JP6269461B2 - Transmission belt - Google Patents

Transmission belt Download PDF

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JP6269461B2
JP6269461B2 JP2014251307A JP2014251307A JP6269461B2 JP 6269461 B2 JP6269461 B2 JP 6269461B2 JP 2014251307 A JP2014251307 A JP 2014251307A JP 2014251307 A JP2014251307 A JP 2014251307A JP 6269461 B2 JP6269461 B2 JP 6269461B2
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edge
transmission belt
saddle
pulley
ring
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JP2016114106A (en
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小林　大介
大介 小林
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Toyota Motor Corp
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Toyota Motor Corp
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Description

本発明は、伝動ベルトに関し、とりわけ、エレメントのサドル面の加工コストの増大を抑制しつつ、伝動ベルトの伝達効率を向上させる技術に関する。   The present invention relates to a transmission belt, and more particularly to a technique for improving transmission efficiency of a transmission belt while suppressing an increase in processing cost of a saddle surface of an element.

板状に形成されて互いに対向して環状に配列される多数のエレメントに、無端環状のリングが巻き掛けられて前記エレメントが環状に結束されるとともに、前記エレメントの配列方向での一方の側面に、前記エレメントが円弧状に湾曲した配列状態となった場合に隣接する他のエレメントに接触して相対回動の中心となるロッキングエッジが形成された伝動ベルトが知られている。たとえば、特許文献１に示される伝動ベルトがそれである。   An endless annular ring is wound around a large number of elements that are formed in a plate shape and are arranged in an annular shape facing each other, and the elements are bound in an annular shape, and on one side surface in the arrangement direction of the elements There is known a transmission belt in which when the elements are arranged in an arcuate shape, a locking edge is formed which comes into contact with another adjacent element and becomes the center of relative rotation. For example, this is the power transmission belt disclosed in Patent Document 1.

図９は、このような従来の伝動ベルト１１０の一例であり、環状に配列された各エレメント１１２のその一部を切り欠いて示す側面図である。従来の伝動ベルト１１０のエレメント１１２は、フープ１１３の最内周に位置させられるリング１１４の内周面に押圧されるサドル面１１６を有するとともに、伝動ベルト１１０が巻き掛けられるプーリのシーブ面に接触する接触面１１８を両側に有する本体部１２０を備えている。また、エレメント１１２の本体部１２０と頭部１２２との間には、フープ１１３を収容するための上記シーブ面側に開口するように設けられた一対の凹溝１２４が設けられている。エレメント１１２は、鋼板がプレス成形により打ち抜かれて形成される。   FIG. 9 is an example of such a conventional transmission belt 110, and is a side view showing a part of each of the elements 112 arranged in an annular shape. The element 112 of the conventional transmission belt 110 has a saddle surface 116 that is pressed against the inner peripheral surface of the ring 114 positioned at the innermost periphery of the hoop 113, and contacts the sheave surface of the pulley around which the transmission belt 110 is wound. A main body 120 having contact surfaces 118 on both sides. Further, between the main body 120 and the head 122 of the element 112, a pair of concave grooves 124 provided to open to the sheave surface side for housing the hoop 113 is provided. The element 112 is formed by punching a steel plate by press forming.

図１０は、エレメント１１２のプレス成形工程の一例を示す模式図である。材料としての鋼版がプレス加工機のダイとパンチとの間に図１０のように設置されて、パンチ側から矢印方向へ力が加えられると、成形品としてのエレメント１１２の厚み方向のせん断面には、せん断によるバリ１２５と、せん断開始前に切刃により鋼板が圧下されることによるダレ１２６が発生する。図９のエレメント１１２の本体部１２０の厚み方向の一方の側面はダレ１２６がサドル面１１６の一端に形成されたダレ面１２７であり、他方の側面は破線の円内に示されるようにバリ１２５がサドル面１１６の他端に形成された側のエッジ面１２８であり、プーリに巻き掛けられる際に隣接するエレメント１１２と接触するロッキングエッジ１３０がダレ面１２７に形成されている。そして、隣接するエレメント１１２のうち、一のエレメント１１２のロッキングエッジ１３０が形成されたダレ面１２７と他のエレメント１１２のバリ１２５が形成されたエッジ面１２８とが対向するように複数のエレメント１１２が環状に連ねられることにより伝動ベルト１１０が構成される。   FIG. 10 is a schematic diagram showing an example of the press molding process of the element 112. When a steel plate as a material is installed between a die and a punch of a press machine as shown in FIG. 10 and a force is applied in the direction of the arrow from the punch side, the shear surface in the thickness direction of the element 112 as a molded product In this case, a burr 125 due to shearing and a sagging 126 due to the steel plate being squeezed by the cutting blade before the start of shearing are generated. One side surface in the thickness direction of the main body 120 of the element 112 of FIG. 9 is a sag surface 127 in which a sag 126 is formed at one end of the saddle surface 116, and the other side surface is a burr 125 as shown in a broken-line circle. Is a side edge surface 128 formed on the other end of the saddle surface 116, and a locking edge 130 is formed on the sag surface 127 that comes into contact with the adjacent element 112 when wound around the pulley. Among the adjacent elements 112, the plurality of elements 112 are arranged such that the sag surface 127 where the locking edge 130 of one element 112 is formed and the edge surface 128 where the burr 125 of another element 112 is formed face each other. The transmission belt 110 is configured by being linked in an annular shape.

特開２００８−３０３９５０号公報JP 2008-303950 A

図９の従来の伝動ベルト１１０は、図９の破線の円で示されるように、本体部１２０のサドル面１１６に形成されたバリ１２５と最内周のリング１１４がエッジ当たりして、サドル面１１６とリング１１４との間の摩擦係数が増大し、伝動ベルト１１０の伝達効率が低下する可能性があった。これに対し、サドル面１１６に形成されたバリをたとえばバレル研磨により除去することにより、サドル面とリングとの間に生じる接触荷重を低減することができるが、エレメントの加工コストが増大するという問題があった。   The conventional transmission belt 110 in FIG. 9 has a saddle surface as shown by the broken circle in FIG. 9 where the burr 125 and the innermost ring 114 formed on the saddle surface 116 of the main body 120 abut against the edge. The friction coefficient between the ring 116 and the ring 114 may increase, and the transmission efficiency of the transmission belt 110 may decrease. On the other hand, by removing the burr formed on the saddle surface 116 by barrel polishing, for example, the contact load generated between the saddle surface and the ring can be reduced, but the processing cost of the element increases. was there.

