a variable groove width. The belt is provided with a convex portion and a concave portion extending alternately in the belt length direction, and the convex portion of the V belt is formed such that the top portion contacting the sheave surface is biased toward the pulley axis. It is characterized by that.
According to a third aspect of the present invention, in the V-belt according to the second aspect, each friction portion of the V-belt is formed in a waveform in which convex portions and concave portions are alternately provided, and the top portion of the convex portion is a pulley shaft. The center side curvature is formed smaller than the curvature on the pulley outer periphery side.
According to a fourth aspect of the present invention, the V-belt according to any one of the first to third aspects is used for a belt-type continuously variable transmission.

上記第２の目的を達成するために、本発明のうち請求項５に記載の発明は、溝幅が可変であるプーリの一対のシーブ面によってベルト幅方向両側の摩擦部が挟圧されるＶベルトに用いられるエレメントであって、Ｖベルトの摩擦部を構成するエレメントの摩擦部は、エレメントがプーリに対してプーリ軸心側へ移動する時のシーブ面との間の摩擦力が、エレメントがプーリに対してプーリ外周側へ移動する時のシーブ面との間の摩擦力よりも大きく設定されることを特徴とする。   In order to achieve the second object, in the invention according to claim 5 of the present invention, the friction portions on both sides in the belt width direction are clamped by a pair of sheave surfaces of a pulley having a variable groove width. The friction part of the element that is used for the belt and constitutes the friction part of the V-belt has a frictional force between the element and the sheave surface when the element moves toward the pulley axis with respect to the pulley. The frictional force between the pulley and the sheave surface when moving toward the pulley outer periphery is set to be larger.

上記第２の目的を達成するために、本発明のうち請求項６に記載の発明は、溝幅が可変であるプーリの一対のシーブ面によってベルト幅方向両側の摩擦部が挟圧されるＶベルトに用いられて、Ｖベルトの摩擦部を構成するエレメントの摩擦部にエレメント厚さ方向へ延びる凸部と凹部とが交互に設けられるＶベルト用エレメントであって、該エレメントの凸部は、シーブ面に接触させる頂部がプーリ軸心側へ偏倚されて形成されることを特徴とする。
請求項７に記載の発明は、請求項６に記載のＶベルト用エレメントにおいて、エレメントの各摩擦部が凸部と凹部とが交互に設けられる波形に形成されて、エレメントの凸部の頂部は、プーリ軸心側の曲率がプーリ外周側の曲率よりも小さく形成されることを特徴とする。 In order to achieve the second object, in the invention according to claim 6 of the present invention, the friction portions on both sides in the belt width direction are clamped by a pair of sheave surfaces of a pulley having a variable groove width. An element for a V-belt that is used in a belt and has a convex portion and a concave portion that are alternately provided in a friction portion of an element that constitutes a friction portion of the V-belt extending in the element thickness direction. A top portion that is in contact with the sheave surface is formed to be biased toward the pulley axis.
According to a seventh aspect of the present invention, in the V-belt element according to the sixth aspect, each friction portion of the element is formed in a waveform in which convex portions and concave portions are alternately provided, and the top portion of the convex portion of the element is The curvature on the pulley axis side is formed smaller than the curvature on the pulley outer peripheral side.

上記第３の目的を達成するために、本発明のうち請求項８に記載の発明は、溝幅が可変に構成されて一対のシーブ面によってＶベルトのベルト幅方向両側の摩擦部が挟圧されるＶベルト用プーリであって、シーブ面は、Ｖベルトがプーリに対してプーリ軸心側へ移動する時の摩擦部との間の摩擦力が、Ｖベルトがプーリに対してプーリ外周側へ移動する時の摩擦部との間の摩擦力よりも大きく設定されることを特徴とする。
上記第３の目的を達成するために、本発明のうち請求項９に記載の発明は、溝幅が可変に構成されて一対のシーブ面によってＶベルトのベルト幅方向両側の摩擦部が挟圧されるＶベルト用プーリであって、シーブ面に、プーリ軸心を中心とする円環状の凸部と凹部とが交互に設けられて、該凸部は、摩擦部に接触させる頂部がプーリ外周側へ偏倚されて形成されることを特徴とする。
請求項１０に記載の発明は、請求項９に記載のＶベルト用プーリにおいて、シーブ面が凸部と凹部とが交互に設けられる波形に形成されて、凸部の頂部は、プーリ外周側の曲率がプーリ軸心側の曲率よりも小さく形成されることを特徴とする。 In order to achieve the third object, the invention according to claim 8 of the present invention is such that the groove width is variable and the friction portions on both sides in the belt width direction of the V-belt are clamped by a pair of sheave surfaces. A pulley for a V-belt, wherein the sheave surface has a frictional force with a friction part when the V-belt moves toward the pulley axis with respect to the pulley. It is characterized in that it is set to be larger than the frictional force with the friction part when moving to.
In order to achieve the third object, in the invention according to claim 9 of the present invention, the groove width is configured to be variable, and the friction portions on both sides in the belt width direction of the V-belt are clamped by the pair of sheave surfaces. A pulley for a V-belt, in which an annular convex portion and a concave portion centering on the pulley axis are alternately provided on the sheave surface, and the convex portion has a top portion that is in contact with the friction portion at the outer periphery of the pulley. It is characterized by being biased to the side.
According to a tenth aspect of the present invention, in the pulley for the V belt according to the ninth aspect, the sheave surface is formed in a corrugated shape in which convex portions and concave portions are provided alternately, and the top portion of the convex portion is on the pulley outer peripheral side. The curvature is smaller than the curvature on the pulley shaft center side.

