JP5228790B2

JP5228790B2 - Chain belt and belt type continuously variable transmission

Info

Publication number: JP5228790B2
Application number: JP2008271758A
Authority: JP
Inventors: 吉孝三浦; 敦史月崎; 雄紀松下
Original assignee: Nissan Motor Co Ltd
Current assignee: Nissan Motor Co Ltd
Priority date: 2008-01-21
Filing date: 2008-10-22
Publication date: 2013-07-03
Anticipated expiration: 2028-10-22
Also published as: JP2009197997A; WO2009093117A1

Description

本発明は、チェーンベルトおよびベルト式無段変速機に関し、特に、両端部にピン係合部を備えた複数枚のリンクプレートと、各リンクプレートを関節運動可能に連結するロッカピンと、からなり、前記ロッカピンにて無端状に連結したチェーンベルトおよびベルト式無段変速機に関するものである。 The present invention relates to a chain belt and a belt-type continuously variable transmission, and in particular, includes a plurality of link plates provided with pin engaging portions at both ends, and rocker pins that connect the link plates so that they can be articulated. The present invention relates to a chain belt and a belt type continuously variable transmission connected endlessly by the rocker pin.

平行な一対の回転軸に夫々Ｖ字状断面の周溝（Ｖ溝）を有するＶ型プーリが配置され、両プーリ間に金属ベルトを掛け渡し、両プーリのＶ溝幅を駆動側と従動側とで互いに関連させつつ変化させることにより、回転動力を無段階に変速して伝達するベルト式無段変速機が一般に実用化されている。従来からこの種のベルト式無段変速機に使用される金属ベルトの一つとして、多数のリンクプレート同士を連結するロッカピンの両端を前記プーリのＶ溝面に接触させて動力を伝達する無段変速機用のチェーンベルトが知られている（特許文献１，２参照）。 A V-shaped pulley having a V-shaped cross-sectional groove (V-groove) is arranged on a pair of parallel rotating shafts, a metal belt is spanned between both pulleys, and the V-groove width of both pulleys is set to the driving side and the driven side In general, belt-type continuously variable transmissions that transmit and transmit rotational power in a stepless manner are generally put into practical use. Conventionally, as one of the metal belts used in this type of belt-type continuously variable transmission, a continuously variable transmission that transmits power by bringing both ends of a rocker pin connecting a plurality of link plates to the V groove surface of the pulley. A chain belt for a transmission is known (see Patent Documents 1 and 2).

特許文献１では、２種類の長さ（ピッチ間隔）のリンクプレートをチェーンベルト内にランダムに配列することで、動力伝達中の周波数ピークを分離させ、発生騒音を低減するようにしている。 In Patent Document 1, link plates having two types of lengths (pitch intervals) are randomly arranged in a chain belt to separate frequency peaks during power transmission and reduce generated noise.

特許文献２では、プーリのＶ溝面に接触する中間ブロックをリンクプレートに取付けて、ロッカピンと中間ブロックとによって３点接触とすることで、接触ピッチを細かくして、Ｖ溝面との１接触当たりの入力を小さくして、発生騒音を低減するようにしている。
特表２００５−５３１７３４号公報特公平７−１０５５号公報 In Patent Document 2, an intermediate block that contacts a V-groove surface of a pulley is attached to a link plate, and a three-point contact is made by a rocker pin and an intermediate block. The hit input is reduced to reduce the generated noise.
JP-T-2005-53734 Japanese Patent Publication No. 7-1055

しかしながら、上記特許文献１では、ランダム化によって所定の周波数ではチェーンによる加振エネルギを減少できるが、チェーンにおけるロッカピンの間隔、即ち、ピッチ間隔が大きいという構成になっているため、加振エネルギそのものが大きく、チェーン周囲の部品の共振周波数領域では騒音が大きくなるといった不具合があった。また、加振エネルギを減少させるために前記ピッチ間隔を狭くすると、部品点数が増加して、コストが高くなる不具合もある。 However, in Patent Document 1, the excitation energy by the chain can be reduced at a predetermined frequency by randomization. However, since the rocker pin interval in the chain, that is, the pitch interval is large, the excitation energy itself is not reduced. There is a problem that the noise becomes large in the resonance frequency region of the parts around the chain. Further, if the pitch interval is narrowed in order to reduce the excitation energy, there is a problem that the number of parts increases and the cost increases.

前記特許文献２では、中間ブロックのＶ溝面に対するピボット形状がロッカピンによるピボット形状に対して大きく相違するため、Ｖ溝面への接触反力による変形量がロッカピンとは相違して、ロッカピンと中間ブロックとの３点が同時に接触しない領域が存在し、プーリへの特定の巻付き半径においての騒音低減に限定されるという不具合があった。 In Patent Document 2, the pivot shape of the intermediate block with respect to the V-groove surface is greatly different from the pivot shape of the rocker pin. Therefore, the deformation amount due to the contact reaction force on the V-groove surface is different from that of the rocker pin. There is a region where the three points with the block do not contact at the same time, and there is a problem that it is limited to noise reduction at a specific winding radius around the pulley.

そこで本発明は、上記問題点に鑑みてなされたもので、プーリとの接触ピッチ間隔の短縮化に好適なチェーンベルトおよびベルト式無段変速機を提供することを目的とする。 Therefore, the present invention has been made in view of the above problems, and an object thereof is to provide a chain belt and a belt-type continuously variable transmission suitable for shortening the contact pitch interval with the pulley.

本発明は、平板状のプレートを板厚方向に複数積層された第１のリンクプレートと、前記第１のリンクプレートの長手方向両側において、平板状のプレートを板厚方向に複数積層され且つ第１のリンクプレートと端部同士を重ね合せて配置された第２，第３のリンクプレートと、前記第１のリンクプレートと第２、第３のリンクプレートとの互いに重ね合わされた端部同士を板厚方向に貫通して互いを連結する第１，第２ピンと、前記第２リンクプレートおよび第３リンクプレートの間において、前記第１リンクプレートを板厚方向に貫通させて前記第１ピンおよび前記第２ピンと平行に配置された第３ピンと、を備えてその長手方向に複数連結した構成を備える。 The present invention includes a first link plate in which a plurality of flat plates are stacked in the thickness direction, and a plurality of flat plates in the thickness direction on both sides in the longitudinal direction of the first link plate. The first and second link plates arranged to overlap each other and the first link plate and the end portions of the first link plate and the second and third link plates that are overlapped with each other. Between the first and second pins penetrating in the plate thickness direction and connecting each other, and between the second link plate and the third link plate, the first link plate penetrates in the plate thickness direction and the first pin and And a third pin arranged in parallel with the second pin, and a plurality of the pins are connected in the longitudinal direction.

したがって、本発明では、第１リンクプレートの長手方向左右に配置される第２リンクプレートおよび第３リンクプレートの間において、第１リンクプレートを板厚方向に貫通させて各リンクプレートを連結する第１ピンおよび第２ピンと平行に配置された第３ピンを備えて、複数のリンクプレートをその長手方向に連結して無端状にした構成を備えることにより、リンクプレートの長さ寸法を短くすることなく動力伝達に寄与する各ピンの接触ピッチ間隔を半減させることができ、コスト増につながるリンク部品点数を増加させることなく、低騒音化を図ることができる。 Therefore, according to the present invention, the first link plate is penetrated in the plate thickness direction between the second link plate and the third link plate arranged on the left and right in the longitudinal direction of the first link plate. The length of the link plate is shortened by providing a third pin arranged in parallel with the first pin and the second pin, and having a structure in which a plurality of link plates are connected endlessly in the longitudinal direction. Therefore, the contact pitch interval of each pin contributing to power transmission can be halved, and the noise can be reduced without increasing the number of link parts leading to an increase in cost.

以下、本発明のチェーンベルトおよびベルト式無段変速機を各実施形態に基づいて説明する。 Hereinafter, the chain belt and belt type continuously variable transmission of the present invention will be described based on each embodiment.

（第１実施形態）
図１〜図７は、本発明を適用したチェーンベルトおよびベルト式無段変速機の第１実施形態を示し、図１は本実施形態におけるチェーンベルトに使用するリンクプレートとロッカピンおよび伝達ピンの概略図、図２は本実施形態のチェーンベルトの構成を示す部分正面図、図３はプーリに巻掛けられた状態の本実施形態のチェーンベルトを示す正面図、図４はプーリへの巻掛けられた状態での変速状態を説明する断面図、図５は図４に示すプーリとチェーンベルトとの接触状態を説明する説明図、図６は比較例のチェーンベルトを示す概略図、図７は本実施形態のチェーンベルトにおける伝達駆動力変化を比較例と共に示す特性図である。 (First embodiment)
1 to 7 show a first embodiment of a chain belt and a belt-type continuously variable transmission to which the present invention is applied, and FIG. 1 is an outline of a link plate, a rocker pin and a transmission pin used for the chain belt in this embodiment. 2 is a partial front view showing the configuration of the chain belt of the present embodiment, FIG. 3 is a front view showing the chain belt of the present embodiment in a state of being wound around a pulley, and FIG. 4 is wound around the pulley. FIG. 5 is an explanatory view for explaining the contact state between the pulley and the chain belt shown in FIG. 4, FIG. 6 is a schematic view showing a comparative chain belt, and FIG. It is a characteristic view which shows the transmission drive force change in the chain belt of embodiment with a comparative example.

本実施形態の無段変速機用のチェーンベルト１は、相対するテーパ面を有する固定シーブおよび可動シーブが一対となって夫々Ｖ溝を構成する駆動プーリと従動プーリとの間に掛け渡されて使用されるものである。具体的には、図１〜図３に示すように、積層方向に配列した複数枚のリンクプレート２(第１リンクプレート)の端部を、チェーンベルト１の長手方向で隣接する同じく積層方向に配列した複数枚のリンクプレート２(第２，３リンクプレート)の端部と重ね合わせて、両者の重なり合った端部同士に互いの関節運動が可能な一対のロッカピン３(第１，２ピン)を貫通させて順次連結することでリング状の無端ベルトに構成している。以下では、一対のロッカピン３を総称して単に「ロッカピン」とし、一対のロッカピン３を構成する個々のロッカピン３Ａ、３Ｂに対しては「内側ピン３Ａ」、「外側ピン３Ｂ」とする。 The chain belt 1 for a continuously variable transmission according to the present embodiment is stretched between a driving pulley and a driven pulley that form a V-groove as a pair of a fixed sheave and a movable sheave having opposing tapered surfaces. It is what is used. Specifically, as shown in FIGS. 1 to 3, end portions of a plurality of link plates 2 (first link plates) arranged in the stacking direction are adjacent to each other in the stacking direction adjacent to the longitudinal direction of the chain belt 1. A pair of rocker pins 3 (first and second pins) that can be overlapped with the ends of a plurality of linked link plates 2 (second and third link plates) and capable of mutual joint movement between the overlapping ends. The ring-shaped endless belt is formed by sequentially connecting the belts. Hereinafter, the pair of rocker pins 3 are collectively referred to simply as “rocker pins”, and the individual rocker pins 3A and 3B constituting the pair of rocker pins 3 are referred to as “inner pins 3A” and “outer pins 3B”.