本発明は、以上の事情を背景として為されたものであり、その目的とするところは、エレメントの加工コストの増大を抑制しつつ、伝達効率の高い伝動ベルトを提供することにある。   The present invention has been made against the background of the above circumstances, and an object of the present invention is to provide a transmission belt having high transmission efficiency while suppressing an increase in processing cost of an element.

上記目的を達成するための本発明の要旨とするところは、厚み方向に連ねられて環状に配列される複数のエレメントが、無端環状のリングにより環状に結束されるとともに、前記エレメントの配列方向での一方の側面に、隣接する他のエレメントに接触して相対回動の中心となるロッキングエッジが形成された伝動ベルトにおいて、前記一方の側面を、前記エレメントをプレス加工により成形する際にダレが発生する側のダレ面とし、前記エレメントの前記一方の側面とは反対側の他方の側面を、前記エレメントをプレス加工により成形する際にバリが発生する側のエッジ面とし、前記伝動ベルトの進行方向における前面をダレ面、後面をエッジ面として成形した第１エレメントと、前記伝動ベルトの進行方向における前面をエッジ面、後面をダレ面として成形した第２エレメントとを、前記第１エレメントのエッジ面と前記第２エレメントのエッジ面とが対向するように交互に配置したことにある。 In order to achieve the above object, the gist of the present invention is that a plurality of elements connected in a ring shape and arranged in a ring shape are bundled in a ring shape by an endless ring, and in the arrangement direction of the elements. In a transmission belt in which a locking edge that is in contact with another adjacent element and becomes the center of relative rotation is formed on one side surface of the first side surface, when the one side surface is formed by pressing, the sagging is not caused. The sag surface on the side to be generated and the other side surface opposite to the one side surface of the element as an edge surface on the side where burrs are generated when the element is formed by press working, the progress of the transmission belt A first element formed with a front surface in a direction as a sag surface and a rear surface as an edge surface, and a front surface in the traveling direction of the transmission belt as an edge surface and a rear surface And a second element that is shaped as a sagging surface, edge surfaces of the first element and said edge surface of the second element is in that arranged alternately so as to face.

本発明の伝動ベルトによれば、前記一方の側面を、前記エレメントをプレス加工により成形する際にダレが発生する側のダレ面とし、前記エレメントの前記一方の側面とは反対側の他方の側面を、前記エレメントをプレス加工により成形する際にバリが発生する側のエッジ面とし、前記伝動ベルトの進行方向における前面をダレ面、後面をエッジ面として成形した第１エレメントと、前記伝動ベルトの進行方向における前面をエッジ面、後面をダレ面として成形した第２エレメントとを、前記第１エレメントのエッジ面と前記第２エレメントのエッジ面とが対向するように交互に配置するため、前記エレメントが伝動ベルトのプーリに巻き掛けられた部分に位置する際、第１エレメントと第２エレメントとのエッジ面同士が密着し合うとともに、進行方向の両面においてダレ面が配置され、最内周側のリングは、第１エレメントのダレ面側および第２エレメントのダレ面側により接触する。これにより、エレメントが伝動ベルトのプーリに巻き掛けられた部分に位置する際に、エレメントと最内周面のリングとのエッジ当たりが抑制されて、エレメントとリングとの間の接触荷重が低減し、エレメントとリングとの間の摩擦の摩擦係数が低減されることから、伝動ベルトの伝達効率が向上する。また、第１エレメントと第２エレメントとのエッジ面同士の密着により、エッジ面に発生したバリの加工が必要ないため、エレメントの加工コストの増大を抑制することができる。 According to the transmission belt of the present invention, the one side surface is a sagging surface on the side where sagging occurs when the element is formed by press working, and the other side surface of the element is opposite to the one side surface. A first element formed with the front surface in the traveling direction of the transmission belt as a sag surface and the rear surface as an edge surface, and the transmission belt The second element formed with the front surface in the traveling direction as an edge surface and the rear surface as a sag surface is alternately arranged so that the edge surface of the first element and the edge surface of the second element face each other. Is positioned at the portion of the transmission belt that is wound around the pulley, the edge surfaces of the first element and the second element are in close contact with each other. , Sagging surface is arranged both in the traveling direction, the ring of the innermost contacts the sagging side of the sagging side and the second element of the first element. As a result, when the element is located at the portion of the transmission belt that is wound around the pulley, the contact between the element and the innermost ring is suppressed, and the contact load between the element and the ring is reduced. Since the friction coefficient of the friction between the element and the ring is reduced, the transmission efficiency of the transmission belt is improved. Further, due to the close contact between the edge surfaces of the first element and the second element, it is not necessary to process the burrs generated on the edge surface, so that an increase in the processing cost of the element can be suppressed.