したがって、請求項１に記載の発明では、Ｖベルトをプーリに対してプーリ軸心側へ移動させる力が抑えられてプーリがＶベルトを挟圧する力（挟圧力）が軽減される。
請求項２に記載の発明では、Ｖベルトがプーリに対してプーリ軸心側へ移動する時の、Ｖベルトの摩擦部とプーリのシーブ面との間の摩擦力が、Ｖベルトがプーリに対してプーリ外周側へ移動する時の、Ｖベルトの摩擦部とプーリのシーブ面との間の摩擦力よりも大きくなる。
請求項３に記載の発明では、Ｖベルトがプーリに対してプーリ軸心側へ移動する時の、Ｖベルトの凸部とプーリのシーブ面との間の摩擦力が、Ｖベルトがプーリに対してプーリ外周側へ移動する時の、Ｖベルトの凸部とプーリのシーブ面との間の摩擦力よりも大きくなる。
請求項４に記載の発明では、ベルト式無段変速機において、Ｖベルトをプーリに対してプーリ軸心側へ移動させる力が抑えられてプーリがＶベルトを挟圧する力（挟圧力）が軽減される。 Therefore, in the first aspect of the invention, the force that moves the V-belt toward the pulley axis with respect to the pulley is suppressed, and the force (clamping pressure) that the pulley clamps the V-belt is reduced.
According to the second aspect of the present invention, the frictional force between the friction portion of the V belt and the sheave surface of the pulley when the V belt moves toward the pulley axis with respect to the pulley is Thus, the frictional force between the friction portion of the V-belt and the sheave surface of the pulley when moving toward the pulley outer peripheral side becomes larger.
According to the third aspect of the present invention, the frictional force between the convex portion of the V-belt and the sheave surface of the pulley when the V-belt moves toward the pulley axis with respect to the pulley is Thus, the frictional force between the convex portion of the V-belt and the sheave surface of the pulley when moving toward the pulley outer peripheral side becomes larger.
In the invention according to claim 4, in the belt-type continuously variable transmission, the force that moves the V-belt toward the pulley axis with respect to the pulley is suppressed, and the force (clamping pressure) that the pulley clamps the V-belt is reduced. Is done.

請求項５に記載の発明では、エレメントをプーリに対してプーリ軸心側へ移動させる力が抑えられてプーリがエレメントを挟圧する力（挟圧力）が軽減される。
請求項６に記載の発明では、エレメントがプーリに対してプーリ軸心側へ移動する時の、エレメントの摩擦部とプーリのシーブ面との間の摩擦力が、エレメントがプーリに対してプーリ外周側へ移動する時の、エレメントの摩擦部とプーリのシーブ面との間の摩擦力よりも大きくなる。
請求項７に記載の発明では、エレメントがプーリに対してプーリ軸心側へ移動する時の、エレメントの凸部とプーリのシーブ面との間の摩擦力が、エレメントがプーリに対してプーリ外周側へ移動する時の、エレメントの凸部とプーリのシーブ面との間の摩擦力よりも大きくなる。 In the fifth aspect of the invention, the force that moves the element toward the pulley axis with respect to the pulley is suppressed, and the force (clamping pressure) that the pulley clamps the element is reduced.
According to the sixth aspect of the present invention, the frictional force between the friction part of the element and the sheave surface of the pulley when the element moves toward the pulley axis with respect to the pulley is It becomes larger than the frictional force between the friction part of the element and the sheave surface of the pulley when moving to the side.
According to the seventh aspect of the present invention, the frictional force between the convex portion of the element and the sheave surface of the pulley when the element moves toward the pulley axis with respect to the pulley is It becomes larger than the frictional force between the convex part of the element and the sheave surface of the pulley when moving to the side.

請求項８に記載の発明では、Ｖベルトをプーリに対してプーリ軸心側へ移動させる力が抑えられてプーリがＶベルトを挟圧する力（挟圧力）が軽減される。
請求項９に記載の発明では、Ｖベルトがプーリに対してプーリ軸心側へ移動する時の、Ｖベルトの摩擦部とプーリのシーブ面との間の摩擦力が、Ｖベルトがプーリに対してプーリ外周側へ移動する時の、Ｖベルトの摩擦部とプーリのシーブ面との間の摩擦力よりも大きくなる。
請求項１０に記載の発明では、Ｖベルトがプーリに対してプーリ軸心側へ移動する時の、Ｖベルトの摩擦部とシーブ面の凸部との間の摩擦力が、Ｖベルトがプーリに対してプーリ外周側へ移動する時の、Ｖベルトの摩擦部とシーブ面の凸部との間の摩擦力よりも大きくなる。 According to the eighth aspect of the present invention, the force that moves the V-belt toward the pulley axis with respect to the pulley is suppressed, and the force (clamping pressure) that the pulley clamps the V-belt is reduced.
According to the ninth aspect of the present invention, the frictional force between the friction part of the V-belt and the sheave surface of the pulley when the V-belt moves toward the pulley axis with respect to the pulley is Thus, the frictional force between the friction portion of the V-belt and the sheave surface of the pulley when moving toward the pulley outer peripheral side becomes larger.
In the invention according to claim 10, when the V belt moves toward the pulley axis with respect to the pulley, the frictional force between the friction portion of the V belt and the convex portion of the sheave surface is On the other hand, it becomes larger than the frictional force between the friction part of the V-belt and the convex part of the sheave surface when moving to the pulley outer peripheral side.

高トルクに対応可能なベルト式無段変速機が、軽量、且つコンパクトに構成されるＶベルト、Ｖベルト用エレメント及びＶベルト用プーリを提供することができる。   A belt-type continuously variable transmission that can handle high torque can provide a V-belt, a V-belt element, and a V-belt pulley that are light and compact.