また、積層方向に配列した各リンクプレート２は、その長手方向の中央部に、前記ロッカピン３と平行配置により伝達ピン４(第３ピン)を保持して備える。前記伝達ピン４は、ロッカピン３とは別に追加した動力伝達用の棒形状の部品である。この伝達ピン４は、図２に示すように、伝達ピン４を保持する当該リンクプレート２にロッカピン３により連結される両側のリンクプレート２の外周端部間に存在するよう配置される。なお、以下では、リング状に形成されたチェーンベルト１の外周側を「外径側」、内周側を「内径側」として説明する。 Each link plate 2 arranged in the stacking direction is provided with a transmission pin 4 (third pin) held in the center in the longitudinal direction in parallel with the rocker pin 3. The transmission pin 4 is a rod-shaped component for power transmission added separately from the rocker pin 3. As shown in FIG. 2, the transmission pins 4 are arranged so as to exist between the outer peripheral ends of the link plates 2 on both sides connected to the link plate 2 holding the transmission pins 4 by the rocker pins 3. In the following description, the outer peripheral side of the chain belt 1 formed in a ring shape is referred to as an “outer diameter side”, and the inner peripheral side is referred to as an “inner diameter side”.

前記ロッカピン３および伝達ピン４は、夫々の断面形状を備える成形ダイスにより引き抜き加工した引き抜き材を切断し、仕上げ加工して夫々形成される。前記ロッカピン３および伝達ピン４のリンクプレート２から両側に突出する端部は、図４に示すように、プーリ１０の固定シーブ１１および可動シーブ１２の相対するテーパ面で形成するＶ溝面１３に接触するよう傾斜された傾斜面に形成されている。また、その傾斜面は、その中央領域がプーリ１０の各シーブに面接触するように丸み(クラウニング)を帯びて突出させるクラウニング加工が施されている。このため、プーリ１０が変形しても接触状態の変化が少なく、プーリ１０の薄肉化が可能である。また、併せて、プーリ１０への巻付き径の小径化を図ることができる。 The rocker pin 3 and the transmission pin 4 are formed by cutting and finishing a drawn material drawn by a forming die having a cross-sectional shape. As shown in FIG. 4, the end portions of the rocker pin 3 and the transmission pin 4 that protrude from the link plate 2 on both sides are formed on the V groove surface 13 formed by the tapered surfaces of the fixed sheave 11 and the movable sheave 12 of the pulley 10. It is formed in the inclined surface inclined so that it may contact. Further, the inclined surface is subjected to a crowning process in which a central region is in contact with each sheave of the pulley 10 so as to be rounded (crowning) and protrude. For this reason, even if the pulley 10 is deformed, the change in the contact state is small, and the pulley 10 can be thinned. In addition, the diameter of the winding around the pulley 10 can be reduced.

前記チェーンベルト１は、駆動プーリ１０および従動プーリ１０へのチェーンベルト１の巻掛け時において、ロッカピン３および伝達ピン４の両端とプーリ１０におけるＶ溝面１３とが接触して、両者間で駆動力を伝達する。図４において、実線で示す状態は固定シーブ１１に対して可動シーブ１２の位置を接近させたプーリ径が「大径」の状態を示す。また、破線で示す状態は固定シーブ１１に対して可動シーブ１２の位置を離したプーリ径が「小径」の状態を夫々示す。図３に示すように、駆動プーリ１０Ａと従動プーリ１０Ｂとの間において、例えば、変速比が「ＬＯＷ」となる場合には、駆動プーリ１０Ａ側でプーリ径が小径となり従動プーリ１０Ｂ側で大径となる。また、前記とは逆に、例えば、変速比が「ＯＤ」となる場合には、図示しないが、駆動プーリ１０Ａ側でプーリ径が大径となり従動プーリ１０Ｂ側で小径となる。また、駆動プーリ１０Ａと従動プーリ１０Ｂとの間で互いに関連させてプーリ径を変化させることにより、変速比を連続的に無段階に変化させることができる。 The chain belt 1 is driven between both ends of the rocker pin 3 and the transmission pin 4 and the V groove surface 13 of the pulley 10 when the chain belt 1 is wound around the drive pulley 10 and the driven pulley 10. Transmit power. In FIG. 4, a state indicated by a solid line indicates a state where the pulley diameter in which the position of the movable sheave 12 approaches the fixed sheave 11 is “large diameter”. The state indicated by the broken line indicates a state in which the pulley diameter at which the position of the movable sheave 12 is separated from the fixed sheave 11 is “small diameter”. As shown in FIG. 3, for example, when the gear ratio is “LOW” between the driving pulley 10A and the driven pulley 10B, the pulley diameter is small on the driving pulley 10A side and the large diameter is on the driven pulley 10B side. It becomes. On the contrary, for example, when the gear ratio is “OD”, the pulley diameter is large on the drive pulley 10A side and small on the driven pulley 10B side, although not shown. Further, by changing the pulley diameter in association with each other between the driving pulley 10A and the driven pulley 10B, the transmission gear ratio can be continuously changed continuously.

前記リンクプレート２は、比較的容易に高精度が得られるファインブランキングにより、平板から打抜き加工により形成される。そして、図２に示すように、全体として外形形状が矩形状をなす環状体となっている。前記環状体の内周面の長手方向両端側には、前記ロッカピン３の外側ピン３Ｂの、内側ピン３Ａに対する背面側が係合するピン係合部５を備える。前記ピン係合部５は、内側ピン３Ａを外側ピン３Ｂに対して、後述するように、転がり移動を許容する形状に形成している。そして、前記両端のピン係合部５は、幅寸法が縮小された長手方向の空間により繋げた貫通孔で連通されている。また、前記リンクプレート２には、両側のピン係合部５間の中央領域において、前記貫通孔を形成する上下の縁部分を内外径方向に窪ませて、伝達ピン４を貫通させて収容する収容部６を形成している。また、前記リンクプレート２に形成する収容部６は、図１に示すように、両側のピン係合部５間の中央領域において、前記貫通孔を形成する上下の縁部分を内側に向けて突出させ、突出した領域の縁部分を夫々部分的に窪ませて形成してもよい。前記伝達ピン４は、図１に示すように、左右のロッカピン３（間隔ｂ）に対して夫々間隔ｃ、ｄを持って中間位置に配置される。前記間隔ｃ、ｄは、等しく（ｃ＝ｄ）しても、また、不等間隔（ｃ≠ｄ）としてもよい。また、リンクプレート２のロッカピン３が挿入されるピン係合部５と伝達ピン４を収容する収容部６（孔）は、図３に示すように、夫々独立した貫通孔により形成してもよい。 The link plate 2 is formed by punching from a flat plate by fine blanking which can obtain high accuracy relatively easily. As shown in FIG. 2, the outer shape as a whole is an annular body having a rectangular shape. On both ends in the longitudinal direction of the inner peripheral surface of the annular body, there are provided pin engaging portions 5 that engage the back side of the outer pin 3B of the rocker pin 3 with respect to the inner pin 3A. The pin engaging portion 5 is formed in a shape that allows the inner pin 3A to roll with respect to the outer pin 3B, as will be described later. And the pin engaging part 5 of the said both ends is connected by the through-hole connected by the space of the longitudinal direction where the width dimension was reduced. In the link plate 2, the upper and lower edge portions that form the through hole are recessed in the inner and outer diameter directions in the central region between the pin engaging portions 5 on both sides, and the transmission pin 4 is penetrated and accommodated. The accommodating part 6 is formed. Further, as shown in FIG. 1, the accommodating portion 6 formed on the link plate 2 protrudes in the center region between the pin engaging portions 5 on both sides, with the upper and lower edge portions forming the through-holes facing inward. The edge portions of the protruding regions may be partially recessed. As shown in FIG. 1, the transmission pin 4 is disposed at an intermediate position with intervals c and d with respect to the left and right rocker pins 3 (interval b). The intervals c and d may be equal (c = d) or unequal intervals (c ≠ d). Further, the pin engaging portion 5 into which the rocker pin 3 of the link plate 2 is inserted and the accommodating portion 6 (hole) for accommodating the transmission pin 4 may be formed by independent through holes as shown in FIG. .

前記ロッカピン３は、互いに相対して接触する面で互いに転がり接触して転動する一対のピン３Ａ、３Ｂにより形成されている。また、ロッカピン３は隣接するリンクプレート２の端部同士を重ね合わせて関節運動するリンクプレート２のピン係合部５に貫通させて挿入される。一対のピン３Ａ、３Ｂは各々は、リンクプレート２の夫々の外側ピン３Ｂがピン係合部５に一体に係合し、リンクプレート２の夫々の内側ピン３Ａは当該リンクプレート２のピン係合部５に対して隙間を持つよう構成している。即ち、図２に示すように、中央に位置するリンクプレート２のピン係合部５に挿入されたロッカピン３は、その一対のピン３Ａ、３Ｂの内の外側に位置する夫々の外側ピン３Ｂが中央位置のリンクプレート２の左右ピン係合部５の互いに離れた端部側の内面に一体に係合している。また、一対のピン３Ａ、３Ｂの内の内側に位置する夫々の内側ピン３Ａが、夫々の端部に関節接合される隣のリンクプレート２のピン係合部５の端部側の内面に一体に係合する。 The rocker pin 3 is formed by a pair of pins 3A and 3B that roll in contact with each other on surfaces that contact each other. Further, the rocker pin 3 is inserted through the pin engaging portion 5 of the link plate 2 that is articulated with the ends of the adjacent link plates 2 being overlapped. In each of the pair of pins 3A and 3B, each outer pin 3B of the link plate 2 is integrally engaged with the pin engaging portion 5, and each inner pin 3A of the link plate 2 is pin-engaged with the link plate 2. The part 5 is configured to have a gap. That is, as shown in FIG. 2, the rocker pin 3 inserted into the pin engaging portion 5 of the link plate 2 located at the center has the outer pins 3B located outside the pair of pins 3A and 3B. The left and right pin engaging portions 5 of the link plate 2 at the center position are integrally engaged with the inner surfaces of the end portions that are separated from each other. Also, each inner pin 3A located inside the pair of pins 3A, 3B is integrated with the inner surface of the end portion side of the pin engaging portion 5 of the adjacent link plate 2 jointed to each end portion. Engage with.