本発明が適用されるベルト式無段変速機の一例を示す斜視図である。It is a perspective view showing an example of a belt type continuously variable transmission to which the present invention is applied. 図１のベルト式無段変速機のプーリに巻き掛けられた伝動ベルトのシーブ面に接触した状態のエレメントをその一部を切り欠いて示す側面図である。FIG. 2 is a side view showing a part of the element in a state of being in contact with a sheave surface of a transmission belt wound around a pulley of the belt type continuously variable transmission of FIG. 1. 図２のエレメントを構成する第１エレメントの進行方向における前方の正面図である。FIG. 3 is a front view of the front of the first element constituting the element of FIG. 2 in the traveling direction. 図３の第１エレメントの一部を切り欠いて示す側面図である。FIG. 4 is a side view showing a part of the first element of FIG. 図２のエレメントを構成する第２エレメントの進行方向における前方の正面図である。FIG. 3 is a front view in front of a second element constituting the element of FIG. 2 in the traveling direction. 図５の第２エレメントの一部を切り欠いて示す側面図である。It is a side view which notches and shows a part of 2nd element of FIG. 図１の伝動ベルト（ＣＶＴベルト）のエレメントとフープとの相対滑りによりサドル面と最内周側のリングとの間の接触部分で生じる摩擦の摩擦係数を説明するストライベック線図である。FIG. 2 is a Stribeck diagram illustrating a friction coefficient of friction generated in a contact portion between a saddle surface and an innermost ring due to relative sliding between an element of the transmission belt (CVT belt) and the hoop in FIG. 1. 図２のエレメントの挟み角を狭くする狭角化とエレメントのリングとの間の接触荷重との間の関係を説明する模式図である。It is a schematic diagram explaining the relationship between the narrowing which narrows the clamping angle of the element of FIG. 2, and the contact load between the rings of an element. 従来のベルト式無段変速機のプーリに巻き掛けられた伝動ベルトのシーブ面に接触した状態のエレメントをその一部を切り欠いて示す側面図である。It is a side view which cuts out the element in the state which contacted the sheave surface of the transmission belt wound around the pulley of the conventional belt-type continuously variable transmission. エレメントのプレス成形工程の一例を示す模式図である。It is a schematic diagram which shows an example of the press molding process of an element.

以下、本発明の伝動ベルトの一実施例について図面を参照して詳細に説明する。   Hereinafter, an embodiment of a transmission belt according to the present invention will be described in detail with reference to the drawings.

図１は、伝動ベルト１０が適用された車両用ベルト式無段変速機１２を示す斜視図である。ベルト式無段変速機１２は、溝幅が可変であるＶ溝１４を外周部に有して互いに平行な軸心まわりに回転可能に設けられた一対のプーリ１６およびプーリ１８を備えており、それ等のプーリ１６およびプーリ１８に跨って伝動ベルト１０（ＣＶＴベルト１０）が巻き掛けられている。プーリ１６およびプーリ１８は、それぞれ回転軸２０および回転軸２２に固定された固定回転体１６ａ、固定回転体１８ａと回転軸に対して軸方向に相対移動可能に設けられた可動回転体１６ｂ、可動回転体１８ｂとを備えている。これら固定回転体１６ａと可動回転体１６ｂとの互いに対向する面、および固定回転体１８ａと可動回転体１８ｂとの互いに対向する面には、径方向外側に向かうにしたがって軸方向の相対距離が大きくなる円錐状のシーブ面２４がそれぞれ設けられている。上記Ｖ溝は、これら一対の互いに対向するシーブ面２４により形成されている。   FIG. 1 is a perspective view showing a vehicle belt type continuously variable transmission 12 to which a transmission belt 10 is applied. The belt-type continuously variable transmission 12 includes a pair of pulleys 16 and 18 that have a V-groove 14 with a variable groove width on the outer peripheral portion and are provided to be rotatable around mutually parallel axes. A transmission belt 10 (CVT belt 10) is wound around the pulley 16 and the pulley 18. The pulley 16 and the pulley 18 are respectively a fixed rotating body 16a fixed to the rotating shaft 20 and the rotating shaft 22, a movable rotating body 16b provided to be movable relative to the fixed rotating body 18a and the rotating shaft in the axial direction, and movable. And a rotating body 18b. The axial relative distances of the fixed rotating body 16a and the movable rotating body 16b that face each other, and the fixed rotating body 18a and the movable rotating body 18b that face each other, increase in the axial direction toward the radially outer side. Conical sheave surfaces 24 are provided. The V-groove is formed by the pair of sheave surfaces 24 facing each other.

図２は、ベルト式無段変速機１２の伝動ベルト１０のプーリ１６に巻き掛けられた部分のシーブ面２４に接触した状態のエレメント３０をその一部を切り欠いて示す側面図である。伝動ベルト１０は、可撓性を有する薄板帯状のリング２６が複数重ね合わされた無端環状の一対のフープ２８と、それら一対のフープ２８によって支持されるとともにそれら一対のフープ２８に沿って厚さ方向に環状に連ねられた板状の金属から成る複数のエレメント３０とを備えている。リング２６は、たとえば厚さ０．２ｍｍ程度の高張力鋼板が輪状とされたもので、内から外へたとえば７層から９層程度層状に重ねられている。エレメント３０は、たとえば厚さ１．８ｍｍ程度の鋼板が打ち抜かれて成形された厚肉板状片で、本実施例ではたとえば２００個程度備えられている。エレメント３０は、プーリ１６およびプーリ１８に巻き掛けられて円弧状に湾曲した状態となる場合に隣接する他のエレメント３０に接触するロッキングエッジ３２およびロッキングエッジ３３が、伝動ベルト１０の周方向への回転による矢印で示される進行方向の前面と後面の両面に形成されるように、一対の第１エレメント３４と第２エレメント３６とが重ね合わされることにより構成されている。   FIG. 2 is a side view showing a part of the element 30 in a state where the element 30 is in contact with the sheave surface 24 of the portion of the transmission belt 10 wound around the pulley 16 of the belt-type continuously variable transmission 12. The transmission belt 10 is supported by the pair of endless annular hoops 28 in which a plurality of thin strip-like rings 26 having flexibility are overlapped, and the pair of hoops 28, and along the pair of hoops 28 in the thickness direction. And a plurality of elements 30 made of plate-like metal linked in a ring shape. The ring 26 is a high-strength steel plate having a thickness of about 0.2 mm, for example, and is stacked in layers from the inside to the outside, for example, about 7 to 9 layers. The element 30 is a thick plate-like piece formed by punching a steel plate having a thickness of about 1.8 mm, for example, and is provided with about 200 in this embodiment. When the element 30 is wound around the pulley 16 and the pulley 18 to be curved in an arc shape, the locking edge 32 and the locking edge 33 that come into contact with other adjacent elements 30 are arranged in the circumferential direction of the transmission belt 10. A pair of the first element 34 and the second element 36 are overlapped so as to be formed on both the front surface and the rear surface in the advancing direction indicated by arrows by rotation.

