JP2562160B2 - Transmission belt - Google Patents
Transmission beltInfo
- Publication number
- JP2562160B2 JP2562160B2 JP62327451A JP32745187A JP2562160B2 JP 2562160 B2 JP2562160 B2 JP 2562160B2 JP 62327451 A JP62327451 A JP 62327451A JP 32745187 A JP32745187 A JP 32745187A JP 2562160 B2 JP2562160 B2 JP 2562160B2
- Authority
- JP
- Japan
- Prior art keywords
- radius
- curvature
- rocker joint
- pulley
- transmission belt
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
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- Transmissions By Endless Flexible Members (AREA)
Description
【発明の詳細な説明】 (産業上の利用分野) 本発明は無段変速機のV溝プーリ間に掛け渡して用い
る伝動ベルトに関するものである。Description: TECHNICAL FIELD The present invention relates to a transmission belt that is used by being stretched between V-groove pulleys of a continuously variable transmission.
(従来の技術) この種伝動ベルトとしては従来、特開昭59−200838号
公報に記載の如く、同じ曲率半径の円筒面で互に接して
転動可能な一対の転動部材よりなるロッカジョイントピ
ンにより多数のリンクプレートを順次連結して構成した
無終端リンク連結体を具え、これにその長手方向へ順次
配してプーリV溝と摩擦係合する多数のV形ブロックを
設けた型式のものが知られている。(Prior Art) Conventionally, as a transmission belt of this type, as described in Japanese Patent Laid-Open No. 59-200838, a rocker joint composed of a pair of rolling members capable of rolling in contact with each other on cylindrical surfaces having the same radius of curvature. A model in which an endless link connecting body constituted by connecting a large number of link plates one after another by a pin is provided, and a plurality of V-shaped blocks which are sequentially arranged in the longitudinal direction thereof and frictionally engage with the pulley V groove are provided. It has been known.
しかしてかかる構成の伝動ベルトでは、ロッカジョイ
ントピンの転動部材円筒面をロッカジョイントピン間で
同じにしていたため、伝動ベルトがV溝プーリに巻付く
際、特定周波数(ベルト噛合い1次周波数)の騒音レベ
ルが高くなる。However, in the transmission belt having such a structure, the rolling member cylindrical surface of the rocker joint pin is the same between the rocker joint pins, so that when the transmission belt is wound around the V-groove pulley, a specific frequency (belt meshing primary frequency) The noise level will be high.
そこで本願出願人は先に実願昭62−92838号により、
転動部材円筒面の曲率半径がロッカジョイントピン間で
異なる2種類以上のロッカジョイントピンを用い、これ
により特定周波数で騒音レベルが高くなるのを防止する
ことを狙った技術を先に提案済である。Therefore, the applicant of the present application previously filed Japanese Utility Model Application No. 62-92838,
We have previously proposed a technology aiming at preventing noise levels from increasing at a specific frequency by using two or more types of rocker joint pins with different radii of curvature of the rolling member cylindrical surface between the rocker joint pins. is there.
(発明が解決しようとする問題点) ところでこの提案技術では、転動部材円筒面の曲率半
径につきその最大値及び最小値を規定していないため、
当該曲率半径の選択次第によってはなお、或るベルト噛
合い1次周波数で騒音レベルが高くなるのを確かめた。
又、無段変速機の停止寸前にトルクの変動が大きくな
り、ガクガク振動を発生することも確かめた。(Problems to be Solved by the Invention) By the way, in this proposed technique, the maximum value and the minimum value of the radius of curvature of the cylindrical surface of the rolling member are not specified,
It was confirmed that the noise level increased at a certain belt meshing primary frequency depending on the selection of the radius of curvature.
Moreover, it was confirmed that the fluctuation of the torque became large just before the stop of the continuously variable transmission, and the rattling vibration occurred.