本発明の一実施の形態を図１〜図６に基づいて説明する。図１に示されるのは、本Ｖベルト１が組付けられたベルト式無段変速機２（ＣＶＴ）である。該ベルト式無段変速機２は、本Ｖベルト１（金属製無端ベルト）が、入力軸３に取付けられた入力側プーリ４と出力軸５に取付けられた出力側プーリ６とに巻回されて構成される。上記入力側プーリ４は、一対のシーブ７，８を有して、油圧駆動機構によってシーブ７に対してシーブ８がプーリ軸心方向（図１における紙面視左右方向）へ位置決めされて溝幅が調節される。また、上記出力側プーリ６は、一対のシーブ９，１０を有して、油圧駆動機構によってシーブ９に対してシーブ１０がプーリ軸心方向へ位置決めされて溝幅が調節される。そして、上記ベルト式無段変速機２では、各プーリ４，６の各溝幅を制御して各プーリ４，６におけるＶベルト１の巻付け半径を必要に応じて調節することにより、入力軸３と出力軸５との回転数比、即ち変速比が連続的に無段階で変化させる構造になっている。   An embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows a belt type continuously variable transmission 2 (CVT) in which the present V belt 1 is assembled. In the belt-type continuously variable transmission 2, the V-belt 1 (metal endless belt) is wound around an input-side pulley 4 attached to an input shaft 3 and an output-side pulley 6 attached to an output shaft 5. Configured. The input-side pulley 4 has a pair of sheaves 7 and 8, and the sheave 8 is positioned with respect to the sheave 7 by the hydraulic drive mechanism in the pulley axial direction (left and right direction in the drawing in FIG. 1), and the groove width is increased. Adjusted. The output pulley 6 has a pair of sheaves 9 and 10, and the sheave 10 is positioned in the pulley axial direction with respect to the sheave 9 by a hydraulic drive mechanism to adjust the groove width. In the belt-type continuously variable transmission 2, the groove width of each pulley 4, 6 is controlled to adjust the winding radius of the V-belt 1 on each pulley 4, 6 as necessary, so that the input shaft 3 and the output shaft 5, i.e., the gear ratio is continuously varied continuously.

図２に示されるように、本Ｖベルト１は、複数個のエレメント１１が重ね合わされるように環状に配列されて、各エレメント１１のベルト幅方向両側のサドル部２５に金属製のフープ１２が巻回される。これにより、上記複数個のエレメント１１が結束されて、図３に示される金属製無端ベルト（Ｖベルト１）が構成される。そして、図４に示されるように、上記ベルト式無段変速機２では、Ｖベルト１のベルト幅方向（図４における紙面視左右方向）両側の摩擦部１３のベルト断面形状がテーパ状に形成されると共に、入力側プーリ４の一対のシーブ７，８のシーブ面１４，１５（以下、単にシーブ面１４，１５と称する。）及び出力側プーリ６の一対のシーブ９，１０のシーブ面１６，１７（以下、単にシーブ面１６，１７と称する。）の軸断面形状が、上記摩擦部１３のベルト断面形状に整合されたテーパ状に形成される。   As shown in FIG. 2, the V-belt 1 is arranged in an annular shape so that a plurality of elements 11 are overlapped, and metal hoops 12 are formed on saddle portions 25 on both sides of each element 11 in the belt width direction. It is wound. Thus, the plurality of elements 11 are bound to form a metal endless belt (V-belt 1) shown in FIG. As shown in FIG. 4, in the belt type continuously variable transmission 2, the belt cross-sectional shape of the friction portion 13 on both sides of the V-belt 1 in the belt width direction (left-right direction in FIG. 4) is formed in a tapered shape. In addition, the sheave surfaces 14 and 15 of the pair of sheaves 7 and 8 of the input side pulley 4 (hereinafter simply referred to as the sheave surfaces 14 and 15) and the sheave surface 16 of the pair of sheaves 9 and 10 of the output side pulley 6. , 17 (hereinafter simply referred to as sheave surfaces 16, 17) are formed in a tapered shape that matches the belt cross-sectional shape of the friction portion 13.

これにより、上記ベルト式無段変速機２では、本Ｖベルト１のベルト幅方向両側の摩擦部１３がシーブ面１４，１５及びシーブ面１６，１７によって挟み込まれて挟圧されると、各プーリ４，６に接触する各エレメント１１には、上記摩擦部１３が挟圧される時の挟圧力によって各プーリ４，６の半径方向（図４における紙面視上方向）への力が作用される。そして、上記ベルト式無段変速機２では、各フープ１２の張力によって各エレメント１１が各プーリ４，６の半径方向へ移動するのが規制されることで、本Ｖベルト１の摩擦部１３と、シーブ面１４，１５及びシーブ面１６，１７との間に摩擦力が生じて、本Ｖベルト１と入力側プーリ４及び出力側プーリ６との間でトルクが伝達される構造になっている。図４に示されるように、本エレメント１１は、基部１８の幅方向（図４における紙面視左右方向）両側に上記摩擦部１３が配設されて、該基部１８の上側（図４における紙面視上側）には首部１９を介して幅方向へ延びる頭部２０が設けられる。   As a result, in the belt type continuously variable transmission 2, when the friction portions 13 on both sides in the belt width direction of the V-belt 1 are sandwiched between the sheave surfaces 14 and 15 and the sheave surfaces 16 and 17, A force in the radial direction of each pulley 4, 6 is applied to each element 11 in contact with 4, 6 by the clamping pressure when the friction portion 13 is clamped. . In the belt-type continuously variable transmission 2, the movement of each element 11 in the radial direction of each pulley 4, 6 is restricted by the tension of each hoop 12, so that A frictional force is generated between the sheave surfaces 14 and 15 and the sheave surfaces 16 and 17 so that torque is transmitted between the V-belt 1 and the input-side pulley 4 and the output-side pulley 6. . As shown in FIG. 4, the present element 11 has the friction portion 13 disposed on both sides in the width direction of the base portion 18 (left and right direction as viewed in FIG. 4). On the upper side, a head 20 extending in the width direction via the neck 19 is provided.