図３は、第１エレメント３４の進行方向の前面である正面図であり、図４は、第１エレメント３４の側面図である。第１エレメント３４は、一対のシーブ面２４にそれぞれ対向しつつ接触する一対の接触面３８を幅方向の両側に備える本体部４０と、進行方向前方の隣接する第２エレメント３６に係合する係合突起４２と、進行方向後方の隣接する第２エレメント３６に係合される係合穴４４とを有する頭部４６と、幅方向の両側に開口するように頭部４６と本体部４０との間に対称的に形成され、多数のエレメント３０を環状に連ねた状態で支持する一対のフープ２８が収容される一対の凹溝４８と、を備えている。また、第１エレメント３４は、プーリ１６およびプーリ１８に巻き掛けられた部分に位置され、接触面３８がシーブ面２４に接触させられると、張力によってフープ２８に押圧される凹溝４８を構成する本体部４０の外向きの壁面であるサドル面５０を備えている。第１エレメント３４の進行方向であり厚み方向の側面は、係合突起４２が形成された側の面である進行方向の前面がプレス加工により形成される際にダレが発生した側の面であるダレ面５２とされ、係合穴４４が形成された側の面である進行方向の後面はプレス加工により形成される際にバリが発生し、サドル面５０との間でエッジＥが形成されたエッジ面５４とされている。本体部４０には、エレメント３０の高さ方向すなわち図４における上下方向においてサドル面５０から距離Ｄだけ下方の位置から頭部４６とは離れる側へ向かうに従い厚みが小さくされるように、ダレ面５２がエッジ面５４へ接近させられており、上記本体部４０のサドル面５０から距離Ｄだけ下方の位置において幅方向に、隣接する他のエレメントに接触して相対回動の中心となるロッキングエッジ３２が形成されている。   FIG. 3 is a front view showing the front surface of the first element 34 in the traveling direction, and FIG. 4 is a side view of the first element 34. The first element 34 is engaged with a main body portion 40 provided with a pair of contact surfaces 38 on both sides in the width direction, and a second element 36 adjacent to the front in the traveling direction. A head 46 having a mating protrusion 42 and an engagement hole 44 engaged with the adjacent second element 36 at the rear in the traveling direction, and the head 46 and the main body 40 so as to open on both sides in the width direction. And a pair of concave grooves 48 that house a pair of hoops 28 that are formed symmetrically between them and support a large number of elements 30 connected in a ring shape. The first element 34 is positioned at a portion wound around the pulley 16 and the pulley 18, and constitutes a concave groove 48 that is pressed against the hoop 28 by tension when the contact surface 38 is brought into contact with the sheave surface 24. A saddle surface 50 which is an outward wall surface of the main body 40 is provided. The side surface in the thickness direction, which is the traveling direction of the first element 34, is the surface on the side where sagging occurs when the front surface in the traveling direction, which is the surface on the side on which the engagement protrusions 42 are formed, is formed by pressing. The rear surface in the advancing direction, which is the side on which the engagement hole 44 is formed, is a sag surface 52, and burrs are generated when it is formed by pressing, and an edge E is formed with the saddle surface 50. An edge surface 54 is provided. The body portion 40 has a sagging surface so that the thickness is reduced from the position below the saddle surface 50 by a distance D in the height direction of the element 30, that is, in the vertical direction in FIG. 52 is brought close to the edge surface 54, and in the width direction at a position below the saddle surface 50 of the main body 40, in the width direction, a rocking edge that contacts another adjacent element and becomes the center of relative rotation 32 is formed.

図５は、第２エレメント３６の進行方向の前面である正面図であり、図６は、第２エレメント３６の側面図である。第２エレメント３６は、一対のシーブ面２４にそれぞれ対向しつつ接触する一対の接触面５６を幅方向の両側に備える本体部５８と、進行方向前方の隣接する第１エレメント３４の係合穴４４に係合する係合突起６０と、進行方向後方の隣接する第１エレメント３４の係合突起４２に係合される係合穴６２とを有する頭部６４と、幅方向の両側に開口するように頭部６４と本体部５８との間に対称的に形成され、多数のエレメント３０を環状に連ねた状態で支持する一対のフープ２８が収容される一対の凹溝６６と、を備えている。また、第２エレメント３６は、プーリ１６およびプーリ１８に巻き掛けられた部分に位置され、接触面５６がシーブ面２４に接触させられると、張力によってフープ２８に押圧される凹溝６６を構成する本体部５８の外向きの壁面であるサドル面６８を備えている。第２エレメント３６の進行方向であり厚み方向の側面は、係合穴６２が形成された側の面である進行方向の後面がプレス加工により形成される際にダレが発生した側の面であるダレ面７０とされ、係合突起６０が形成された側の面である進行方向の前面はプレス加工により形成される際にバリが発生し、サドル面６８との間でエッジＥが形成されたエッジ面７２とされている。本体部５８には、エレメント３０の高さ方向すなわち図６における上下方向においてサドル面６８から距離Ｄだけ下方の位置から頭部６４とは離れる側へ向かうに従い厚みが小さくされるように、ダレ面７０がエッジ面７２へ接近させられており、上記本体部５８のサドル面６８から距離Ｄだけ下方の位置において幅方向に、隣接する他のエレメントに接触して相対回動の中心となるロッキングエッジ３３が形成されている。   FIG. 5 is a front view showing the front surface of the second element 36 in the traveling direction, and FIG. 6 is a side view of the second element 36. The second element 36 includes a main body 58 provided with a pair of contact surfaces 56 on both sides in the width direction, which are in contact with each other while facing the pair of sheave surfaces 24, and an engagement hole 44 of the adjacent first element 34 in the forward direction. A head 64 having an engagement protrusion 60 that engages with the engagement protrusion 42 of the first element 34 adjacent to the rear in the traveling direction, and an opening on both sides in the width direction. And a pair of concave grooves 66 that are formed symmetrically between the head portion 64 and the main body portion 58 and accommodate a pair of hoops 28 that support a large number of elements 30 connected in a ring shape. . The second element 36 is positioned at a portion wound around the pulley 16 and the pulley 18, and constitutes a concave groove 66 that is pressed against the hoop 28 by tension when the contact surface 56 is brought into contact with the sheave surface 24. A saddle surface 68 which is an outward wall surface of the main body portion 58 is provided. The side surface in the thickness direction of the second element 36 is the surface on which the sagging occurs when the rear surface in the direction of travel, which is the surface on the side where the engagement holes 62 are formed, is formed by pressing. The front surface in the advancing direction, which is the side on which the engagement protrusion 60 is formed, is a sag surface 70, and burrs are generated when it is formed by pressing, and an edge E is formed between the saddle surface 68 and the saddle surface 68. An edge surface 72 is provided. The main body 58 has a sagging surface so that the thickness is reduced from the position below the saddle surface 68 by a distance D in the height direction of the element 30, that is, in the vertical direction in FIG. 70 is brought close to the edge surface 72, and in the width direction at a position lower than the saddle surface 68 of the main body portion 58 in the width direction, it is a rocking edge that contacts other adjacent elements and becomes the center of relative rotation 33 is formed.