したがって、チェーンベルト１が直線状態からプーリ１０に巻き付く際および巻き付いたプーリ１０から離脱して直線状態となる折れ曲がり運動の際には、一対のピン３Ａ、３Ｂのうちの外側ピン３Ｂは当該リンクプレート２と一体に回動し、一対のピン３Ａ、３Ｂのうちの内側ピン３Ａは当該リンクプレート２に関節結合する隣のリンクプレート２と一体に回動する。結果として、隣接して関節結合したリンクプレート２同士は、両者間を連結するロッカピン３の一対のピン３Ａ、３Ｂ同士の転がり接触により連結され相対回転することとなる。 Therefore, when the chain belt 1 is wound around the pulley 10 from the straight state and when the chain belt 1 is bent so as to be separated from the wound pulley 10 to be in the straight state, the outer pin 3B of the pair of pins 3A and 3B is linked to the link. The inner pin 3 A of the pair of pins 3 A and 3 B rotates integrally with the adjacent link plate 2 jointed with the link plate 2. As a result, the link plates 2 that are adjacently connected to each other are connected to each other by the rolling contact between the pair of pins 3A and 3B of the rocker pin 3 that connects the two and rotate relative to each other.

以上の構成になる本実施形態の無段変速機用チェーンベルト１においては、ロッカピン３同士の間に伝達ピン４が追加されていることにより、リンクプレート２の長さを短くすることなく、プーリ１０への接触ピッチ間隔を半減させることができる。図５は変速比に応じて大きいプーリ径となる状態および小さいプーリ径となる状態において、チェーンベルト１がプーリ１０に巻き掛かった際のロッカピン３および伝達ピン４のＶ溝面１３への接触状態を示すものである。 In the continuously variable transmission chain belt 1 of the present embodiment having the above-described configuration, the transmission pin 4 is added between the rocker pins 3 so that the length of the link plate 2 can be reduced without shortening the pulley. The contact pitch interval to 10 can be halved. FIG. 5 shows a contact state of the rocker pin 3 and the transmission pin 4 with the V-groove surface 13 when the chain belt 1 is wound around the pulley 10 in a state where the pulley diameter is large and a state where the pulley diameter is small according to the gear ratio. Is shown.

変速比に応じて大きいプーリ径となる状態においてチェーンベルト１が巻き掛かった場合には、半径方向外側に示すように、プーリ１０を構成する固定シーブ１１および可動シーブ１２の曲率半径が大きいことから、左右のロッカピン３に対する伝達ピン４の外側へのオフセット量Ｘは比較的小さくなる。また逆に、変速比に応じて小さいプーリ径となる状態においてチェーンベルト１が巻き掛かった場合には、半径方向内側に示すように、プーリ１０を構成する固定シーブ１１および可動シーブ１２の曲率半径が小さいことから、左右のロッカピン３に対する伝達ピン４の外側へのオフセット量Ｘは比較的大きくなる。 When the chain belt 1 is wound in a state where the pulley diameter becomes large according to the gear ratio, the radius of curvature of the fixed sheave 11 and the movable sheave 12 constituting the pulley 10 is large as shown on the outer side in the radial direction. The offset X to the outside of the transmission pin 4 with respect to the left and right rocker pins 3 is relatively small. Conversely, when the chain belt 1 is wound in a state where the pulley diameter is small according to the gear ratio, the curvature radii of the fixed sheave 11 and the movable sheave 12 constituting the pulley 10 are shown on the inner side in the radial direction. Therefore, the offset amount X to the outside of the transmission pin 4 with respect to the left and right rocker pins 3 is relatively large.

チェーンベルト１がプーリ１０に巻付く動作としては、先ず先行するロッカピン３の一対の外側ピン３Ｂの端面がプーリ１０のＶ溝面１３に接触し、次いで一対の内側ピン３Ａの端面がプーリ１０のＶ溝面１３に接触する。固定シーブ１１と可動シーブ１２とを互いに接近させるよう作用するクランプ力に対向してロッカピン３はプーリ１０の半径方向外径側からＶ溝面１３に押し付けられる。この結果、プーリ１０のＶ溝面１３とロッカピン３端面に円周方向の摩擦力が発生し、プーリ１０のＶ溝面１３からロッカピン３に動力が伝達され、リンクプレート２へ伝達される。同時に一対の外側ピン３Ｂと内側ピン３Ａとは巻付き曲率によって互いに転がり運動を発生する。 As the operation of winding the chain belt 1 around the pulley 10, first, the end surfaces of the pair of outer pins 3 B of the preceding rocker pin 3 come into contact with the V groove surface 13 of the pulley 10, and then the end surfaces of the pair of inner pins 3 A Contact the V-groove surface 13. The rocker pin 3 is pressed against the V-groove surface 13 from the radially outer diameter side of the pulley 10 in opposition to the clamping force acting to bring the fixed sheave 11 and the movable sheave 12 closer to each other. As a result, a circumferential frictional force is generated on the V groove surface 13 of the pulley 10 and the end surface of the rocker pin 3, and power is transmitted from the V groove surface 13 of the pulley 10 to the rocker pin 3 and transmitted to the link plate 2. At the same time, the pair of outer pins 3B and the inner pins 3A generate rolling motions due to the winding curvature.

次に、伝達ピン４の端面がプーリ１０のＶ溝面１３と接触し、これによって、伝達ピン４もロッカピン３と同一曲率半径上にプーリ１０のＶ溝面１３に接触し、動力を伝達する。その後に、後行するロッカピン３（内側ピン３Ａおよび外側ピン３Ｂ）も同一曲率半径上でプーリ１０のＶ溝面１３と接触し、互いに転がり運動をしながら動力を伝達する。 Next, the end surface of the transmission pin 4 comes into contact with the V-groove surface 13 of the pulley 10, whereby the transmission pin 4 also comes into contact with the V-groove surface 13 of the pulley 10 on the same radius of curvature as the rocker pin 3 to transmit power. . Thereafter, the rocker pins 3 (the inner pins 3A and the outer pins 3B) that follow are also in contact with the V-groove surface 13 of the pulley 10 on the same radius of curvature, and transmit power while performing a rolling motion.

図７は本実施形態のチェーンベルト１のプーリ１０への巻付き状態における伝達動力の変化を、比較例のチェーンベルト１における伝達動力の変化と対比して示すものである。なお、比較例のチェーンベルト１は、図６に示すように、長さ（ａ≠ｂ）が異なる２種類のリンクプレート２を、１本のチェーンベルト１内にランダムに配置して、発生騒音を低減するものを選定した。 FIG. 7 shows a change in transmission power in the state where the chain belt 1 of the present embodiment is wound around the pulley 10 in comparison with a change in transmission power in the chain belt 1 of the comparative example. As shown in FIG. 6, the chain belt 1 of the comparative example has two types of link plates 2 having different lengths (a ≠ b) arranged at random in one chain belt 1 to generate noise. The one that reduces the

比較例のチェーンベルト１においては、先行するロッカピン３による動力伝達曲線が頂点から充分に低下した段階において後行するロッカピン３による動力伝達曲線が立ち上がる状態が繰り返されて、動力伝達力の変動幅が比較的大きく発生している。これは、先行するロッカピン３がプーリ１０のＶ溝面１３に接触して動力伝達が低下した後に、後行するロッカピン３が接触して動力伝達を開始することを繰り返すために生ずる。したがって、動力伝達誤差（回転ムラ）が大きく、加振エネルギが大きく、大きな騒音となる。また、ロッカピン３とＶ溝面１３との接触荷重が大きくなるため、ロッカピン３の磨耗が大きく、耐久性が低下する不具合も発生する。 In the chain belt 1 of the comparative example, the state in which the power transmission curve by the rocker pin 3 that follows is repeated at the stage where the power transmission curve by the preceding rocker pin 3 is sufficiently lowered from the top is repeated, and the fluctuation range of the power transmission force is reduced. It is relatively large. This occurs because the following rocker pin 3 comes into contact with the V-groove surface 13 of the pulley 10 to reduce power transmission, and then the subsequent rocker pin 3 comes into contact and starts power transmission. Therefore, the power transmission error (rotation unevenness) is large, the excitation energy is large, and the noise is large. In addition, since the contact load between the rocker pin 3 and the V-groove surface 13 is increased, the rocker pin 3 is greatly worn, resulting in a problem that durability is lowered.

これに対して、本実施形態におけるチェーンベルト１においては、先行するロッカピン３による動力伝達曲線が頂点から低下する間に伝達ピン４による動力伝達曲線が立上り、伝達ピン４による動力伝達曲線が頂点から低下する間に後行するロッカピン３による動力伝達曲線が立上る動作を交互に繰り返す。このため、動力伝達力の変動幅が比較的小さく抑えられている。結果として、加振エネルギを半減でき、動力伝達誤差（回転ムラ）が小さく、低騒音とできる。因みに、ノイズはピッチの３乗に比例するため、前記ピッチが半減されることにより、ノイズも１／８程度に低減できる。また、ロッカピン３および伝達ピン４とＶ溝面１３との接触荷重を小さくできるため、ロッカピン３および伝達ピン４の磨耗を抑制でき、耐久性を向上できる。しかも、リンクプレート２の長さを短縮化することなくピンのピッチ間隔を半減できるため、コスト増につながるリンク部品の点数を増やすことなく、低騒音化が図れる。 On the other hand, in the chain belt 1 in this embodiment, the power transmission curve by the transmission pin 4 rises while the power transmission curve by the preceding rocker pin 3 decreases from the top, and the power transmission curve by the transmission pin 4 starts from the top. While descending, the subsequent operation of rising the power transmission curve by the rocker pin 3 is repeated alternately. For this reason, the fluctuation range of the power transmission force is suppressed to be relatively small. As a result, the excitation energy can be halved, the power transmission error (unevenness of rotation) is small, and the noise can be reduced. Incidentally, since the noise is proportional to the cube of the pitch, the noise can be reduced to about 1/8 by reducing the pitch by half. Further, since the contact load between the rocker pin 3 and the transmission pin 4 and the V-groove surface 13 can be reduced, wear of the rocker pin 3 and the transmission pin 4 can be suppressed, and durability can be improved. In addition, since the pin pitch interval can be halved without shortening the length of the link plate 2, noise can be reduced without increasing the number of link parts that lead to increased costs.