なお、本エレメント１１は、頭部２０の略中央に、一側面で凸状に形成されて他側面で凹状に形成された連結部２１が設けられる。図５に示されるように、本エレメント１１は、幅方向両側の摩擦部１３が、板厚方向（図５における紙面視方向）へ延びる凸部２２と凹部２３とが各摩擦部１３に沿って交互に設けられることにより波形に形成される。そして、本エレメント１１は、各摩擦部１３の各凸部２２の各頂部２４がプーリ軸心側（図５における紙面視下側）へ偏倚されて、各頂部２４におけるプーリ軸心側の曲率Ｒ１がプーリ外周側（図５における紙面視上側）の曲率Ｒ２よりも小さく（Ｒ２＞Ｒ１）形成される。これにより、本エレメント１１は、入力側プーリ４に対してプーリ軸心側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ1が、入力側プーリ４に対してプーリ外周側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ2よりも大きく（μ1＞μ2）設定される。   The element 11 is provided with a connecting portion 21 that is formed in a convex shape on one side surface and formed in a concave shape on the other side surface at the approximate center of the head 20. As shown in FIG. 5, the present element 11 has a frictional portion 13 on both sides in the width direction, and a convex portion 22 and a concave portion 23 extending in the plate thickness direction (the direction of the paper in FIG. 5) along each frictional portion 13. By being provided alternately, a waveform is formed. In this element 11, each top portion 24 of each convex portion 22 of each friction portion 13 is biased toward the pulley axis side (the lower side in the drawing in FIG. 5), and the curvature R1 of each top portion 24 on the pulley axis side. Is smaller than the curvature R2 (R2> R1) on the pulley outer peripheral side (upper side in the drawing in FIG. 5). Thereby, when this element 11 moves to the pulley axial center side with respect to the input side pulley 4, the frictional force μ 1 between the friction portion 13 and the sheave surfaces 14, 15 is applied to the input side pulley 4. It is set larger than the frictional force μ2 between the friction part 13 and the sheave surfaces 14 and 15 when moving to the pulley outer peripheral side (μ1> μ2).

次に、本実施の形態の作用を説明する。なお、上述したように、エレメント１１が入力側プーリ４に対してプーリ軸心側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ1が、エレメント１１が入力側プーリ４に対してプーリ外周側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ2よりも大きく（μ1＞μ2）なる。これと同様に、エレメント１１が出力側プーリ６に対してプーリ軸心側へ移動する時の、摩擦部１３とシーブ面１６，１７との間の摩擦力は、エレメント１１が出力側プーリ６に対してプーリ外周側へ移動する時の、摩擦部１３とシーブ面１６，１７との間の摩擦力よりも大きくなる。このため、本エレメント１１（本Ｖベルト１）では、入力側プーリ４に対する場合と出力側プーリに対する場合とで同一の作用を有するので、ここでは、本エレメント１１の入力側プーリ４に対する作用のみを説明して、本エレメント１１の出力側プーリ６に対する作用の説明を省略すると共に、以下、入力側プーリ４を単にプーリ４と称する。   Next, the operation of the present embodiment will be described. As described above, the frictional force μ1 between the friction portion 13 and the sheave surfaces 14 and 15 when the element 11 moves toward the pulley axis with respect to the input side pulley 4 is such that the element 11 is on the input side. It becomes larger than the frictional force μ2 between the friction part 13 and the sheave surfaces 14 and 15 when moving toward the pulley outer peripheral side with respect to the pulley 4 (μ1> μ2). Similarly, the frictional force between the friction portion 13 and the sheave surfaces 16 and 17 when the element 11 moves toward the pulley axis with respect to the output side pulley 6 causes the element 11 to act on the output side pulley 6. On the other hand, it becomes larger than the frictional force between the friction part 13 and the sheave surfaces 16 and 17 when moving to the pulley outer peripheral side. For this reason, this element 11 (this V-belt 1) has the same effect on the input-side pulley 4 and on the output-side pulley. Therefore, here, only the action of the element 11 on the input-side pulley 4 is performed. In the following, description of the operation of the element 11 on the output side pulley 6 is omitted, and the input side pulley 4 is hereinafter simply referred to as the pulley 4.

図４に示されるように、上記ベルト式無段変速機２では、本Ｖベルト１のプーリ４に接触する各エレメント１１（以下、単にエレメント１１と称する。）の幅方向両側の摩擦部１３が、シーブ面１４，１５によって挟圧される。そして、図５に示されるように、エレメント１１は、波形に形成された摩擦部１３の各凸部２２の各頂部２４が、シーブ面１４，１５に接触される。ここで、エレメント１１は、摩擦部１３の各凸部２２の各頂部２４がプーリ軸心側（図５における紙面視下側）へ偏倚されて、各頂部２４におけるプーリ軸心側の曲率Ｒ１がプーリ外周側（図５における紙面視上側）の曲率Ｒ２よりも小さい（Ｒ２＞Ｒ１）ため、プーリ４に対してプーリ軸心側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ1が、プーリ４に対してプーリ外周側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ2よりも大きい（μ1＞μ2）。   As shown in FIG. 4, in the belt type continuously variable transmission 2, the friction portions 13 on both sides in the width direction of each element 11 (hereinafter simply referred to as the element 11) that contacts the pulley 4 of the V belt 1 are provided. The sheave surfaces 14 and 15 are clamped. As shown in FIG. 5, in the element 11, the top portions 24 of the convex portions 22 of the friction portion 13 formed in a corrugated shape are brought into contact with the sheave surfaces 14 and 15. Here, in the element 11, each top portion 24 of each convex portion 22 of the friction portion 13 is biased toward the pulley shaft center side (the lower side in the drawing in FIG. 5), and the curvature R1 of each top portion 24 on the pulley shaft center side is Since the curvature R2 is smaller than the curvature R2 on the pulley outer periphery side (the upper side in the drawing in FIG. 5) (R2> R1), The frictional force μ1 between them is larger than the frictional force μ2 between the friction part 13 and the sheave surfaces 14 and 15 when the pulley 4 moves toward the pulley outer peripheral side (μ1> μ2).