(問題点を解決するための手段) 本発明は、これらの問題が全て転動部材円筒面の曲率
半径差に起因するプーリ巻付き半径の差に応じて生ずる
との事実認識に基づき、転動部材円筒面の曲率半径を前
記の問題が生じない値に定めるもので、 一対の転動部材よりなり、これら一対の転動部材が同
じ曲率半径の円筒面で相互に接して転動するようにした
ロッカジョイントピンにより、多数のリンクプレートを
順次連結して構成した無終端リンク連結体を具え、この
無終端リンク連結体に長手方向へ順次配してプーリV溝
と摩擦係合する多数のV形ブロックを設け、前記ロッカ
ジョイントピンとして、転動部材円筒面の曲率半径がロ
ッカジョイントピン間で異なる、2種類以上のロッカジ
ョイントピンを用いた伝動ベルトにおいて、 前記ロッカジョイントピン間で異なる転動部材円筒面
の曲率半径をそれぞれ、 を満足する最大曲率半径rmax及び最小曲率半径rmin間の
値に選択した構成に特徴づけられる。(Means for Solving the Problems) The present invention is based on the fact that all of these problems occur in accordance with the difference in the radius of curvature of the rolling member, which is caused by the difference in the radius of curvature of the cylindrical surface. It defines the radius of curvature of the cylindrical surface of the member to a value that does not cause the above problem. It consists of a pair of rolling members, and these rolling members make contact with each other on cylindrical surfaces of the same radius of curvature. With the rocker joint pin, an endless link connecting body formed by connecting a number of link plates sequentially is provided, and a plurality of Vs frictionally engaged with the pulley V groove by sequentially arranging the endless link connecting body in the longitudinal direction. In a transmission belt using two or more types of rocker joint pins, the rocker joint pins are provided with a shaped block, and the radius of curvature of the rolling member cylindrical surface is different between the rocker joint pins. Each radius of curvature of the different rolling members cylindrical surface between Intopin, To a value between the maximum radius of curvature r max and the minimum radius of curvature r min that satisfies
(作 用) V溝プーリに掛けての伝動ベルトの実用中、V溝プー
リはこれに摩擦係合するV形ブロックとの間で動力の受
渡しを行い、V形ブロックは無終端リンク連結体との間
で動力の受渡しを行って所定の動力伝達を可能にする。(Operation) During practical use of the transmission belt hung on the V-groove pulley, the V-groove pulley transfers power to and from the V-shaped block that frictionally engages with the V-shaped pulley. Power is transferred between the two to enable predetermined power transmission.
しかし、ロッカジョイントピンの転動部材円筒面に2
種類以上の曲率半径を設定し、これら曲率半径を前記の
式によって規定されるrmax,rmin間の値に選択するた
め、伝動ベルトがV溝プーリに巻付く際特定周波数で騒
音レベルが高くなったり、停止寸前にトルク変動が大き
くなってガクガク振動が発生するのを防止することがで
きる。However, 2 on the cylindrical surface of the rocker joint pin rolling member.
Since more than one kind of radius of curvature is set and these radii of curvature are selected as values between r max and r min defined by the above formula, when the transmission belt is wound around the V groove pulley, the noise level is high at a specific frequency. It is possible to prevent the occurrence of jerky vibration due to a large torque fluctuation immediately before the stop.
(実施例) 以下、図示の実施例に基づき本発明を詳細に説明す
る。(Examples) Hereinafter, the present invention will be described in detail based on illustrated examples.
第1図は本発明伝動ベルトの一実施例で、同図(a)
は要部切欠平面図、(b)は縦断正面図、(c)は要部
縦断側面図を示す。FIG. 1 shows an embodiment of the power transmission belt of the present invention.
Shows a cutaway plan view of essential parts, (b) shows a front view in vertical section, and (c) shows a side view in vertical section.