図２に示されるように、伝動ベルト１０は、第１エレメント３４の進行方向後面のエッジ面５４と第２エレメント３６の進行方向前面のエッジ面７２とが対向させられ、第２エレメント３６の進行方向後面のダレ面７０と第１エレメント３４の進行方向前面のダレ面５２とが対向させられるように、第１エレメント３４と第２エレメント３６とが交互に配列させられ、第１エレメント３４の凹溝４８と第２エレメント３６の凹溝６６にフープ２８が巻き掛けられて環状に結束させられることにより構成される。エッジ面５４とエッジ面７２とが互いに対向する第１エレメント３４および第２エレメント３６は、エッジ面５４とエッジ面７２とにおいて密着させられ、プーリ１６およびプーリ１８に巻き掛けられた部分に位置され、張力によってフープ２８が本体部４０のサドル面５０および本体部５８のサドル面６８に押圧された状態では、エッジ面５４とエッジ面７２との密着が維持されつつ、第１エレメント３４の進行方向前方の第２エレメント３６のダレ面７０と第１エレメント３４のロッキングエッジ３２とが、第２エレメント３６の進行方向後方の第１エレメント３４のダレ面５２と第２エレメント３６のロッキングエッジ３３とがそれぞれ接触されつつ相対回転可能であり、進行方向において前面と後面の両面にロッキングエッジ３２およびロッキングエッジ３３が形成された１つのエレメントとして機能するエレメント３０を構成する。このエレメント３０は、エッジ面５４とエッジ面７２とが密着されて第１エレメント３４のエッジと第２エレメント３６のエッジとが重ねられることによりエッジが消滅しているため、プーリ１６およびプーリ１８に巻き掛けられた部分に位置された際には、フープ２８の最内周側のリング２６が破線の円内に示されるように進行方向両面に位置されるダレ面５２側のサドル面５０およびダレ面７０側のサドル面６８に潤滑油を介して接触される。これにより、エレメントのサドル面のエッジがフープの最内周側のリングにエッジ当たりする場合と比較して、サドル面５０およびサドル面６８と最内周側のリング２６との間の接触荷重、およびリング２６にかかる面圧が大きく減少されている。これにより、エレメント３０が伝動ベルト１０の特に有効径が小径側プーリに巻き掛けられた際にサドル面５０およびサドル面６８と最内周側のリング２６との間の接触荷重がエッジ当たりする場合よりも小さいため、サドル面５０およびサドル面６８と最内周側のリング２６との間の摩擦における摩擦係数が低下されている。   As shown in FIG. 2, in the transmission belt 10, the edge surface 54 on the rear surface in the traveling direction of the first element 34 and the edge surface 72 on the front surface in the traveling direction of the second element 36 are opposed to each other. The first element 34 and the second element 36 are alternately arranged so that the sag surface 70 on the rear side in the direction and the sag surface 52 on the front surface in the traveling direction of the first element 34 are opposed to each other. The hoop 28 is wound around the groove 48 and the concave groove 66 of the second element 36, and is formed into an annular shape. The first element 34 and the second element 36 in which the edge surface 54 and the edge surface 72 are opposed to each other are in close contact with each other on the edge surface 54 and the edge surface 72, and are positioned in a portion wound around the pulley 16 and the pulley 18. In the state where the hoop 28 is pressed against the saddle surface 50 of the main body 40 and the saddle surface 68 of the main body 58 by tension, the direction of travel of the first element 34 is maintained while maintaining the close contact between the edge surface 54 and the edge surface 72. The sag surface 70 of the second element 36 at the front and the locking edge 32 of the first element 34, and the sag surface 52 of the first element 34 at the rear of the second element 36 in the traveling direction and the locking edge 33 of the second element 36 are They can rotate relative to each other while being in contact with each other. Constituting the element 30 that serves as one of the elements finely rocking edge 33 is formed. In this element 30, the edge surface 54 and the edge surface 72 are brought into close contact with each other, and the edge of the first element 34 and the edge of the second element 36 are overlapped. When positioned on the wound portion, the innermost ring 26 of the hoop 28 has a saddle surface 50 and a sag surface 50 on the sag surface 52 side that are positioned on both sides of the traveling direction as shown in the broken circle. The saddle surface 68 on the surface 70 side is brought into contact with the lubricating oil. Thereby, the contact load between the saddle surface 50 and the saddle surface 68 and the innermost ring 26 is compared with the case where the edge of the saddle surface of the element hits the innermost ring on the hoop. The surface pressure applied to the ring 26 is greatly reduced. As a result, when the element 30 is wound around the pulley having a particularly small effective diameter of the transmission belt 10, the contact load between the saddle surface 50 and the saddle surface 68 and the innermost ring 26 hits the edge. Therefore, the friction coefficient in the friction between the saddle surface 50 and the saddle surface 68 and the innermost ring 26 is reduced.