ここで、図６に示されるのは、従来のエレメント１１´の各摩擦部１３´に形成された波形であって、各凸部２２´の各頂部２４´は、均一な曲率Ｒ３（Ｒ２＞Ｒ３＞Ｒ１）で形成される。そして、従来のエレメント１１´は、プーリ４に対してプーリ軸心側（図６における紙面視下側）へ移動する時の、摩擦部１３´とシーブ面１４，１５との間の摩擦力と、プーリ４に対してプーリ外周側（図６における紙面視下側）へ移動する時の、摩擦部１３´とシーブ面１４，１５との間の摩擦力とが、等しい摩擦力μ3（μ1＞μ3＞μ2）になる。したがって、本エレメント１１は、プーリ４に対してプーリ軸心側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ1が、従来のエレメント１１´における当該摩擦力μ3と比較して大きくなる（μ1＞μ3）。このため、本エレメント１１では、フープ１２の張力によってエレメント１１がプーリ軸心に向けて押圧された時の当該エレメント１１がプーリ軸心側へ移動しようとする力（以下、エレメント１１の推力と称する。）が、従来のエレメント１１´と比較して小さくなり、従来のエレメント１１´と比較してプーリ軸心側へ入り込み難い。   Here, FIG. 6 shows a waveform formed in each friction portion 13 ′ of the conventional element 11 ′, and each top portion 24 ′ of each convex portion 22 ′ has a uniform curvature R 3 (R 2>). R3> R1). The conventional element 11 ′ has a frictional force between the friction portion 13 ′ and the sheave surfaces 14 and 15 when moving to the pulley shaft center side (the lower side in FIG. 6) with respect to the pulley 4. The frictional force between the friction part 13 'and the sheave surfaces 14, 15 when moving toward the pulley outer periphery side (the lower side in the drawing in FIG. 6) with respect to the pulley 4 is equal to the frictional force μ3 (μ1>). μ3> μ2). Therefore, the frictional force μ1 between the friction portion 13 and the sheave surfaces 14 and 15 when the element 11 moves toward the pulley axis with respect to the pulley 4 is the frictional force μ3 in the conventional element 11 ′. (Μ1> μ3). For this reason, in this element 11, when the element 11 is pressed toward the pulley shaft center by the tension of the hoop 12, the element 11 tries to move toward the pulley shaft center (hereinafter referred to as the thrust of the element 11). )) Is smaller than the conventional element 11 ', and is less likely to enter the pulley shaft side than the conventional element 11'.

また、本エレメント１１は、プーリ４に対してプーリ外周側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ2が、従来のエレメント１１´における当該摩擦力μ3と比較して小さくなる（μ3＞μ2）。このため、本エレメント１１では、一対のシーブ７，８によって挟圧された時の当該エレメント１１がプーリ外周側へ移動しようとする力が、従来のエレメント１１´と比較して大きくなり、従来のエレメント１１´と比較してプーリ外周側への移動が容易になる。   Further, when the element 11 moves to the pulley outer peripheral side with respect to the pulley 4, the friction force μ2 between the friction portion 13 and the sheave surfaces 14 and 15 is the friction force μ3 in the conventional element 11 ′. Smaller than that (μ3> μ2). For this reason, in this element 11, when the element 11 is clamped by the pair of sheaves 7 and 8, the force that the element 11 tends to move to the pulley outer peripheral side is larger than that of the conventional element 11 ′. Compared with the element 11 ', the movement toward the pulley outer peripheral side is facilitated.

この実施の形態では以下の効果を奏する。
本エレメント１１は、幅方向両側の摩擦部１３が、板厚方向へ延びる凸部２２と凹部２３とが各摩擦部１３に沿って交互に設けられて波形に形成されて、各摩擦部１３の各凸部２２の各頂部２４がプーリ軸心側へ偏倚される。
そして、本エレメント１１では、各頂部２４におけるプーリ軸心側の曲率Ｒ１がプーリ外周側の曲率Ｒ２よりも小さく（Ｒ２＞Ｒ１）形成されることにより、プーリ４に対してプーリ軸心側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ1が、プーリ４に対してプーリ外周側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ2よりも大きくなる（μ1＞μ2）。また、従来のエレメント１１´では、各摩擦部１３´に形成された波形の各凸部２２´の各頂部２４´が均一な曲率Ｒ３（Ｒ２＞Ｒ３＞Ｒ１）で形成されることから、本エレメント１１では、プーリ４に対してプーリ軸心側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ1が、従来のエレメント１１´における当該摩擦力μ3と比較して大きくなる（μ1＞μ3）。 This embodiment has the following effects.
In the present element 11, the friction portions 13 on both sides in the width direction are formed in a waveform by alternately forming convex portions 22 and concave portions 23 extending in the plate thickness direction along the respective friction portions 13. Each top 24 of each convex portion 22 is biased toward the pulley axis.
In this element 11, the curvature R1 on the pulley axis side at each apex 24 is smaller than the curvature R2 on the pulley outer periphery side (R2> R1), so that the pulley 4 moves toward the pulley axis side. When the frictional force μ1 between the friction part 13 and the sheave surfaces 14 and 15 moves to the pulley outer peripheral side with respect to the pulley 4, the friction between the friction part 13 and the sheave surfaces 14 and 15 The force becomes larger than μ2 (μ1> μ2). Further, in the conventional element 11 ′, each top 24 ′ of each corrugated convex portion 22 ′ formed in each friction portion 13 ′ is formed with a uniform curvature R3 (R2>R3> R1). In the element 11, the frictional force μ1 between the friction part 13 and the sheave surfaces 14 and 15 when moving toward the pulley axis with respect to the pulley 4 is compared with the frictional force μ3 in the conventional element 11 ′. (Μ1> μ3).