これら図中1は多数のロッカジョイントピンで、各ロ
ッカジョイントピンは一対の転動部材1a,1bで構成し、
各対の転動部材は同じ曲率半径の円筒面を互に接して相
互に転動可能とする。しかして、ロッカジョイントピン
間で転動部材円筒面の曲率半径がr1,r2,r3で示す如く異
なるよう3種類のロッカジョイントピンを用意し、これ
ら3種類のロッカジョイントピンにより多数のリンクプ
レート2を相互に連結して無終端リンク連結体3,4を構
成する。In these figures, reference numeral 1 denotes a number of rocker joint pins, each rocker joint pin comprising a pair of rolling members 1a, 1b,
The rolling members of each pair contact cylindrical surfaces having the same radius of curvature with each other so that they can roll with each other. Therefore, three types of rocker joint pins are prepared so that the radius of curvature of the rolling member cylindrical surface is different between the rocker joint pins as shown by r 1 , r 2 and r 3 , and a large number of these three types of rocker joint pins are used. The link plates 2 are connected to each other to form endless link connection bodies 3 and 4.
3種類のロッカジョイントピンは配列順序をランダム
とするが、リンク連結体3,4間でこの配列順序を同じと
する。そして2本のリンク連結体3,4を、同じ種類のロ
ッカジョイントピンが隣り合うようピン配列ピッチP0の
半径だけずらせて並置し、各リンク連結体の各ロッカジ
ョイントピンを他方のリンク連結体のピン間に侵入させ
る。この時、侵入し合ったピン1の端部間に隙間がある
場合、ブッシュ5(図面では便宜上1個のみを示す)に
よりこの隙間を埋めてリンク連結体3,4の長手方向相対
位置が不変に保たれるようにする。The three rocker joint pins have a random arrangement order, but the link connection bodies 3 and 4 have the same arrangement order. Then, the two link connecting bodies 3 and 4 are juxtaposed by being displaced by the radius of the pin arrangement pitch P 0 so that the rocker joint pins of the same type are adjacent to each other, and each rocker joint pin of each link connecting body is connected to the other link connecting body. In between the pins. At this time, if there is a gap between the ends of the pins 1 that have entered each other, the gap 5 is filled with the bush 5 (only one is shown in the drawing for convenience) so that the relative positions in the longitudinal direction of the link coupling bodies 3 and 4 do not change. To be kept at.
これらリンク連結体3,4をまとめて横方向に包囲する
V形ブロック6を順次リンク連結体3,4の長手方向に滑
動可能に設ける。そのため各V形ブロック6に形成した
窓6a間に突起6bを設け、これによりリンク連結体3,4の
ピン(1)軸線方向相対位置を不変に保つ。A V-shaped block 6 which encloses the link connecting bodies 3 and 4 together in the lateral direction is sequentially provided slidably in the longitudinal direction of the link connecting bodies 3 and 4. Therefore, a protrusion 6b is provided between the windows 6a formed in each V-shaped block 6 to keep the relative position of the link connectors 3 and 4 in the axial direction of the pin (1) unchanged.
上記の伝動ベルトを組立てるに当っては、リンク連結
体3,4を無終端状とする直前迄組立てておき、これらリ
ンク連結体3,4の並置を行なう。このように並置したリ
ンク連結体3,4にV形ブロック6の窓6aを嵌合してV形
ブロック6を順次組付ける。そして最後のV形ブロック
を嵌合したところで、この最後のV形ブロックに設けた
ピン挿入孔(図示せず)より最後のピン1を挿入しつつ
リンク連結体3,4を無終端形状にして伝動ベルトの組立
てを完了する。In assembling the above-mentioned transmission belt, the link connecting bodies 3 and 4 are assembled until just before the endless shape, and the link connecting bodies 3 and 4 are juxtaposed. The window 6a of the V-shaped block 6 is fitted into the link connection bodies 3 and 4 arranged side by side in this way, and the V-shaped block 6 is assembled in sequence. Then, when the final V-shaped block is fitted, the link connecting bodies 3 and 4 are made into an endless shape while inserting the final pin 1 through the pin insertion hole (not shown) provided in the final V-shaped block. Complete the assembly of the power transmission belt.