ところで、第１エレメント３４のロッキングエッジ３２はサドル面５０から距離Ｄだけ下方の位置に形成され、および第２エレメント３６のロッキングエッジ３３は、第２エレメント３６のサドル面６８から距離Ｄだけ下方の位置に形成されているため、エレメント３０が伝動ベルト１０のプーリ１６およびプーリ１８のうちの特に有効径が小径側のプーリに巻き掛けられた際、エレメント３０とフープ２８との間で相対滑りが発生し、エレメント３０の第１エレメント３４のサドル面５０および第２エレメント３６のサドル面６８と最内周側のリング２６との間の接触部分で摩擦が生じる。   Incidentally, the locking edge 32 of the first element 34 is formed at a position below the saddle surface 50 by a distance D, and the locking edge 33 of the second element 36 is below the saddle surface 68 of the second element 36 by a distance D. Therefore, when the element 30 is wound around the pulley 16 and the pulley 18 of the transmission belt 10, particularly when the effective diameter is wound around the pulley on the small diameter side, relative slip occurs between the element 30 and the hoop 28. Friction occurs at the contact portion between the saddle surface 50 of the first element 34 and the saddle surface 68 of the second element 36 and the innermost ring 26 of the element 30.

図７は、車両用ベルト式無段変速機１２の伝動ベルト１０（ＣＶＴベルト）のエレメント３０とフープ２８との相対滑りによりサドル面５０およびサドル面６８と最内周側のリング２６との間の接触部分で生じる摩擦の摩擦係数を説明するストライベック線図である。伝動ベルト１０の第１エレメント３４のサドル面５０および第２エレメント３６のサドル面６８とフープ２８の最内周のリング２６との接触部分に生じる摩擦は、サドル面５０およびサドル面６８と最内周側のリング２６との間に作用する接触荷重、エレメント３０とフープ２８との間の相対滑りによるサドル面５０およびサドル面６８の最内周側のリング２６に対する相対速度および潤滑油の粘度から、ストライベック線図上の流体潤滑領域と境界潤滑領域との間の破線で示される混合潤滑領域の摩擦となるように設定される。   FIG. 7 shows the saddle surface 50 and the saddle surface 68 between the innermost ring 26 and the saddle surface 50 due to relative sliding between the element 30 of the transmission belt 10 (CVT belt) of the vehicle belt type continuously variable transmission 12 and the hoop 28. It is a Stribeck diagram explaining the friction coefficient of the friction which arises in the contact part. The friction generated at the contact portion between the saddle surface 50 of the first element 34 and the saddle surface 68 of the second element 36 and the innermost ring 26 of the hoop 28 of the transmission belt 10 is the innermost contact with the saddle surface 50 and the saddle surface 68. From the contact load acting between the ring 26 on the circumferential side, the relative speed of the saddle surface 50 and the saddle surface 68 with respect to the innermost ring 26 due to the relative slip between the element 30 and the hoop 28 and the viscosity of the lubricating oil. The friction in the mixed lubrication region indicated by the broken line between the fluid lubrication region and the boundary lubrication region on the Stribeck diagram is set.