したがって、本エレメント１１は、フープ１２の張力によってエレメント１１がプーリ軸心に向けて押圧された時の当該エレメント１１の推力が、従来のエレメント１１´と比較して小さくなり、従来のエレメント１１´と比較してプーリ軸心側へ入り込み難くなる。このため、本エレメント１１によって構成されたＶベルト１を用いるベルト式無段変速機２では、フープ１２の張力が同一である場合に、従来のエレメント１１´によって構成されたＶベルト１´を用いるベルト式無段変速機２´と比較して、エレメント１１によって一対のシーブ７，８が押拡げられる力が小さくなる。これにより、本Ｖベルト１を用いてベルト式無段変速機２を構成した場合、従来のＶベルト１´を用いてベルト式無段変速機２´を構成した場合と比較して、プーリ４の一対のシーブ７，８による挟圧力が小さいため、高トルクに対応させる場合であっても、従来のＶベルト１´を用いるベルト式無段変速機２´で行われていたように、プーリ４の剛性を高める必要がない。このため、高トルクに対応するベルト式無段変速機２を軽量、且つコンパクトに構成することができる。   Therefore, in the present element 11, the thrust of the element 11 when the element 11 is pressed toward the pulley axis by the tension of the hoop 12 is smaller than that of the conventional element 11 ′, and thus the conventional element 11 ′. Compared to the pulley shaft, it becomes difficult to enter the pulley shaft side. For this reason, the belt-type continuously variable transmission 2 using the V-belt 1 constituted by the element 11 uses the V-belt 1 ′ constituted by the conventional element 11 ′ when the tension of the hoop 12 is the same. Compared with the belt-type continuously variable transmission 2 ′, the force by which the pair of sheaves 7 and 8 are expanded by the element 11 is reduced. Thus, when the belt type continuously variable transmission 2 is configured using the V belt 1, the pulley 4 is compared with the case where the belt type continuously variable transmission 2 ′ is configured using the conventional V belt 1 ′. Since the pinching force by the pair of sheaves 7 and 8 is small, even when the high torque is dealt with, the pulley as in the conventional belt-type continuously variable transmission 2 ′ using the V-belt 1 ′ is used. There is no need to increase the rigidity of 4. For this reason, the belt-type continuously variable transmission 2 corresponding to high torque can be configured to be lightweight and compact.

なお、実施の形態は上記に限定されるものではなく、例えば次のように構成してもよい。
本エレメント１１は、幅方向両側の摩擦部１３が、板厚方向へ延びる凸部２２と凹部２３とが交互に設けられることにより波形に形成されるが、摩擦部１３の凸部２２と凹部２３とはエレメント１１の板厚方向に対して必ずしも平行ではなく、摩擦部１３の凸部２２と凹部２３とを必要に応じて当該板厚方向に対して傾斜させてもよい。
この場合、プーリ４に対するＶベルト１（エレメント１１）の、プーリ接線方向への摩擦力が調節が調節されて当該プーリ接線方向への滑りが調節される。 In addition, embodiment is not limited above, For example, you may comprise as follows.
In the present element 11, the frictional portions 13 on both sides in the width direction are formed in a waveform by alternately providing convex portions 22 and concave portions 23 extending in the plate thickness direction, but the convex portions 22 and the concave portions 23 of the friction portion 13 are formed. Is not necessarily parallel to the plate thickness direction of the element 11, and the convex portion 22 and the concave portion 23 of the friction portion 13 may be inclined with respect to the plate thickness direction as necessary.
In this case, the frictional force of the V-belt 1 (element 11) with respect to the pulley 4 in the pulley tangential direction is adjusted to adjust the slip in the pulley tangential direction.

また、本エレメント１１は、摩擦部１３が波形に形成されるが、エレメント１１がプーリ４に対してプーリ軸心側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ1が、エレメント１１がプーリ４に対してプーリ外周側へ移動する時の、摩擦部１３とシーブ面１４，１５との間の摩擦力μ2よりも大きく（μ1＞μ2）、且つ、従来のエレメント１１´における当該摩擦力μ3と比較して大きく（μ1＞μ3）設定されていれば、例えば、図７の（Ａ）〜（Ｃ）に示されるような鋸刃形であってもよい。   Further, in this element 11, the friction portion 13 is formed in a waveform, but the friction between the friction portion 13 and the sheave surfaces 14 and 15 when the element 11 moves toward the pulley axis with respect to the pulley 4. The force μ1 is larger than the friction force μ2 between the friction portion 13 and the sheave surfaces 14 and 15 when the element 11 moves toward the pulley outer side with respect to the pulley 4 (μ1> μ2), and As long as it is set to be larger (μ1> μ3) than the frictional force μ3 in the element 11 ′, for example, a saw blade shape as shown in FIGS.