実用に当っては第1図(b)に示すように、V形ブロ
ック6をプーリV溝7に巻き掛けして伝動ベルトをV溝
プーリ間に掛け渡す。この時、駆動側プーリの動力はそ
のV溝に摩擦係合したV形ブロック6からリンク連結体
3,4に至り、その被動側プーリのV溝に摩擦係合したV
形ブロック6を経て当該プーリに達し、両プーリ間で動
力の受渡しを行なうことができる。In practical use, as shown in FIG. 1 (b), the V-shaped block 6 is wound around the pulley V groove 7 and the transmission belt is stretched between the V groove pulleys. At this time, the power of the driving pulley is changed from the V-shaped block 6 frictionally engaged with the V groove to the link connecting body.
V that has reached 3 and 4 and is frictionally engaged with the V groove of the driven pulley
It is possible to reach the pulley through the shaped block 6 and transfer power between the both pulleys.
そして、ロッカジョイントピン1の転動部材1a,1bに
おける円筒面の曲率半径r1,r2,r3を夫々以下の如くに決
定する。Then, the radii of curvature r 1 , r 2 , r 3 of the cylindrical surfaces of the rolling members 1a, 1b of the rocker joint pin 1 are determined as follows, respectively.
先ずx−y座標系として示す第2図につき、転動部材
円筒面の曲率半径がr1の時のロッカジョイントピン1の
プーリ走行半径R(転動部材1a,1bの接点B1からプーリ
回転中心0迄の距離)を求める。First, referring to FIG. 2 shown as an xy coordinate system, when the radius of curvature of the cylindrical surface of the rolling member is r 1 , the pulley running radius R of the rocker joint pin 1 (from the contact point B 1 of the rolling members 1a and 1b to the pulley rotation). Find the distance to the center 0).
第2図中リンクプレート2aはプーリに完全に巻き付い
ているリンク、リンクプレート2bは巻き付き始めている
リンクプレート、リンクプレート2cは巻き付いていない
リンクプレートである。又第3図はリンクプレート2a,2
b間のロッカジョイントピンをx−y座標系に拡大して
示す。In FIG. 2, the link plate 2a is a link that is completely wound around the pulley, the link plate 2b is a link plate that has started winding, and the link plate 2c is a link plate that is not wound. Fig. 3 shows the link plates 2a, 2
The rocker joint pin between b is expanded and shown to an xy coordinate system.
βはリンクプレート2aとリンクプレート2bとの交差角
(リンクプレート中心線の成す角)、 点A1はリンクプレート2aとリンクプレート2bとの中心
線が1直線となる場合における転動部材1a,1bの接点、 点B1は交差角βのときの転動部材1a,1bの接点、 点01は転動部材1aの曲率半径の中心点、 点O1は点B1から線分O1−A1に下ろした垂線の足、 R0は点0と点A1との間の距離、 とする。β is the angle of intersection between the link plates 2a and 2b (the angle formed by the link plate center lines), and point A 1 is the rolling member 1a when the center lines of the link plates 2a and 2b are one straight line, 1b the contact point B 1 represents rolling element 1a when the crossing angle beta, contacts 1b, the point 0 1 is the radius of curvature of the center point of the rolling member 1a, the line segment O 1 point O 1 from the point B 1 -A 1 is a perpendicular foot, R 0 is the distance between point 0 and point A 1 .