図８は、伝動ベルト１０のプーリ１６およびプーリ１８のＶ溝１４のエレメント３０の挟み角とエレメント３０の第１エレメント３４の本体部４０および第２エレメント３６の本体部５８の幅方向の長さの製造公差（バラツキ）により生じるエレメント３０の第１エレメント３４のサドル面５０および第２エレメント３６のサドル面６８の高さのバラツキの程度を、Ｖ溝１４の挟み角の狭角化前後で分けて説明する模式図である。図８の左側の伝動ベルト１０が、Ｖ溝１４の挟み角の狭角化前の図であり、右側の伝動ベルト１０がＶ溝１４の挟み角の挟角化後の左側の挟み角よりも小さい図である。なお、図８中においては、プーリ１６のシーブ面２４に接触した第１エレメント３４が示されている。左側のＶ溝１４の狭角化前の伝動ベルト１０において、第１エレメント３４の本体部４０および第２エレメント３６の本体部５６の幅方向の長さの製造バラツキδＬにより、エレメント３０の第１エレメント３４のサドル面５０および第２エレメント３６のサドル面６８のプーリ１６またはプーリ１８の回転中心からの距離すなわちサドル面５０およびサドル面６８の高さは、δＲ１の範囲内でのバラツキを有する。一方、右側のＶ溝１４の狭角化後の伝動ベルト１０においては、第１エレメント３４の本体部４０および第２エレメント３６の本体部５６の幅方向の長さのバラツキが狭角化前と同じδＬである場合には、エレメント３０の第１エレメント３４のサドル面５０および第２エレメント３６のサドル面６８の高さは、δＲ１よりも大きいδＲ２の範囲内のバラツキを有する。このため、エレメント３０の第１エレメント３４の本体部４０および第２エレメント３６の本体部５８の幅方向の長さのバラツキδＬに対するサドル面５０およびサドル面６８の高さのバラツキδＲ、すなわちエレメント幅の製造バラツキに対するサドル面の高さのバラツキ感度δＲ／δＬは、狭角化後においてδＲ２／δＬであり、狭角化前のδＲ１／δＬよりも大きくなる。このＶ溝１４の狭角化によるバラツキ感度δＲ／δＬの増加により、狭角化後のエレメント３０の第１エレメント３４のサドル面５０および第２エレメント３６のサドル面７２と最内周側のリング２６との接触荷重およびリング２６に作用する面圧の増加は狭角化前と比較してより顕著となるが、エレメント３０が伝動ベルト１０のプーリ１６およびプーリ１８に巻き掛けられた部分に位置する際に、第１エレメント３４のダレ面５２側のサドル面５０および第２エレメント３６のダレ面７０側のサドル面６８において最内周側リング２６と接触するため、サドル面５０およびサドル面６８と最内周側リング２６との間の接触荷重の狭角化による増加が、サドル面が最内周側リングとエッジ当たりする場合と比較して抑制され、小径側プーリで発生するエレメント３０とフープ２８との滑りによる生じる摩擦の摩擦係数の増加が抑制される。   8 shows the angle between the elements 30 of the pulley 16 of the transmission belt 10 and the V-groove 14 of the pulley 18 and the lengths of the main body portion 40 of the first element 34 and the main body portion 58 of the second element 36 in the width direction. The degree of variation in the height of the saddle surface 50 of the first element 34 and the saddle surface 68 of the second element 36 of the element 30 caused by the manufacturing tolerance (variation) of the element 30 is divided before and after the narrowing of the sandwiching angle of the V groove 14. FIG. 8 is a view of the left transmission belt 10 before the narrowing of the sandwiching angle of the V-groove 14, and the right transmission belt 10 is more than the sandwiching angle of the left side after the narrowing of the sandwiching angle of the V-groove 14. It is a small figure. In FIG. 8, the first element 34 in contact with the sheave surface 24 of the pulley 16 is shown. In the transmission belt 10 before the left V-groove 14 is narrowed, the first variation of the element 30 due to the manufacturing variation δL in the width direction of the main body portion 40 of the first element 34 and the main body portion 56 of the second element 36. The distance from the rotation center of the pulley 16 or the pulley 18 of the saddle surface 50 of the element 34 and the saddle surface 68 of the second element 36, that is, the height of the saddle surface 50 and the saddle surface 68 has a variation within the range of δR1. On the other hand, in the transmission belt 10 after narrowing the right V-groove 14, the variation in the length in the width direction of the main body portion 40 of the first element 34 and the main body portion 56 of the second element 36 is the same as before the narrowing. In the case of the same δL, the heights of the saddle surface 50 of the first element 34 and the saddle surface 68 of the second element 36 of the element 30 have variations within the range of δR2 that is larger than δR1. For this reason, the variation δR in the height of the saddle surface 50 and the saddle surface 68 with respect to the variation δL in the width direction of the main body portion 40 of the first element 34 and the main body portion 58 of the second element 36, that is, the element width The variation sensitivity δR / δL of the height of the saddle surface with respect to the manufacturing variation is δR2 / δL after the narrowing, and is larger than δR1 / δL before the narrowing. Due to the increase in variation sensitivity δR / δL due to the narrowing of the V-groove 14, the saddle surface 50 of the first element 34 and the saddle surface 72 of the second element 36 and the innermost ring on the innermost side are reduced. The contact load with the belt 26 and the increase in the surface pressure acting on the ring 26 become more conspicuous than before the narrowing of the angle, but the element 30 is positioned at the portion of the transmission belt 10 around the pulley 16 and the pulley 18. At this time, the saddle surface 50 on the sag surface 52 side of the first element 34 and the saddle surface 68 on the sag surface 70 side of the second element 36 are in contact with the innermost ring 26. Increase due to the narrowing of the contact load between the innermost ring 26 and the innermost ring 26 is suppressed as compared with the case where the saddle surface hits the edge with the innermost ring. An increase in the friction coefficient of the friction caused by the sliding between the generated element 30 and the hoop 28 is suppressed.

上述のように、本実施例の伝動ベルト１０によれば、エレメント３０は、伝動ベルト１０の進行方向における前面をプレス加工により成形する際にダレが発生する側のダレ面５２、伝動ベルト１０の進行方向における後面をプレス加工により成形する際にバリが発生する側のエッジ面５４として成形した第１エレメント３４と、前面をエッジ面７２、後面をダレ面７０として成形した第２エレメント３６とを、第１エレメント３４のエッジ面５４と第２エレメント３６のエッジ面７２とが対向するように交互に配置されている。このため、エレメント３０が伝動ベルト１０のプーリ１６およびプーリ１８に巻き掛けられた部分に位置する際、第１エレメント３４のエッジ面５４と第２エレメント３６のエッジ面７２とが密着し合うとともに、第１エレメント３４のダレ面５２が進行方向の前面に第２エレメント３６のダレ面７０が進行方向の後面にそれぞれ配置され、フープ２８の最内周側のリング２６は、第１エレメント３４のダレ面５２側のサドル面５０および第２エレメント３６のダレ面７０側のサドル面６８により接触する。これにより、エレメント３０が伝動ベルト１０のプーリ１６およびプーリ１８に巻き掛けられた部分に位置する際に、エレメント３０と最内周側のリング２６とのエッジ当たりが抑制されて、エレメント３０とリング２６との間の接触荷重が低減され、エレメント３０とフープ２８との滑りが発生する小径側プーリにおいてエレメント３０と最内周側のリング２６との間に生じる摩擦の摩擦係数が低減されることから、伝動ベルト１０の伝達効率が向上する。また、第１エレメント３４のエッジ面５４と第２エレメント３６のエッジ面７２との密着により、第１エレメント３４のエッジ面５４および第２エレメント３６のエッジ面７２に発生したバリの加工が必要ないため、エレメント３０の加工コストの増大を抑制することができる。   As described above, according to the transmission belt 10 of the present embodiment, the element 30 includes the sag surface 52 on the side where sag occurs when the front surface in the traveling direction of the transmission belt 10 is formed by press working, and the transmission belt 10. A first element 34 formed as an edge surface 54 on the side where burrs are generated when the rear surface in the traveling direction is formed by press working, and a second element 36 formed with the front surface as an edge surface 72 and the rear surface as a sag surface 70. The edge surfaces 54 of the first elements 34 and the edge surfaces 72 of the second elements 36 are alternately arranged so as to face each other. For this reason, when the element 30 is positioned at a portion of the transmission belt 10 wound around the pulley 16 and the pulley 18, the edge surface 54 of the first element 34 and the edge surface 72 of the second element 36 are in close contact with each other, The sag surface 52 of the first element 34 is disposed on the front surface in the traveling direction, and the sag surface 70 of the second element 36 is disposed on the rear surface in the traveling direction. The ring 26 on the innermost peripheral side of the hoop 28 Contact is made by the saddle surface 50 on the surface 52 side and the saddle surface 68 on the sag surface 70 side of the second element 36. As a result, when the element 30 is positioned at a portion of the transmission belt 10 that is wound around the pulley 16 and the pulley 18, the edge contact between the element 30 and the innermost ring 26 is suppressed, and the element 30 and the ring The contact load between the element 30 and the hoop 28 is reduced, and the friction coefficient of the friction generated between the element 30 and the innermost ring 26 is reduced in the small-diameter pulley in which the slip between the element 30 and the hoop 28 occurs. Therefore, the transmission efficiency of the transmission belt 10 is improved. Further, due to the close contact between the edge surface 54 of the first element 34 and the edge surface 72 of the second element 36, it is not necessary to process burrs generated on the edge surface 54 of the first element 34 and the edge surface 72 of the second element 36. Therefore, an increase in processing cost of the element 30 can be suppressed.