また、図１に示すように、左右のロッカピン３（間隔ｂ）に対して夫々間隔ｃ、ｄを持って中間位置に配置される前記伝達ピン４を、不等間隔（ｃ≠ｄ、即ち、不等ピッチ化）とすることもできる。これは、伝達ピン４の収容部６（孔）の設置位置を変更することにより容易に変更可能である。この結果、加振周波数を更に分散させ、低騒音化の効果を増加させることができる。 Further, as shown in FIG. 1, the transmission pins 4 arranged at intermediate positions with intervals c and d with respect to the left and right rocker pins 3 (interval b) are arranged at unequal intervals (c ≠ d, that is, Unequal pitch). This can be easily changed by changing the installation position of the accommodating portion 6 (hole) of the transmission pin 4. As a result, the excitation frequency can be further dispersed, and the effect of reducing noise can be increased.

図８は本実施形態のチェーンベルト１の第２実施例を示したものである。この第２実施例によれば、伝達ピン４のプーリ１０のＶ溝面１３への接触点を、左右ロッカピン３のＶ溝面１３への接触点同士を結んだ直線に対して、プーリ巻き付き曲率分だけ外径側へオフセットした構成としている。このように構成することにより、伝達ピン４が両側のロッカピン３と同様にプーリ１０のＶ溝面１３と接触し、伝達ピン４およびロッカピン３の端面の接触荷重がより一層分散される。このため、各ピン端面の磨耗が分散され寿命向上につながる。 FIG. 8 shows a second example of the chain belt 1 of the present embodiment. According to the second embodiment, the contact point of the transmission pin 4 with respect to the V-groove surface 13 of the pulley 10 is set with respect to the straight line connecting the contact points with the V-groove surface 13 of the left and right rocker pins 3. It is configured to be offset to the outer diameter side by that amount. With this configuration, the transmission pin 4 comes into contact with the V-groove surface 13 of the pulley 10 like the rocker pins 3 on both sides, and the contact load on the end surfaces of the transmission pin 4 and the rocker pin 3 is further dispersed. For this reason, the wear of each pin end surface is dispersed and the life is improved.

なお、上記実施形態において、チェーンベルト１として、固定シーブ１１および可動シーブ１２を備えるＶ型プーリ１０間に巻掛けて無段変速機を構成するものについて説明したが、図示はしないが、両側のシーブが固定的に配置されるＶ型プーリの間に巻掛けるものであってもよい。 In the above embodiment, the chain belt 1 has been described as a continuously variable transmission that is wound around a V-type pulley 10 including a fixed sheave 11 and a movable sheave 12. The sheave may be wound around a V-shaped pulley that is fixedly disposed.

本実施形態においては、以下に記載する効果を奏することができる。 In the present embodiment, the following effects can be achieved.

（ア）両端部にピン係合部５を備えた複数枚のリンクプレート２と、前記リンクプレート２の係合部５と係合し、各リンクプレート２を関節運動可能に連結するロッカピン３と、を有し、前記ロッカピン３にて前記複数のリンクプレート２を無端状に連結した無段変速機用チェーンベルト１において、前記リンクプレート２のピン係合部５間に伝達ピン４の収容部６を設けると共に、前記伝達ピン４の収容部６を貫通させて伝達ピン４を前記ロッカピン３と平行に配置し、前記ロッカピン３の両端面をＶ型プーリ１０に摩擦接触させて第１の接触点を構成すると共に、前記伝達ピン４の両端面をＶ型プーリ１０に摩擦接触させて第２の接触点を構成した。したがって、リンクプレート２の長さ寸法を短くすることなくＶ型プーリ１０への接触ピッチ間隔を半減させることができ、コスト増につながるリンク部品点数を増加させることなく、低騒音化を図ることができる。 (A) A plurality of link plates 2 having pin engaging portions 5 at both ends, and rocker pins 3 that engage with the engaging portions 5 of the link plate 2 and connect the link plates 2 so that they can be articulated. In the continuously variable transmission chain belt 1 in which the plurality of link plates 2 are connected endlessly by the rocker pins 3, the accommodating portions of the transmission pins 4 between the pin engaging portions 5 of the link plates 2. 6, the accommodating portion 6 of the transmission pin 4 is penetrated, the transmission pin 4 is disposed in parallel with the rocker pin 3, and both end surfaces of the rocker pin 3 are brought into frictional contact with the V-type pulley 10 to form a first contact. In addition to forming a point, both end surfaces of the transmission pin 4 were brought into frictional contact with the V-type pulley 10 to form a second contact point. Therefore, the contact pitch interval to the V-type pulley 10 can be halved without shortening the length dimension of the link plate 2, and noise reduction can be achieved without increasing the number of link parts leading to cost increase. it can.

（イ）図１に示すように、伝達ピン４を、左右のロッカピン３同士の中間位置からチェーベルト１の長手方向のいずれかに偏らせて配置することにより、Ｖ型プーリ１０への接触による加振周波数を分散させ、より低騒音化の効果を増加させることができる。 (A) As shown in FIG. 1, the transmission pin 4 is arranged so as to be deviated from an intermediate position between the left and right rocker pins 3 in any one of the longitudinal directions of the chain belt 1, thereby making contact with the V-type pulley 10. It is possible to disperse the excitation frequency and increase the noise reduction effect.

（ウ）伝達ピン４を左右のロッカピン３同士の中間の位置に配置することにより、リンクプレート２の長さ寸法を短くできると共にロッカピン３および伝達ピン４で構成するＶ型プーリ１０への接触ピッチ間隔を短くでき、低騒音化を図ることができる。 (C) By arranging the transmission pin 4 at an intermediate position between the left and right rocker pins 3, the length dimension of the link plate 2 can be shortened and the contact pitch to the V-shaped pulley 10 constituted by the rocker pin 3 and the transmission pin 4. The interval can be shortened, and noise can be reduced.

（エ）図８に示すように、伝達ピン４を、左右のロッカピン３同士で形成する平面よりチェーンベルト１の外側にオフセットして配置することにより、Ｖ型プーリ１０への巻付け時に伝達ピン４をプーリ巻き付き曲率分だけ外側にオフセットされてロッカピン３と同一ピッチ円周上に接触させることができ、各ピン端面の接触荷重を分散でき、各ピン端面の磨耗が分散され、寿命向上できる。 (D) As shown in FIG. 8, the transmission pin 4 is offset from the plane formed by the left and right rocker pins 3 to the outside of the chain belt 1 so that the transmission pin 4 is wound around the V-type pulley 10. 4 is offset outwardly by the curvature of the winding of the pulley and can be brought into contact with the rocker pin 3 on the same pitch circumference, the contact load of each pin end surface can be dispersed, the wear of each pin end surface is dispersed, and the life can be improved.

（第２実施形態）
図９〜図１４は、本発明を適用したチェーンベルトおよびベルト式無段変速機の第２実施形態を示し、図９はチェーンベルトの詳細を示す構成図、図１０は伝達ピンとリンクプレートとの関係を説明する説明図、図１１，１２は駆動プーリ１０への巻付き状態における変速比大および変速比小の状態を示す説明図、図１３はリンクプレートに生ずる作用力を説明する説明図、図１４はチェーンベルトの第２の実施例を示す説明図である。本実施形態においては、伝達ピンをリンクプレートの端部に設けた弧状突起に接触・係合させた構成を第１実施形態に追加したものである。なお、第１実施形態と同一装置・部品には同一符号を付してその説明を省略ないし簡略化する。 (Second Embodiment)
9 to 14 show a second embodiment of a chain belt and a belt-type continuously variable transmission to which the present invention is applied, FIG. 9 is a configuration diagram showing details of the chain belt, and FIG. 10 is a diagram showing a transmission pin and a link plate. FIG. 11 and FIG. 12 are explanatory diagrams showing a state of a large transmission gear ratio and a small transmission gear ratio when the drive pulley 10 is wound, and FIG. 13 is an explanatory diagram explaining an acting force generated in the link plate. FIG. 14 is an explanatory view showing a second embodiment of the chain belt. In the present embodiment, a configuration in which the transmission pin is brought into contact with and engaged with an arc-shaped protrusion provided at the end of the link plate is added to the first embodiment. In addition, the same code | symbol is attached | subjected to the same apparatus and components as 1st Embodiment, and the description is abbreviate | omitted or simplified.

図９において、本実施形態のチェーンベルト１の左右のロッカピン３間に配置されている伝達ピン４は、当該伝達ピン４を収容するリンクプレート２の収容部６（孔）に対して、内外径方向に隙間をもって配置されて、チェーンベルト１の内外径方向（図中の上下方向）に移動可能に構成している。また、伝達ピン４のチェーン長手方向の両面には、リンクプレート２の端部と係合する略円弧状断面の窪みを伝達ピン４軸方向に延在させた係合溝７を形成している。また、前記伝達ピン４の前記係合溝７に臨んで配置されるリンクプレート２の端部には、前記伝達ピン４の係合溝７に係合する弧状突起８を形成している。 In FIG. 9, the transmission pin 4 disposed between the left and right rocker pins 3 of the chain belt 1 of the present embodiment has inner and outer diameters relative to the accommodating portion 6 (hole) of the link plate 2 that accommodates the transmission pin 4. It arrange | positions with a clearance gap in the direction, and is comprised so that a movement in the inner-outer-diameter direction (up-down direction in a figure) of the chain belt 1 is possible. Further, on both surfaces of the transmission pin 4 in the longitudinal direction of the chain, engagement grooves 7 are formed in which recesses having a substantially arc-shaped cross section that engages with the end of the link plate 2 extend in the axial direction of the transmission pin 4. . An arc-shaped protrusion 8 that engages with the engaging groove 7 of the transmission pin 4 is formed at the end of the link plate 2 that faces the engaging groove 7 of the transmission pin 4.