ここで、 とすると、 ロッカジョイントピン1のプーリ巻き付き半径 R(=0 B1)は となる。here, Then, the radius R (= 0 B 1 ) of the rocker joint pin 1 around the pulley is Becomes
ここで、βとθとの関係は第4図から分かるとおり、 β+(π/2+θ)+(π/2−α)=π ∴β=α−θ である。ただし、 α=sin-1(P0/2R0) (P0:ピッチ) ところで、完全に巻付きが終了すると、θ=−α,β
=2αであるからロッカジョイントピンのプーリ走行半
径Rは、 となる。次に、第1図(c)においてr1<r2<r3とする
と、転動部材円筒面の最大曲率半径r3と最小曲率半径r1
との違いによるロッカジョイントピンのプーリ走行半径
差ΔRは で表わされる。Here, the relationship between β and θ is β + (π / 2 + θ) + (π / 2−α) = π∴β = α−θ, as can be seen from FIG. However, α = sin -1 (P 0 / 2R 0 ) (P 0 : pitch) By the way, when winding is completely completed, θ = -α, β
= 2α, the pulley running radius R of the rocker joint pin is Becomes Next, when r 1 <r 2 <r 3 in FIG. 1C, the maximum radius of curvature r 3 and the minimum radius of curvature r 1 of the rolling member cylindrical surface are set.
The difference in the pulley running radius of the rocker joint pin ΔR is Is represented by
一方、V形ブロック幅の差ΔWによるロッカジョイン
トピンのプーリ走行半径差ΔRは ΔR=ΔW/2tan γ …(2) (γ:プーリV溝の半シーブ角) で表わされる。On the other hand, the pulley running radius difference ΔR of the rocker joint pin due to the V-shaped block width difference ΔW is represented by ΔR = ΔW / 2tan γ (2) (γ: half sheave angle of pulley V groove).
(1)式においてΔRはr3,r1間の差Δr=r3−r1が
大きい程、又R0が小さい程大きくなり、更に(2)式に
おいてΔRはΔWと比例関係にあるため、ΔrとΔWと
の間にはR0をパラメータとする第5図の関係が成立す
る。第5図中R0=Rminはロッカジョイントピンのプーリ
走行半径が無段変速機の変速範囲における最小値である
時の関係を示し、又R0=Rmaxはロッカジョイントピンの
プーリ走行半径が無段変速機の変速範囲における最大値
である時の関係を示す。(1) as ΔR is larger difference [Delta] r = r 3 -r 1 between r 3, r 1 in the expression, also increases as R 0 is small, and (2) because ΔR is proportional to ΔW in formula , Δr and ΔW satisfy the relationship shown in FIG. 5 with R 0 as a parameter. In Fig. 5, R 0 = R min shows the relationship when the pulley running radius of the rocker joint pin is the minimum value in the gear shift range of the continuously variable transmission, and R 0 = R max is the pulley running radius of the rocker joint pin. Shows the relationship when is the maximum value in the shift range of the continuously variable transmission.
ところで、V形ブロック幅の差ΔW毎にベルト噛合い
1次周波数の振動レベルL及びトルク変動量Tを実験に
より求めると、夫々第6図の如き傾向を持って変化する
ことを確かめた。又、感覚上許容できる騒音レベル及び
トルク変動レベルは夫々L1,T1であり、このことから騒
音レベル及びトルク変動を共に許容範囲内に抑えるため
には、V形ブロック幅の差ΔWを0.08〜0.13mmの範囲内
にすべきであることを確かめた。By the way, when the vibration level L of the belt meshing primary frequency and the torque fluctuation amount T were obtained by an experiment for each difference ΔW of the V-shaped block width, it was confirmed that the vibration level L and the torque fluctuation amount T change with the tendency as shown in FIG. 6, respectively. Also, the noise level and the torque fluctuation level which are permissible perceptually are L 1 and T 1 , respectively. Therefore, in order to suppress both the noise level and the torque fluctuation within the permissible range, the V-shaped block width difference ΔW is 0.08. It was confirmed that it should be within the range of 0.13 mm.