また、本実施の形態では、エレメント１１の幅方向両側の摩擦部１３に、板厚方向へ延びる凸部２２と凹部２３とを交互に設けて波形を形成したが、エレメント１１の幅方向両側の摩擦部１３を平坦に形成しておいて、プーリ４の一対のシーブ７，８の各シーブ面１４，１５に、プーリ軸心を中心とする円環状の凸部２２と凹部２３とを交互に設けて波形を形成してもよい。この場合、各シーブ面１４，１５の凸部２２は、摩擦部１３に接触させる頂部２４がプーリ外周側へ偏倚されるように形成される。これにより、上述したようなエレメント１１（Ｖベルト１）に波形を形成した場合と同様の作用効果が得られる。   Further, in the present embodiment, the corrugations are formed by alternately providing the convex portions 22 and the concave portions 23 extending in the plate thickness direction on the friction portions 13 on both sides in the width direction of the element 11. The friction portion 13 is formed flat, and annular convex portions 22 and concave portions 23 centering on the pulley axis are alternately formed on the sheave surfaces 14 and 15 of the pair of sheaves 7 and 8 of the pulley 4. It may be provided to form a waveform. In this case, the convex portions 22 of the respective sheave surfaces 14 and 15 are formed so that the top portion 24 brought into contact with the friction portion 13 is biased toward the pulley outer peripheral side. Thereby, the same effect as the case where a waveform is formed in the element 11 (V belt 1) as described above can be obtained.

ベルト式無段変速機の説明図である。It is explanatory drawing of a belt-type continuously variable transmission. 本Ｖベルトの説明図である。It is explanatory drawing of this V belt. 本Ｖベルトの全体図である。It is a general view of this V belt. 本実施の形態の説明図であって、エレメントが一対のシーブによって挟圧される状態を示す図である。It is explanatory drawing of this Embodiment, Comprising: It is a figure which shows the state in which an element is pinched by a pair of sheaves. 本実施の形態の説明図であって、エレメントの摩擦部に形成された波形を示す図である。It is explanatory drawing of this Embodiment, Comprising: It is a figure which shows the waveform formed in the friction part of the element. 従来のエレメントの摩擦部に形成された波形を示す図である。It is a figure which shows the waveform formed in the friction part of the conventional element. 他の実施の形態の説明図であって、（Ａ）〜（Ｃ）はエレメントの摩擦部に形成される各鋸刃形を示す図である。It is explanatory drawing of other embodiment, Comprising: (A)-(C) is a figure which shows each saw blade shape formed in the friction part of an element.

符号の説明Explanation of symbols

１ Ｖベルト、２ ベルト式無段変速機、４ 入力側プーリ、６ 出力側プーリ、１１ エレメント、１３ 摩擦部、１４〜１７ シーブ面、２２ 凸部２２ 凹部、２４ 頂部   1 V belt, 2 belt type continuously variable transmission, 4 input side pulley, 6 output side pulley, 11 element, 13 friction part, 14-17 sheave surface, 22 convex part 22 concave part, 24 top part

Claims (10)