図１０は前記係合溝７および弧状突起８の係合状態を拡大して示すものである。前記係合溝７は、伝達ピン４を保持している当該リンクプレート２とその両側に夫々配置されるリンクプレート２とを互いに転がり接触させるロッカピン３の転がり接触点を中心とし、ロッカピン３の転がり接触点からの概略距離を半径とする概略円弧状に形成している。 FIG. 10 shows the engagement state of the engagement groove 7 and the arcuate protrusion 8 in an enlarged manner. The engagement groove 7 rolls the rocker pin 3 around the rolling contact point of the rocker pin 3 that causes the link plate 2 holding the transmission pin 4 and the link plates 2 disposed on both sides thereof to roll and contact each other. It is formed in a generally arcuate shape with a radius from the approximate distance from the contact point.

また、リンクプレート２の端部に形成された、前記係合溝７と係合する弧状突起８は、半径方向線Ｃ１と交差する部位の円弧形状Ｃ２と、半径方向線Ｂ１と交差する部位の円弧形状Ｂ２と、半径方向線Ａ１と交差する部位の円弧形状Ａ２と、を備える。前記円弧形状Ｂ２は、前記ロッカピン３の転がり接触点を中心として、同様の半径を備える円弧状の形状ロッカピン３の転がり接触点までの概略距離を半径とする円弧状の形状Ｂの部分円弧に形成されている。前記円弧形状Ｃ２は、前記ロッカピン３の転がり接触点よりチェーン外径側(図中の上側)へオフセットした部分を中心として、同様の半径を備える円弧状の形状Ｃの部分円弧に形成されている。前記円弧形状Ａ２は、前記ロッカピン３の転がり接触点よりチェーン内径側(図中の下側)へオフセットした部分を中心として同様の半径を備える円弧状の形状Ａの部分円弧に形成されている。 Further, the arc-shaped protrusion 8 that engages with the engaging groove 7 formed at the end of the link plate 2 has an arc shape C2 that intersects the radial line C1 and a portion that intersects the radial line B1. An arc shape B2 and an arc shape A2 that intersects the radial line A1 are provided. The circular arc shape B2 is formed in a partial circular arc of the circular arc shape B having a radius of an approximate distance from the rolling contact point of the rocker pin 3 to the rolling contact point of the circular arc shape rocker pin 3 having a similar radius. Has been. The arc shape C2 is formed as a partial arc of an arc shape C having a similar radius around a portion offset from the rolling contact point of the rocker pin 3 to the chain outer diameter side (upper side in the drawing). . The arc shape A2 is formed as a partial arc of an arc shape A having a similar radius centered on a portion offset from the rolling contact point of the rocker pin 3 toward the inner diameter side of the chain (lower side in the figure).

前記の各円弧形状Ａ２〜Ｃ２は、半径方向線Ｃ１と交差する円弧形状Ｃ２の部分から、円弧中心の外径側へのオフセットを徐々に減少させつつ、半径方向線Ｂ１と交差する円弧形状Ｂ２の部分に連なるよう形成している。また、半径方向線Ｂ１と交差する円弧形状Ｂ２の部分から、円弧中心の内径側へのオフセットを徐々に増加させつつ、半径方向線Ａ１と交差する円弧形状Ａ２の部分に連なるよう形成している。即ち、弧状突起８の形状は、これらの円弧形状Ａ２〜Ｃ２をつないだ包絡線により形成された輪郭を備える。その他の構成は、第１実施形態と同様に構成されている。 Each of the arc shapes A2 to C2 has an arc shape B2 that intersects the radial line B1 while gradually reducing the offset from the arc shape C2 portion that intersects the radial line C1 to the outer diameter side of the arc center. It is formed so as to continue to the part. In addition, the arc shape B2 that intersects the radial line B1 is formed so as to continue to the arc shape A2 that intersects the radial line A1 while gradually increasing the offset toward the inner diameter side of the arc center. . That is, the shape of the arc-shaped protrusion 8 has a contour formed by an envelope connecting these arc shapes A2 to C2. Other configurations are the same as those in the first embodiment.

図１０中の破線で示す円弧Ａおよび当該円弧Ａの中心とを結ぶ半径方向線Ａ１は、図９に示すように、チェーンベルト１が直線状態となった時に半径方向線Ａ１同士が一直線となる弧状突起８の配列状態を示している。また、図１０中の一点鎖線で示す円弧Ｂおよび当該円弧Ｂの中心とを結ぶ半径方向線Ｂ１は、図１２に示すように、ＯＤ（オーバドライブ）状態においてチェーンベルト１が駆動プーリ１０側で所定の曲率で曲げられた時及びＬＯＷ（低速ドライブ）状態においてチェーンベルト１が従動プーリ１０側で所定の曲率で曲げられた時に、互いの半径方向線Ｂ１で示す円弧領域同士が、伝達ピン４の係合溝７の下部領域に係合する弧状突起８の配列状態を示している。さらに、図１０中の二点鎖線で示す円弧Ｃおよび当該円弧Ｃの中心とを結ぶ半径方向線Ｃ１は、図１１に示すように、ＬＯＷ（低速ドライブ）状態において、チェーンベルト１が駆動プーリ１０側で大きい曲率で曲げられた時及びＯＤ（オーパドライブ）状態においてチェーンベルト１が従動プーリ１０側で所定の曲率で曲げられた時に、互いの半径方向線同士Ｃ１で示す円弧領域同士が、伝達ピン４の係合溝７の下部領域に係合する弧状突起８の配列状態を示している。各円弧Ａ〜Ｃおよびその中心位置の夫々半径方向Ａ１〜Ｃ１（チェーンベルト１の内外径方向）へのオフセットは、チェーンベルト１の曲げ状態に応じて、伝達ピン４のチェーベルト内外径方向の保持位置を変化させるために形成している。 As shown in FIG. 9, the radial line A1 connecting the arc A indicated by the broken line in FIG. 10 and the center of the arc A becomes a straight line when the chain belt 1 is in a straight state. The arrangement | sequence state of the arc-shaped protrusion 8 is shown. Further, as shown in FIG. 12, the radial line B1 connecting the circular arc B indicated by the one-dot chain line in FIG. 10 and the center of the circular arc B indicates that the chain belt 1 is on the drive pulley 10 side in the OD (overdrive) state. When the chain belt 1 is bent with a predetermined curvature on the driven pulley 10 side in a LOW (low speed drive) state when bent with a predetermined curvature, the arc regions indicated by the radial lines B1 are the transmission pins 4. The arrangement | sequence state of the arc-shaped processus | protrusion 8 engaged with the lower region of this engagement groove | channel 7 is shown. Furthermore, as shown in FIG. 11, a radial line C1 connecting the circular arc C indicated by a two-dot chain line in FIG. 10 and the center of the circular arc C indicates that the chain belt 1 is connected to the driving pulley 10 in the LOW (low speed drive) state. When the chain belt 1 is bent with a predetermined curvature on the driven pulley 10 side when the belt belt 1 is bent with a large curvature on the side and in the OD (overdrive) state, the arc regions indicated by the mutual radial lines C1 are transmitted. An arrangement state of arcuate protrusions 8 engaged with the lower region of the engaging groove 7 of the pin 4 is shown. The offsets of the respective arcs A to C and the center positions thereof in the radial directions A1 to C1 (inner and outer diameter directions of the chain belt 1) are in the inner and outer diameter directions of the transmission pin 4 according to the bending state of the chain belt 1. It is formed to change the holding position.

従って、本実施形態のチェーンベルト１においては、前記伝達ピン４のチェーベルト内外径方向の位置が、伝達ピン４を収容する当該リンクプレート２と当該リンクプレート２にロッカピン３により連結されたリンクプレート２との相対曲げ角度に応じて、隣接するリンクプレート２の端部に形成した弧状突起８の内外径方向（チェーンベルト１の内外径方向）への相対位置変化（前記オフセット）に応じて変化される。 Therefore, in the chain belt 1 of the present embodiment, the position of the transmission pin 4 in the inner and outer diameter directions of the chain belt is the link plate 2 that houses the transmission pin 4 and the link plate that is connected to the link plate 2 by the rocker pin 3. 2 changes according to the relative position change (the offset) in the inner / outer diameter direction (inner / outer diameter direction of the chain belt 1) of the arc-shaped protrusion 8 formed at the end of the adjacent link plate 2 Is done.

具体的には、隣接するリンクプレート２同士が直線となる、プーリ１０間にあってプーリ１０に巻付いていない状態のチェーンベルト１部分においては、図９に示すように、両隣のリンクプレート２同士は直線状に配列されて、その弧状突起８の中心が最も内径側（図中の下側）に位置することにより、弧状突起８に係合する係合溝７を備える伝達ピン４の内外径方向位置も最も内側（図中の下側）に位置する。なお、この状態においては、伝達ピン４はプーリ１０に接触していないため、プーリ１０からの外力が作用せず、上記のように、専ら弧状突起８と係合溝７との係合により位置決めされる。 Specifically, in the chain belt 1 portion in which the adjacent link plates 2 are in a straight line and are not wound around the pulley 10 between the pulleys 10, as shown in FIG. Inner and outer diameter directions of the transmission pin 4 provided with the engagement grooves 7 that are arranged in a straight line and have the center of the arc-shaped protrusion 8 located on the innermost diameter side (the lower side in the drawing) to be engaged with the arc-shaped protrusion 8. The position is also located on the innermost side (lower side in the figure). In this state, since the transmission pin 4 is not in contact with the pulley 10, the external force from the pulley 10 does not act, and as described above, the positioning is performed exclusively by the engagement between the arc-shaped protrusion 8 and the engagement groove 7. Is done.