以上、本発明を表及び図面を参照して詳細に説明したが、本発明は更に別の態様でも実施でき、その主旨を逸脱しない範囲で種々変更を加え得るものである。   As mentioned above, although this invention was demonstrated in detail with reference to the table | surface and drawing, this invention can be implemented in another aspect, and can be variously changed in the range which does not deviate from the main point.

たとえば、前述の実施例の伝動ベルト１０は、第１エレメント３４の進行方向における前面のダレ面５２に係合突起４２が形成されるとともに進行方向後面のエッジ面５４に係合穴４４が形成され、第２エレメント３６の進行方向における前面のエッジ面７２に係合突起６０が形成されるとともに進行方向後面のダレ面７０に係合穴６２が形成されていたが、これに限定されるものではなく、第１エレメント３４の進行方向における後面のエッジ面５４に係合突起４２が形成されるとともに進行方向における前面のダレ面５２に係合穴４４が形成され、第２エレメント３６の進行方向における後面のダレ面７０に係合突起６０が形成されるとともに進行方向における前面のエッジ面７２に係合穴６２が形成されてもよい。   For example, in the transmission belt 10 of the above-described embodiment, the engagement protrusions 42 are formed on the sag surface 52 on the front surface in the traveling direction of the first element 34 and the engagement holes 44 are formed on the edge surface 54 on the rear surface in the traveling direction. The engagement protrusion 60 is formed on the edge surface 72 of the front surface in the traveling direction of the second element 36 and the engagement hole 62 is formed on the sag surface 70 on the rear surface in the traveling direction. However, the present invention is not limited to this. Rather, the engagement protrusions 42 are formed on the edge surface 54 of the rear surface in the traveling direction of the first element 34, and the engagement holes 44 are formed in the sag surface 52 of the front surface in the traveling direction. Engagement protrusions 60 may be formed on the sag surface 70 on the rear surface, and engagement holes 62 may be formed on the edge surface 72 on the front surface in the traveling direction.

また、前述の実施例の第１エレメント３４には一対の凹溝４４が形成され、第２エレメント３６には一対の凹溝６６が形成されていたが、第１エレメント３４および第２エレメント３６の幅方向の中央に形成された１個の凹溝４４および１個の凹溝６６であってもよい。   Further, the first element 34 of the above-described embodiment has a pair of concave grooves 44 and the second element 36 has a pair of concave grooves 66. The first element 34 and the second element 36 One concave groove 44 and one concave groove 66 formed at the center in the width direction may be used.

なお、上述したのはあくまでも一実施形態であり、その他一々例示はしないが、本発明は、その主旨を逸脱しない範囲で当業者の知識に基づいて種々変更、改良を加えた態様で実施することができる。   It should be noted that the above description is merely an embodiment, and other examples are not illustrated. However, the present invention is implemented in variously modified and improved modes based on the knowledge of those skilled in the art without departing from the gist of the present invention. Can do.

１０：伝動ベルト
２６：リング
３０：エレメント
３２、３３：ロッキングエッジ
３４：第１エレメント
３６：第２エレメント
５２、７０：ダレ面
５４、７２：エッジ面
10: Transmission belt 26: Ring 30: Element 32, 33: Rocking edge 34: First element 36: Second element 52, 70: Sag surface 54, 72: Edge surface

Claims (1)

厚み方向に連ねられて環状に配列される複数のエレメントが、無端環状のリングにより環状に結束されるとともに、前記エレメントの配列方向での一方の側面に、隣接する他のエレメントに接触して相対回動の中心となるロッキングエッジが形成された伝動ベルトにおいて、
前記一方の側面を、前記エレメントをプレス加工により成形する際にダレが発生する側のダレ面とし、
前記エレメントの前記一方の側面とは反対側の他方の側面を、前記エレメントをプレス加工により成形する際にバリが発生する側のエッジ面とし、
前記伝動ベルトの進行方向における前面をダレ面、後面をエッジ面として成形した第１エレメントと、前記伝動ベルトの進行方向における前面をエッジ面、後面をダレ面として成形した第２エレメントとを、
前記第１エレメントのエッジ面と前記第２エレメントのエッジ面とが対向するように交互に配置したことを特徴とする伝動ベルト。 A plurality of elements arranged in a ring in the thickness direction are bound together in a ring shape by an endless ring, and on one side surface in the arrangement direction of the elements, the other elements are adjacent to each other. In the transmission belt formed with the rocking edge that becomes the center of rotation,
The one side surface is a sagging surface on the side where sagging occurs when the element is formed by pressing.
The other side surface opposite to the one side surface of the element is an edge surface on the side where burrs are generated when the element is formed by press working,
A first element formed with a front surface in the traveling direction of the transmission belt as a sag surface and a rear surface as an edge surface; a second element formed with a front surface in the traveling direction of the transmission belt as an edge surface and a rear surface as a sag surface;
The power transmission belt is characterized in that the edge surface of the first element and the edge surface of the second element are alternately arranged so as to face each other.
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