このことから、騒音レベル及びトルク変動の双方を満
足する転動部材円筒面の曲率半径差Δrは、第5図及び
第6図を移記した第7図にXで示す範囲であることが判
る。しかして、トルク変動が問題になるのは、無段変速
機の停止直前、つまり変速比が最低速比で出力側V溝プ
ーリのベルト巻き掛け径が最大になっている時であるこ
とから、騒音レベル及びトルク変動の双方を満足するΔ
rの範囲は実際上第7図中Yで示す如きものである。From this, it is understood that the curvature radius difference Δr of the cylindrical surface of the rolling member that satisfies both the noise level and the torque fluctuation is in the range indicated by X in FIG. 7 which is a transfer of FIGS. 5 and 6. . The torque fluctuation becomes a problem immediately before the stop of the continuously variable transmission, that is, when the gear ratio is the minimum speed ratio and the belt winding diameter of the output side V-groove pulley is maximum. Δ that satisfies both noise level and torque fluctuation
The range of r is actually as shown by Y in FIG.
この範囲を式により表わすと、(1),(2)式より であり、この式を満足するr3,r1間の値に転動部材円筒
面の曲率半径r1,r2,r3を決定すれば、騒音レベル及びト
ルク変動を共に許容レベルに抑え込むことができる。When this range is expressed by an equation, from equations (1) and (2) Therefore, if the radii of curvature r 1 , r 2 , r 3 of the cylindrical surface of the rolling member are determined to be a value between r 3 and r 1 that satisfies this equation, both noise level and torque fluctuation can be suppressed to an allowable level. You can
このことから本例においては、r=11゜、P0=7.82m
m、Rmax=81mmの場合を例として、r1=5mm、r2=8mm、r
3=10mmに決定する。これにより(3)式中の が0.094/2tan γとなり、(3)式を満足して騒音レベ
ル及びトルク変動を共に許容範囲内に抑え込むことがで
きる。又、r1=5mmを(3)式に代入した場合9.26≦r3
≦11.93となり、このことからもr3=10mmとしたこと
で、騒音レベル及びトルク変動を許容範囲内に抑え得る
ことが判る。Therefore, in this example, r = 11 °, P 0 = 7.82 m
Taking m and R max = 81 mm as an example, r 1 = 5 mm, r 2 = 8 mm, r
Determine to 3 = 10 mm. Thus, in equation (3) Is 0.094 / 2tan γ, and both the noise level and torque fluctuation can be suppressed within the allowable range by satisfying the expression (3). When r 1 = 5 mm is substituted into the formula (3), 9.26 ≦ r 3
≦ 11.93, which also shows that the noise level and the torque fluctuation can be suppressed within the permissible range by setting r 3 = 10 mm.
(発明の効果) かくして本発明伝動ベルトは、ロッカジョイントピン
を構成する転動部材の円筒面を前記の如くに定めた最大
曲率半径及び最小曲率半径間の曲率半径とするから、伝
動ベルトがV溝プーリに巻付く際特定周波数で騒音レベ
ルが高くなるのを防止し得ると共に、停止寸前のトルク
変動が大きくなってガクガク振動が発生するのを防止す
ることができる。(Effects of the Invention) Thus, in the transmission belt of the present invention, the cylindrical surface of the rolling member constituting the rocker joint pin is set to have the radius of curvature between the maximum radius of curvature and the minimum radius of curvature determined as described above, and therefore the transmission belt is V-shaped. It is possible to prevent the noise level from becoming high at a specific frequency when wound around the grooved pulley, and to prevent the jerky vibration from occurring due to the large torque fluctuation immediately before the stop.
第1図は本発明伝動ベルトの一実施例を示し、同図
(a)はその要部切欠平面図、(b)は縦断平面図、
(c)は要部縦断側面図、 第2図及び第3図は夫々ロッカジョイントピンの模式
図、 第4図は伝動ベルトのプーリ巻付き状態を示す模式図、 第5図は転動部材円筒面の曲率半径差とV形ブロック幅
の差との関係線図、 第6図はV形ブロック幅の差とベルト噛合い1次周波数
の騒音レベル及びトルク変動量との関係を示す線図、 第7図は騒音レベル及びトルク変動を満足する転動部材
円筒面の曲率半径差の範囲を示す領域線図である。 1……ロッカジョイントピン 1a,1b……転動部材、2……リンクプレート 3,4……無終端リンク連結体 6……V形ブロック、7……プーリV溝FIG. 1 shows an embodiment of a power transmission belt of the present invention, in which FIG. 1 (a) is a plan view of a notched portion of the same, and FIG.