また、隣接するリンクプレート２同士が相対的に大きく曲げられる、相対的に小径となった駆動側プーリ１０に巻付いて相対的に大径の従動側プーリ１０を駆動するＬＯＷ駆動状態のチェーンベルト１部分においては、図１１に示すように、両隣のリンクプレート２同士は大きく折曲げて配列される。伝達ピン４にはプーリ１０に接触することにより、チェーンベルト外径方向へ移動させる外力が作用する。このため、その弧状突起８が最も内外径方向外側（図中の上側）に位置（オフセット）して、半径方向線同士Ｃ１で示す円弧領域同士が伝達ピン４の係合溝７の下部領域に係合することにより、伝達ピン４の内外方向位置も最も外側（図中の上側）に位置させて、前記プーリ１０からの外力に対向して伝達ピン４を保持する。この場合に、チェーンベルト１の長手方向両側で隣り合って左右に配置される一対のリンクプレート２の弧状突起８のロッカピン３の転がり点を中心とした回動運動の回転成分は弧状突起８と伝達ピン４の係合溝７とのすべりによる接触位置変化に吸収され、弧状突起８の内外径方向外側へのオフセット移動成分のみが伝達ピン４に伝達されて、伝達ピン４を内外方向外側へ移動させる。 In addition, the chain belt in the LOW driving state in which the adjacent link plates 2 are bent relatively large and wound around the driving pulley 10 having a relatively small diameter to drive the driven pulley 10 having a relatively large diameter. In one part, as shown in FIG. 11, the link plates 2 on both sides are largely bent and arranged. An external force that moves the transmission pin 4 in the outer diameter direction of the chain belt acts by contacting the pulley 10. For this reason, the arc-shaped protrusion 8 is positioned (offset) at the outermost radial inner side (the upper side in the drawing), and the arc regions indicated by the radial lines C1 are the lower region of the engaging groove 7 of the transmission pin 4. By engaging, the inner and outer positions of the transmission pin 4 are also positioned on the outermost side (upper side in the drawing), and the transmission pin 4 is held facing the external force from the pulley 10. In this case, the rotational component of the rotational movement around the rolling point of the rocker pin 3 of the arc-shaped projections 8 of the pair of link plates 2 arranged on the left and right sides adjacent to each other in the longitudinal direction of the chain belt 1 is the arc-shaped projection 8. Absorbed by the change in contact position due to the sliding of the transmission pin 4 with the engaging groove 7, only the offset movement component of the arc-shaped protrusion 8 toward the outer side in the inner and outer radial directions is transmitted to the transmission pin 4, and the transmission pin 4 is moved outward in the inner and outer direction. Move.

同様に、隣接するリンクプレート２同士の相対的な曲げが比較的に小さくなる、相対的に大径となった駆動側プーリ１０に巻付いて相対的に小径の従動側プーリ１０を駆動するＯＤ駆動状態のチェーンベルト１部分においては、図１２に示すように、両隣のリンクプレート２同士の曲げは小さくなるよう配列される。この場合においても、伝達ピン４にはプーリ１０に接触することにより、チェーンベルト外径方向へ移動させる外力が作用する。このため、その弧状突起８がＬＯＷ駆動状態よりも内外径方向内側（図中の下側）に位置（オフセット）し、半径方向線同士Ｂ１で示す円弧領域同士が伝達ピン４の係合溝７の下部領域に係合することにより、伝達ピン４の内外径方向位置も、ＬＯＷ駆動状態よりも内側（図中の下側）に位置させて、前記プーリ１０からの外力に対向して伝達ピン４を保持する。この場合においても、チェーンベルト１の長手方向両側で隣り合って左右に配置される一対のリンクプレート２の弧状突起８のロッカピン３の転がり点を中心とした回動運動の回転成分は弧状突起８と伝達ピン４の係合溝７とのすべりによる接触位置変化に吸収され、弧状突起８の半径方向外側へのオフセット移動成分のみが伝達ピン４に伝達されて、伝達ピン４を内外方向外側へ移動させる。 Similarly, an OD that drives a relatively small diameter driven pulley 10 by winding around a relatively large diameter drive pulley 10 with relatively small relative bending between adjacent link plates 2. In the chain belt 1 portion in the driven state, as shown in FIG. 12, the adjacent link plates 2 are arranged so that the bending between the link plates 2 is small. Even in this case, an external force that moves in the direction of the outer diameter of the chain belt acts on the transmission pin 4 by contacting the pulley 10. For this reason, the arc-shaped protrusion 8 is positioned (offset) inwardly and radially outwardly (downward in the drawing) from the LOW driving state, and the arc regions indicated by the radial lines B1 are the engagement grooves 7 of the transmission pin 4. Is engaged with the lower region of the transmission pin 4 so that the inner and outer radial positions of the transmission pin 4 are also located on the inner side (lower side in the figure) than the LOW driving state, and opposed to the external force from the pulley 10. 4 is held. Even in this case, the rotational component of the rotational movement around the rolling point of the rocker pin 3 of the arc-shaped projections 8 of the pair of link plates 2 adjacent to each other on both sides in the longitudinal direction of the chain belt 1 is the arc-shaped projection 8. Is absorbed by the change in the contact position due to the sliding of the transmission pin 4 with the engagement groove 7, and only the offset movement component of the arcuate protrusion 8 outward in the radial direction is transmitted to the transmission pin 4, so Move.

なお、第１実施形態に記載したチェーンベルト１においては、伝達ピン４が当該リンクプレート２に対して、収容部６（孔）により内外方向への移動を拘束した状態で、固定的に保持されるものであるため、ロッカピン３のプーリ１０への接触ピッチサークルとできるだけ同一サークル上で接触するよう、左右ロッカピン３より内外方向外方へオフセットして配置することが望まれる。しかしながら、このように特定の曲率半径のピッチサークルの巻付き半径が小さい領域に対応して位置設定すると、駆動プーリ１０側での巻付き半径が小さいＬＯＷ駆動時と、従動プーリ１０側での巻付き半径が小さいＯＤ駆動時においては伝達ピン４を加えた３点接触となるが、その他の変速比においては、伝達ピン４によるプーリ１０への接触が達成されずに、２点接触となり、接触ピッチが大きく騒音が大きい状態となる領域が存在した。 In the chain belt 1 described in the first embodiment, the transmission pin 4 is fixedly held with respect to the link plate 2 in a state where movement in the inner and outer directions is restricted by the accommodating portion 6 (hole). Therefore, it is desirable to arrange the rocker pins 3 so as to be offset inwardly and outwardly from the left and right rocker pins 3 so that the rocker pins 3 are in contact with the pulley 10 on the same pitch circle as possible. However, if the position is set corresponding to the region where the winding radius of the pitch circle having a specific curvature radius is small as described above, the wrapping radius on the driving pulley 10 side is small and the winding on the driven pulley 10 side is performed. At the time of OD driving with a small radius, the contact is made with 3 points including the transmission pin 4, but at other speed ratios, the contact with the pulley 10 by the transmission pin 4 is not achieved and the contact is made with 2 points. There was a region where the pitch was large and the noise was high.

しかしながら、本実施形態のチェーンベルト１においては、伝達ピン４がリンクプレート２同士の傾き角度、即ち、プーリ１０への巻付きの曲率半径に応じて、曲率半径が小さい場合には左右のロッカピン３に対して大きく半径方向外側に位置決め（オフセット）されてロッカピン３と同一ピッチ円上の接触点に接触して、プーリ１０への３点接触を確保する。また、リンクプレート２同士の傾き角度、即ち、プーリ１０への巻付きの曲率半径の増加につれて、伝達ピン４の左右のロッカピン３に対する内外方向外側へのオフセット量が減少されることにより、ロッカピン３と同一ピッチ円上の接触点に接触して、プーリ１０への３点接触を維持する。 However, in the chain belt 1 of the present embodiment, the left and right rocker pins 3 when the radius of curvature of the transmission pin 4 is small according to the angle of inclination between the link plates 2, that is, the radius of curvature around the pulley 10. Is positioned (offset) radially outward with respect to the rocker pin 3 and contacts a contact point on the same pitch circle to ensure three-point contact with the pulley 10. Further, as the inclination angle between the link plates 2, that is, the radius of curvature of the winding around the pulley 10 increases, the amount of offset of the transmission pin 4 to the left and right rocker pins 3 to the outside in the inner and outer directions decreases, and the rocker pin 3 The three-point contact to the pulley 10 is maintained by contacting the contact point on the same pitch circle.

したがって、本実施形態のチェーンベルト１においては、ロッカピン３間に配置された伝達ピン４が、変速比の変更によるプーリ１０への巻付き曲率に応じて内外方向位置（オフセット量）を制御され、特定の変速比だけでなく全変速領域で３点接触を維持・確保することができる。このため、本実施形態のチェーンベルト１の伝達ピン４は、ＬＯＷ駆動時は最も外側にオフセットし、巻付き半径小に対応し、ＯＤ駆動時はやや外側へのオフセットを減少させることで、巻付き半径の変化に対応し、どの変速比においてもチェーンピッチ円上の３点接触が可能となり、噛合いピッチを小さく維持して低騒音を実現できる。 Therefore, in the chain belt 1 of the present embodiment, the transmission pin 4 disposed between the rocker pins 3 is controlled in the inner / outer direction position (offset amount) according to the winding curvature of the pulley 10 due to the change in the gear ratio, It is possible to maintain and secure a three-point contact not only in a specific gear ratio but also in the entire gear range. For this reason, the transmission pin 4 of the chain belt 1 of the present embodiment is offset outwardly at the time of LOW driving, corresponds to a small winding radius, and slightly reduces the offset to the outside at the time of OD driving. Corresponding to the change in the attached radius, three-point contact on the chain pitch circle is possible at any gear ratio, and low noise can be realized by keeping the mesh pitch small.

なお、上記した実施例では、係合溝７と係合するリンクプレート２の端部に形成された弧状突起８として、半径方向線Ａ１〜Ｃ１と交差する夫々の円弧領域の法絡線により形成される輪郭を備えるものについて説明したが、弧状突起８の形状は、この例に限定されず、同様な動きを成立させる別のカム形状であってもよい。 In the above-described embodiment, the arcuate protrusion 8 formed at the end of the link plate 2 engaged with the engaging groove 7 is formed by the normal line of each arc region intersecting with the radial lines A1 to C1. However, the shape of the arc-shaped protrusion 8 is not limited to this example, and may be another cam shape that achieves the same movement.

図１３は本実施形態のチェーンベルト１をプーリ１０に巻き付けた際に発生する作用力を示す説明図である。各リンクプレート２には、（図示しないプーリ１０の対向するシーブへ接触する）左右のロッカピン３の一対のピン（内側ピン３Ａおよび外側ピン３Ｂ）からの反力（リンク張力Ｆ０）が作用する。このリンク張力Ｆ０はリンクプレート２の長手方向にリンクプレート２を引き伸ばすよう作用し、リンクプレート２の内外方向内側および外側のリブ２Ａにより受け持たれる。 FIG. 13 is an explanatory view showing the acting force generated when the chain belt 1 of this embodiment is wound around the pulley 10. The reaction force (link tension F0) from the pair of pins (inner pin 3A and outer pin 3B) of the left and right rocker pins 3 (contacts with the opposing sheave of the pulley 10 (not shown)) acts on each link plate 2. The link tension F0 acts to stretch the link plate 2 in the longitudinal direction of the link plate 2 and is supported by the ribs 2A on the inner and outer sides of the link plate 2 in the inner and outer directions.