溝幅が可変であるプーリの一対のシーブ面によってベルト幅方向両側の摩擦部が挟圧されるＶベルトであって、該Ｖベルトの前記摩擦部は、前記Ｖベルトが前記プーリに対してプーリ軸心側へ移動する時の前記シーブ面との間の摩擦力が、前記Ｖベルトが前記プーリに対してプーリ外周側へ移動する時の前記シーブ面との間の摩擦力よりも大きく設定されることを特徴とするＶベルト。   A V-belt in which friction portions on both sides in the belt width direction are clamped by a pair of sheave surfaces of a pulley having a variable groove width, and the friction portion of the V-belt is configured so that the V-belt is connected to the pulley. The frictional force between the sheave surface and the sheave surface when moving toward the shaft center side is set to be larger than the frictional force between the sheave surface when the V-belt moves toward the pulley outer peripheral side with respect to the pulley. A V-belt characterized by that. 溝幅が可変であるプーリの一対のシーブ面によって挟圧されるＶベルトのベルト幅方向両側の摩擦部に、ベルト長さ方向へ延びる凸部と凹部とが交互に設けられるＶベルトであって、該Ｖベルトの前記凸部は、前記シーブ面に接触させる頂部がプーリ軸心側へ偏倚されて形成されることを特徴とするＶベルト。   A V-belt in which convex portions and concave portions extending in the belt length direction are alternately provided at friction portions on both sides in the belt width direction of the V-belt sandwiched between a pair of sheave surfaces of a pulley having a variable groove width. The convex portion of the V-belt is formed such that a top portion that is in contact with the sheave surface is biased toward the pulley axis. 前記Ｖベルトの各摩擦部が前記凸部と前記凹部とが交互に設けられる波形に形成されて、前記凸部の前記頂部は、プーリ軸心側の曲率がプーリ外周側の曲率よりも小さく形成されることを特徴とする請求項２に記載のＶベルト。   Each friction part of the V-belt is formed in a waveform in which the convex part and the concave part are alternately provided, and the top part of the convex part is formed so that the curvature on the pulley axis side is smaller than the curvature on the pulley outer peripheral side. The V-belt according to claim 2, wherein: ベルト式無段変速機に用いられることを特徴とする請求項１〜３のいずれかに記載のＶベルト。   The V-belt according to any one of claims 1 to 3, wherein the V-belt is used in a belt-type continuously variable transmission. 溝幅が可変であるプーリの一対のシーブ面によってベルト幅方向両側の摩擦部が挟圧されるＶベルトに用いられるエレメントであって、前記Ｖベルトの摩擦部を構成する前記エレメントの摩擦部は、前記エレメントが前記プーリに対してプーリ軸心側へ移動する時の前記シーブ面との間の摩擦力が、前記エレメントが前記プーリに対してプーリ外周側へ移動する時の前記シーブ面との間の摩擦力よりも大きく設定されることを特徴とするＶベルト用エレメント。   An element used in a V-belt in which friction portions on both sides in the belt width direction are clamped by a pair of sheave surfaces of a pulley having a variable groove width, and the friction portion of the element constituting the friction portion of the V-belt is The frictional force between the element and the sheave surface when the element moves toward the pulley axis side with respect to the pulley is different from the sheave surface when the element moves toward the pulley outer periphery side with respect to the pulley. V-belt element characterized by being set to be larger than the frictional force between them. 溝幅が可変であるプーリの一対のシーブ面によってベルト幅方向両側の摩擦部が挟圧されるＶベルトに用いられて、前記Ｖベルトの摩擦部を構成するエレメントの摩擦部にエレメント厚さ方向へ延びる凸部と凹部とが交互に設けられるＶベルト用エレメントであって、該エレメントの前記凸部は、前記シーブ面に接触させる頂部がプーリ軸心側へ偏倚されて形成されることを特徴とするＶベルト用エレメント。   Used in a V-belt in which friction portions on both sides in the belt width direction are clamped by a pair of sheave surfaces of a pulley having a variable groove width, and the friction portion of the element constituting the friction portion of the V-belt has an element thickness direction. A V-belt element in which convex portions and concave portions extending alternately are provided, and the convex portion of the element is formed such that a top portion contacting the sheave surface is biased toward the pulley shaft side. V-belt element. 前記エレメントの各摩擦部が前記凸部と前記凹部とが交互に設けられる波形に形成されて、前記エレメントの前記凸部の前記頂部は、プーリ軸心側の曲率がプーリ外周側の曲率よりも小さく形成されることを特徴とする請求項６に記載のＶベルト用エレメント。   Each friction part of the element is formed in a waveform in which the convex part and the concave part are alternately provided, and the top part of the convex part of the element has a curvature on the pulley axis side that is larger than a curvature on the pulley outer peripheral side. The element for a V-belt according to claim 6, wherein the element is formed small. 溝幅が可変に構成されて一対のシーブ面によってＶベルトのベルト幅方向両側の摩擦部が挟圧されるＶベルト用プーリであって、前記シーブ面は、前記Ｖベルトが前記プーリに対してプーリ軸心側へ移動する時の前記摩擦部との間の摩擦力が、前記Ｖベルトが前記プーリに対してプーリ外周側へ移動する時の前記摩擦部との間の摩擦力よりも大きく設定されることを特徴とするＶベルト用プーリ。   A pulley for a V belt having a groove width variably configured so that friction portions on both sides in the belt width direction of the V belt are clamped by a pair of sheave surfaces. The frictional force with the frictional part when moving toward the pulley shaft side is set to be larger than the frictional force with the frictional part when the V-belt moves toward the pulley outer peripheral side with respect to the pulley. A pulley for a V-belt. 溝幅が可変に構成されて一対のシーブ面によってＶベルトのベルト幅方向両側の摩擦部が挟圧されるＶベルト用プーリであって、前記シーブ面に、プーリ軸心を中心とする円環状の凸部と凹部とが交互に設けられて、該凸部は、前記摩擦部に接触させる頂部がプーリ外周側へ偏倚されて形成されることを特徴とするＶベルト用プーリ。   A V-belt pulley having a groove width variably configured so that friction portions on both sides in the belt width direction of the V-belt are clamped by a pair of sheave surfaces, and the sheave surface having an annular shape centering on the pulley axis The V-belt pulley is characterized in that convex portions and concave portions are alternately provided, and the convex portions are formed such that a top portion that is brought into contact with the friction portion is biased toward the outer peripheral side of the pulley. 前記シーブ面が前記凸部と前記凹部とが交互に設けられる波形に形成されて、前記凸部の前記頂部は、プーリ外周側の曲率がプーリ軸心側の曲率よりも小さく形成されることを特徴とする請求項９に記載のＶベルト用プーリ。
The sheave surface is formed in a waveform in which the convex portions and the concave portions are alternately provided, and the top portion of the convex portion is formed such that the curvature on the pulley outer peripheral side is smaller than the curvature on the pulley axis side. The pulley for V belts of Claim 9 characterized by the above-mentioned.
JP2004340635A 2004-11-25 2004-11-25 V belt, V belt element and V belt pulley Expired - Fee Related JP4525910B2 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2119939A3 (en) * 2008-05-12 2010-08-25 JATCO Ltd Metal V-belt of continuously variable transmission
JP2017084685A (en) * 2015-10-30 2017-05-18 日立アプライアンス株式会社 Induction heating cooker

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05157146A (en) * 1991-12-03 1993-06-22 Toyota Motor Corp Belt type continuously variable transmission for vehicle
JP2003083407A (en) * 2001-09-11 2003-03-19 Toyota Motor Corp Belt type continuously variable transmission
JP2004324873A (en) * 2003-03-06 2004-11-18 Nissan Motor Co Ltd Metal belt element

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05157146A (en) * 1991-12-03 1993-06-22 Toyota Motor Corp Belt type continuously variable transmission for vehicle
JP2003083407A (en) * 2001-09-11 2003-03-19 Toyota Motor Corp Belt type continuously variable transmission
JP2004324873A (en) * 2003-03-06 2004-11-18 Nissan Motor Co Ltd Metal belt element

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2119939A3 (en) * 2008-05-12 2010-08-25 JATCO Ltd Metal V-belt of continuously variable transmission
US8814735B2 (en) 2008-05-12 2014-08-26 Jatco Ltd Metal V-belt of continuously variable transmission
JP2017084685A (en) * 2015-10-30 2017-05-18 日立アプライアンス株式会社 Induction heating cooker

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