(C) is a longitudinal side view of a main part, FIGS. 2 and 3 are schematic diagrams of rocker joint pins, FIG. 4 is a schematic diagram showing a pulley winding state of a transmission belt, and FIG. 5 is a rolling member cylinder. FIG. 6 is a diagram showing the relationship between the difference in the radius of curvature of the surfaces and the difference in the V-shaped block width. FIG. 6 is a diagram showing the relationship between the difference in the V-shaped block width and the noise level of the belt meshing primary frequency and the torque fluctuation amount. FIG. 7 is a region diagram showing the range of the radius of curvature difference of the cylindrical surface of the rolling member that satisfies the noise level and the torque fluctuation. 1 ... Rocker joint pin 1a, 1b ... Rolling member, 2 ... Link plate 3,4 ... Endless link connection body 6 ... V-shaped block, 7 ... Pulley V groove
Claims (1)
動部材が同じ曲率半径の円筒面で相互に接して転動する
ようにしたロッカジョイントピンにより、多数のリンク
プレートを順次連結して構成した無終端リンク連結体を
具え、この無終端リンク連結体に長手方向へ順次配して
プーリV溝と摩擦係合する多数のV形ブロックを設け、
前記ロッカジョイントピンとして、転動部材円筒面の曲
率半径がロッカジョイントピン間で異なる、2種類以上
のロッカジョイントピンを用いた伝動ベルトにおいて、 前記ロッカジョイントピン間で異なる転動部材円筒面の
曲率半径をそれぞれ、 を満足する最大曲率半径rmax及び最小曲率半径rmin間の
値に選択したことを特徴とする伝動ベルト。1. A large number of link plates are sequentially connected by a rocker joint pin which is composed of a pair of rolling members and which rolls in contact with each other on cylindrical surfaces having the same radius of curvature. And a plurality of V-shaped blocks which are sequentially arranged in the longitudinal direction and frictionally engage with the pulley V groove.
As the rocker joint pin, in the transmission belt using two or more types of rocker joint pins, the curvature radius of the rolling member cylindrical surface is different between the rocker joint pins, and the curvature of the rolling member cylindrical surface is different between the rocker joint pins. Each radius, A transmission belt having a maximum curvature radius r max and a minimum curvature radius r min that satisfy
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP62327451A JP2562160B2 (en) | 1987-12-25 | 1987-12-25 | Transmission belt |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP62327451A JP2562160B2 (en) | 1987-12-25 | 1987-12-25 | Transmission belt |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH01169150A JPH01169150A (en) | 1989-07-04 |
JP2562160B2 true JP2562160B2 (en) | 1996-12-11 |
Family
ID=18199309
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP62327451A Expired - Fee Related JP2562160B2 (en) | 1987-12-25 | 1987-12-25 | Transmission belt |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2562160B2 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006077847A (en) * | 2004-09-08 | 2006-03-23 | Jtekt Corp | Power transmission chain and power transmission device equipped with it |
JP4941698B2 (en) | 2005-02-04 | 2012-05-30 | 株式会社ジェイテクト | Power transmission chain and power transmission device including the same |
JP2007051711A (en) | 2005-08-18 | 2007-03-01 | Jtekt Corp | Power transmission chain and power transmission provided with the same |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4650445A (en) * | 1985-02-20 | 1987-03-17 | Borg-Warner Automotive, Inc. | Chain-belt |
-
1987
- 1987-12-25 JP JP62327451A patent/JP2562160B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JPH01169150A (en) | 1989-07-04 |
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