前記伝達ピン４には、図示しないプーリ１０の対向するテーパ状のシーブ１１，１２へ接触により内外方向外側への接触反力Ｆ１が作用する。この接触反力Ｆ１は、伝達ピン４の両側面に形成した係合溝７とチェーンベルト１の長手方向両側で隣り合って左右に配置される一対のリンクプレート２の弧状突起８との接触部に作用する。そして、この接触反力Ｆ２による内外方向内方への合成反力Ｆ３により相殺され、伝達ピン４の内外方向位置が保持される。同時に、前記接触部からリンクプレート２の弧状突起８に作用する内外方向外方への作用力Ｆ４は、リンクプレート２の張力Ｆ０に対向して作用し、この張力Ｆ０の一部をキャンセルするよう作用する。このため、リンクプレート２の強度をより向上させ、チェーンベルト１の高容量化を可能とする。 The transmission pin 4 is subjected to a contact reaction force F 1 outward in the inner / outer direction by contact with the tapered sheaves 11, 12 of the pulley 10 (not shown) facing each other. This contact reaction force F1 is a contact portion between the engagement groove 7 formed on both side surfaces of the transmission pin 4 and the arc-shaped projections 8 of the pair of link plates 2 arranged on the left and right sides on both sides in the longitudinal direction of the chain belt 1. Act on. Then, the contact reaction force F2 cancels out by the combined reaction force F3 inward and outward, and the position of the transmission pin 4 in the inner and outer directions is maintained. At the same time, the outward and outward acting force F4 acting on the arc-shaped protrusion 8 of the link plate 2 from the contact portion acts against the tension F0 of the link plate 2 so as to cancel a part of the tension F0. Works. For this reason, the strength of the link plate 2 is further improved, and the capacity of the chain belt 1 can be increased.

図１４に示す本実施形態の他の実施例のチェーンベルト１においては、伝達ピン４を２個に分割してリンクプレート２の夫々の収容部６に保持させたものである。前記夫々の収容部６は互いに独立され、夫々の側においてロッカピン３のピン係合部５と繋げた貫通孔により形成されている。夫々の伝達ピン４は、その係合溝７の片側において隣接するリンクプレート２の弧状突起８に係合させて構成している。 In the chain belt 1 of another example of the present embodiment shown in FIG. 14, the transmission pin 4 is divided into two parts and held in the respective accommodating portions 6 of the link plate 2. The respective accommodating portions 6 are independent from each other and are formed by through holes connected to the pin engaging portions 5 of the rocker pins 3 on the respective sides. Each transmission pin 4 is configured to engage with an arcuate protrusion 8 of the adjacent link plate 2 on one side of the engagement groove 7.

この実施例のチェーンベルト１においても、図９〜図１２に示す実施例と同様に、プーリ１０への巻き付け時にその巻付き曲率により変化するリンクプレート２同士の折り曲げ角度に応じて、伝達ピン４の内外径方向位置（オフセット量）が制御され、特定の変速比だけでなく全変速領域で４点接触を維持・確保することができる。
このため、ＬＯＷ駆動時は最も外側にオフセットして巻付き半径小に対応し、ＯＤ駆動時はややオフセットを減少させることで巻付き半径大に対応し、どの変速比においてもピッチ円上の４点接触が可能となる。このため、噛合いピッチを左右ロッカピン３と２個の伝達ピン４とにより、より一層小さく維持してより一層低騒音を実現できる。さらに、第１実施例と同じ接触ピッチであっても、リンクプレート２長が長くなるため、リンクプレート２の枚数、ピン本数を削減できる効果がある。 Also in the chain belt 1 of this embodiment, as in the embodiment shown in FIGS. 9 to 12, the transmission pin 4 varies depending on the bending angle of the link plates 2 that changes depending on the winding curvature when the pulley 10 is wound. The position in the inner and outer diameter direction (offset amount) of the gear is controlled, and four-point contact can be maintained and ensured not only in a specific gear ratio but also in the entire speed change region.
For this reason, at the time of LOW driving, it corresponds to a small winding radius by offsetting to the outermost side, and at the time of OD driving, it corresponds to a large winding radius by slightly reducing the offset. Point contact is possible. For this reason, the engagement pitch can be kept even smaller by the left and right rocker pins 3 and the two transmission pins 4, and further noise can be realized. Furthermore, even if the contact pitch is the same as that of the first embodiment, the length of the link plate 2 is increased, so that the number of link plates 2 and the number of pins can be reduced.

また、図１３と同様に、プーリ１０のシーブへの接触により伝達ピン４に作用する半径方向外側への作用力Ｆ１は、係合溝７と弧状突起８との接触部に作用し、この接触反力Ｆ２による内外方向内方への合成反力Ｆ３により相殺され、伝達ピン４の内外方向位置が保持される。同時に、前記接触部からリンクプレート２の弧状突起８に作用する内外方向外方への作用力Ｆ４は、リンクプレート２の張力Ｆ０に対向して作用し、この張力Ｆ０の一部をキャンセルするよう作用する。なお、２個の伝達ピン４同士の間には、前記キャンセル力は作用しないため、リンクプレート２の内外のリブ２Ａの強度を増加させる必要があるが、このリブ２Ａの強度は、リブ幅の増加により容易に強度確保が可能である。したがって、本実施例においても、リンクプレート２の強度をより向上させ、チェーンベルト１の高容量化を可能とする。 Similarly to FIG. 13, the radially outward acting force F 1 acting on the transmission pin 4 by the contact of the pulley 10 with the sheave acts on the contact portion between the engagement groove 7 and the arc-shaped protrusion 8, and this contact It is canceled by the combined reaction force F3 inward and outward in the reaction force F2, and the position of the transmission pin 4 in the inside and outside direction is maintained. At the same time, the outward and outward acting force F4 acting on the arc-shaped protrusion 8 of the link plate 2 from the contact portion acts against the tension F0 of the link plate 2 so as to cancel a part of the tension F0. Works. Since the canceling force does not act between the two transmission pins 4, it is necessary to increase the strength of the ribs 2A inside and outside the link plate 2. The strength of the ribs 2A is equal to the rib width. The strength can be easily secured by the increase. Therefore, also in the present embodiment, the strength of the link plate 2 is further improved and the capacity of the chain belt 1 can be increased.

なお、上記実施形態において、伝達ピン４とチェーンベルト１の長手方向両側で隣り合って左右に配置される一対のリンクプレート２との係合構造として、伝達ピン４側に設ける係合溝７と突起８とが円弧状の接触面により係合するものについて説明したが、図示はしないが、いずれか一方を円弧状面とし他方を前記円弧状面に接触するよう構成してもよい。また、係合溝７と突起８との一方をカム面に形成して、チェーンベルト１の長手方向両側で隣り合って左右に配置される一対のリンクプレート２同士の相対曲げの曲率の変化に応じて係合溝７と突起８との接触点を変化させて、伝達ピン４のチェーンベルト１の内外方向（プーリに対して半径方向）の位置を積極的に制御するようにしてもよい。 In the above embodiment, the engagement groove 7 provided on the transmission pin 4 side is used as an engagement structure between the transmission pin 4 and the pair of link plates 2 arranged on the left and right sides on both sides in the longitudinal direction of the chain belt 1. Although the projection 8 is engaged with the arcuate contact surface, although not illustrated, it may be configured such that one of them is an arcuate surface and the other is in contact with the arcuate surface. Further, one of the engagement groove 7 and the protrusion 8 is formed on the cam surface, and the relative bending curvature of the pair of link plates 2 arranged on the left and right sides adjacent to each other in the longitudinal direction of the chain belt 1 is changed. Accordingly, the contact point between the engagement groove 7 and the protrusion 8 may be changed to positively control the position of the transmission pin 4 in the inner and outer direction of the chain belt 1 (in the radial direction with respect to the pulley).

本実施形態においては、第１実施形態における効果（ア）〜（ウ）に加えて以下に記載した効果を奏することができる。 In the present embodiment, in addition to the effects (a) to (c) in the first embodiment, the following effects can be achieved.

（オ）伝達ピン４は、チェーンベルト１の長手方向両側で隣合って左右に配置される一対のリンクプレート２の少なくとも一方の端部と係合されてチェーンベルト１外径側への移動が拘束されることにより、プーリ１０への巻付き時に伝達ピン４に生ずる外径側への付勢力の少なくとも一部を、前記係合部を介してリンクプレート２の圧縮力に変換させることができ、当該圧縮力によりリンク張力を軽減乃至相殺させてリンクプレート２に生ずる応力を低減して、リンクプレート２の寿命を向上させることができ、また、チェーンベルト１のトルク容量を向上できる。 (E) The transmission pin 4 is engaged with at least one end portion of the pair of link plates 2 that are arranged adjacent to each other on both sides in the longitudinal direction of the chain belt 1 so as to move toward the outer diameter side of the chain belt 1. By being restrained, at least a part of the urging force on the outer diameter side generated in the transmission pin 4 when the pulley 10 is wound can be converted into the compressive force of the link plate 2 via the engaging portion. The link tension can be reduced or offset by the compression force to reduce the stress generated in the link plate 2, the life of the link plate 2 can be improved, and the torque capacity of the chain belt 1 can be improved.

（カ）前記伝達ピン４とチェーンベルト１の長手方向両側で隣り合って左右に配置される一対のリンクプレート２端部との係合は、左右ロッカピン３により関節運動する左右のリンクプレート２同士の相対曲げ曲率に応じて伝達ピン４のチェーンベルト１内外径方向の位置を変化させるものであることにより、伝達ピン４のプーリ１０に接触する半径方向位置を、駆動側プーリ１０と従動側プーリ１０との間の変速比により変化するプーリ１０への巻付き曲率に応じて追従させることができ、特定の変速比だけでなく全ての変速比で左右ロッカピン３と合わせて、接触ピッチの半減効果を得る３点接触とでき、チェーン騒音の低減を確実化できる。 (F) The engagement between the transmission pin 4 and the ends of the pair of link plates 2 arranged on the left and right sides adjacent to each other in the longitudinal direction of the chain belt 1 is performed between the left and right link plates 2 that are articulated by the left and right rocker pins 3. By changing the position of the transmission pin 4 in the inner and outer diameter directions of the chain belt 1 in accordance with the relative bending curvature of the driving pin 10 and the driven pulley, the radial position of the transmission pin 4 contacting the pulley 10 is changed. Can be followed according to the winding curvature of the pulley 10 that changes depending on the gear ratio between the two and the gear 10 and can be matched with the left and right rocker pins 3 not only at a specific gear ratio but also at all gear ratios. It is possible to obtain a three-point contact, and the reduction of chain noise can be ensured.

（キ）前記伝達ピン４とチェーンベルト１の長手方向両側で隣り合って左右に配置される一対のリンクプレート２端部との係合は、左右ロッカピン３により夫々関節運動する左右のリンクプレート２の端部における弧状突起がロッカピン３回りに回動する回動運動の一部を伝達ピン４のチェーンベルト１内外径方向の位置に変化させるものであることにより、伝達ピン４のチェーンベルト１内外径方向の位置制御を、部品点数を増加することなく実現でき、無段変速機の駆動システムの信頼性向上、コスト抑制に有利となる。 (G) The left and right link plates 2 that are jointed by the left and right rocker pins 3 are engaged with the ends of the pair of link plates 2 that are adjacent to each other on both sides in the longitudinal direction of the chain belt 1 and arranged on the left and right. By changing a part of the rotational movement in which the arc-shaped projection at the end of the shaft rotates about the rocker pin 3 to the position of the transmission pin 4 in the inner and outer diameter directions of the transmission pin 4, Radial position control can be realized without increasing the number of components, which is advantageous in improving the reliability of the continuously variable transmission drive system and in reducing costs.

（ク）図１４に示すように、伝達ピン４を左右のロッカピン３間に２個配置し、夫々対応する側の左右のリンクプレート２の端部と係合させてチェーンベルト１外径側への移動を拘束することにより、左右のロッカピン３と合わせて４点接触とでき、同じ接触ピッチであっても、リンクプレート２の長手方向寸法が長くなるため、リンクプレート２の枚数、ピン本数を削減できる効果がある。 (H) As shown in FIG. 14, two transmission pins 4 are arranged between the left and right rocker pins 3 and engaged with the ends of the left and right link plates 2 on the corresponding side, respectively, toward the outer diameter side of the chain belt 1. By restraining the movement of the left and right rocker pins 3, the four-point contact can be achieved, and even if the contact pitch is the same, the longitudinal dimension of the link plate 2 becomes longer, so the number of link plates 2 and the number of pins can be reduced. There is an effect that can be reduced.

本発明の一実施形態を示す無段変速機用チェーンベルトに使用するリンクプレートとロッカピンおよび伝達ピンの概略図。1 is a schematic view of a link plate, a rocker pin, and a transmission pin used in a continuously variable transmission chain belt showing an embodiment of the present invention. 同じく本実施形態のチェーンベルトの構成を示す部分正面図。The partial front view which similarly shows the structure of the chain belt of this embodiment. プーリに巻掛けられた状態の本実施形態のチェーンベルトを示す正面図。The front view which shows the chain belt of this embodiment of the state wound around the pulley. プーリへの巻掛けられた状態での変速状態を説明する断面図。Sectional drawing explaining the speed-change state in the state wound around the pulley. 図４に示すプーリとチェーンベルトとの接触状態を説明する説明図。Explanatory drawing explaining the contact state of the pulley and chain belt shown in FIG. 比較例のチェーンベルトを示す概略図。Schematic which shows the chain belt of a comparative example. 本実施形態のチェーンベルトにおける伝達駆動力変化を比較例と共に示す特性図。The characteristic view which shows the transmission drive force change in the chain belt of this embodiment with a comparative example. 本実施形態のチェーンベルトの第２実施例を示す概略図。Schematic which shows the 2nd Example of the chain belt of this embodiment. 本発明の第２実施形態を示す無段変速機用チェーンベルトの詳細を示す構成図。The block diagram which shows the detail of the chain belt for continuously variable transmission which shows 2nd Embodiment of this invention. 伝達ピンとリンクプレートとの関係を説明する説明図。Explanatory drawing explaining the relationship between a transmission pin and a link plate. 駆動プーリへの巻付き状態における変速比大の状態を示す説明図。Explanatory drawing which shows the state of the large gear ratio in the state wound around the drive pulley. 駆動プーリへの巻付き状態における変速比小の状態を示す説明図。Explanatory drawing which shows the state with a small gear ratio in the winding state to a drive pulley. リンクプレートに生ずる作用力を説明する説明図。Explanatory drawing explaining the action force which arises in a link plate. チェーンベルトの第２の実施例を示す説明図。Explanatory drawing which shows the 2nd Example of a chain belt.

Explanation of symbols

１チェーンベルト
２リンクプレート
３ロッカピン
４伝達ピン
５ピン係合部
６収容部（孔）
７係合溝
８弧状突起 DESCRIPTION OF SYMBOLS 1 Chain belt 2 Link plate 3 Rocker pin 4 Transmission pin 5 Pin engaging part 6 Storage part (hole)
7 Engaging groove 8 Arc-shaped protrusion

Claims

A first link plate in which a plurality of flat plates are laminated in the thickness direction;
Second and third link plates arranged on the both sides in the longitudinal direction of the first link plate by laminating a plurality of plate-like plates in the thickness direction and overlapping the first link plate and the end portions thereof ,
First and second pins connecting the first link plate and the second and third link plates, which are overlapped with each other, through each other in the thickness direction;
A third pin disposed between the second link plate and the third link plate in a thickness direction through the first link plate and disposed in parallel with the first pin and the second pin; An endless chain belt characterized by a plurality of links in the direction.

A plurality of link plates having pin engagement portions at both ends, and rocker pins that engage with the engagement portions of the link plates and connect the link plates so that they can be articulated; In the chain belt for continuously variable transmission in which the plurality of link plates are connected endlessly,
A transmission pin housing portion is provided between the pin engaging portions of the link plate, the transmission pin housing portion is penetrated and the transmission pin is arranged in parallel with the rocker pin,
A first contact point is configured by frictionally contacting both end surfaces of the rocker pin with a V-type pulley, and a second contact point is configured by frictionally contacting both end surfaces of the transmission pin with the V-type pulley. And chain belt.

The third pin or the transmission pin is engaged with at least one end portion of the second, third link plate or the pair of link plates arranged adjacent to each other on both sides in the longitudinal direction of the chain belt, and the outer diameter of the chain belt. The chain belt according to claim 1, wherein movement toward the side is restricted.

The engagement between the third pin or the transmission pin and the ends of the second and third link plates or the pair of link plates that are arranged adjacent to each other on both sides in the longitudinal direction of the chain belt is the first, second pins, or left and right 4. The chain belt according to claim 3, wherein the position of the third pin or the transmission pin in the inner and outer diameter direction of the chain belt is changed in accordance with the relative bending curvature between the left and right link plates that are articulated by the rocker pin.

The engagement between the third pin or the transmission pin and the ends of the second and third link plates or the pair of link plates that are arranged adjacent to each other on both sides in the longitudinal direction of the chain belt is the first, second pins, or left and right A part of the rotational movement in which the arc-shaped projections at the ends of the left and right link plates that are jointly moved by the rocker pins rotate around the rocker pins is changed to the position of the third pin or the transmission pin in the inner and outer radial directions of the chain belt. The chain belt according to claim 3 or 4, wherein the chain belt is provided.

The third pin or the transmission pin is arranged so as to be deviated in any one of the longitudinal directions of the chain belt from an intermediate position between the first and second pins or the left and right rocker pins. Item 6. The chain belt according to any one of Items 5.

Two third pins or transmission pins are arranged between the first and second pins or the left and right rocker pins, and are engaged with the end portions of the corresponding second and third link plates or left and right link plates, respectively. The chain belt according to any one of claims 3 to 6, wherein movement toward the outer diameter side of the chain belt is restricted.

The chain belt according to any one of claims 1 to 5, wherein the third pin or the transmission pin is disposed at an intermediate position between the first and second pins or the left and right rocker pins.

The chain belt according to claim 1 or 2, wherein the third pin or the transmission pin is restrained from moving toward the outer diameter side of the chain belt by a transmission pin housing portion of a link plate through which the third pin or the transmission pin passes. .

The said 3rd pin or a transmission pin is offset and arrange | positioned from the plane formed by the 1st, 2nd pin or the left and right rocker pins to the outer diameter side of the chain belt. Chain belt.

A plurality of link plates each having a pin engaging portion at both ends and a transmission pin accommodating portion between the pin engaging portions, a rocker pin for connecting the link plates so as to be capable of articulation, and a transmission disposed between the rocker pins And a chain belt that is arranged in parallel with the rocker pin through the transmission pin housing portion of the link plate, and the link plates are connected endlessly with the rocker pin.
A V-shaped pulley having a V-groove surface having a V-shaped cross section, which is disposed on each of the parallel drive shaft and the driven shaft,
The chain belt is stretched between the pulleys, and a V-type pulley is formed by a first contact point caused by frictional contact between both end surfaces of the rocker pin and a second contact point caused by frictional contact between both end surfaces of the transmission pin. Configured to contact the V groove surface of
A belt-type continuously variable transmission that transmits and transmits rotational power steplessly by changing the V groove widths of the two pulleys while being associated with each other on the driving side and the driven side.

The transmission pin is engaged with at least one end portion of a pair of link plates that are adjacent to each other on both sides in the longitudinal direction of the chain belt and is restrained from moving toward the outer side of the chain belt. The belt-type continuously variable transmission according to claim 11.

The engagement between the transmission pin and the pair of link plate ends arranged on the left and right sides adjacent to each other in the longitudinal direction of the chain belt is performed between the left and right link plates that are jointed by the left and right rocker pins when wound around the V-type pulley. The belt-type continuously variable transmission according to claim 11, wherein the position of the transmission pin in the inner and outer diameter direction of the chain belt is changed according to the relative bending curvature.

The engagement between the transmission pin and the pair of link plate ends arranged on the left and right sides adjacent to each other in the longitudinal direction of the chain belt is such that the arc-shaped projections at the ends of the left and right link plates that are articulated by the left and right rocker pins are around the rocker pins. The belt-type continuously variable transmission according to claim 12 or 13, wherein a part of the rotating motion is changed to a position of the transmission pin in the inner and outer diameter direction of the chain belt.

The transmission pin is disposed between two rocker pins on the left and right sides, and engages with the ends of the left and right link plates on the corresponding side to restrict movement to the outer side of the chain belt. The belt type continuously variable transmission according to any one of claims 12 to 14.

The belt-type continuously variable transmission according to any one of claims 11 to 14, wherein the transmission pin is disposed at an intermediate position between the left and right rocker pins.

The belt-type continuously variable transmission according to claim 11, wherein movement of the transmission pin toward the outer diameter side of the chain belt is restricted by a transmission pin housing portion of the link plate through which the transmission pin passes.