JPH0222253B2 - - Google Patents
Info
- Publication number
- JPH0222253B2 JPH0222253B2 JP57172032A JP17203282A JPH0222253B2 JP H0222253 B2 JPH0222253 B2 JP H0222253B2 JP 57172032 A JP57172032 A JP 57172032A JP 17203282 A JP17203282 A JP 17203282A JP H0222253 B2 JPH0222253 B2 JP H0222253B2
- Authority
- JP
- Japan
- Prior art keywords
- rubber
- tooth
- belt
- layer
- hardness
- 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 - Lifetime
Links
- 229920001971 elastomer Polymers 0.000 claims description 96
- 239000005060 rubber Substances 0.000 claims description 96
- 238000010030 laminating Methods 0.000 claims description 2
- 230000005540 biological transmission Effects 0.000 description 6
- 239000000463 material Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 239000000853 adhesive Substances 0.000 description 3
- 230000001070 adhesive effect Effects 0.000 description 3
- 238000005336 cracking Methods 0.000 description 3
- 230000006866 deterioration Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 229920001084 poly(chloroprene) Polymers 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 238000004073 vulcanization Methods 0.000 description 2
- 229920002292 Nylon 6 Polymers 0.000 description 1
- 229920002302 Nylon 6,6 Polymers 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 239000003831 antifriction material Substances 0.000 description 1
- 208000018747 cerebellar ataxia with neuropathy and bilateral vestibular areflexia syndrome Diseases 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 239000011521 glass Substances 0.000 description 1
- 239000003292 glue Substances 0.000 description 1
- 238000004898 kneading Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
- F16G1/00—Driving-belts
- F16G1/28—Driving-belts with a contact surface of special shape, e.g. toothed
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
Description
（産業上の利用分野）
本発明は、主として高温高負荷用の歯付ベルト
に関する。
（従来の技術）
従来、高負荷伝動装置においては、歯付ベルト
が使用されている。しかし、非常な高負荷条件
下、例えば負荷がベルト１本当り6t〜10tという
条件での使用であるため、歯付ベルト、特に歯部
の摩耗が著しいという問題があつた。
そこで、前述したような高負荷に対処するため
に、歯部の強度を高めて摩耗を少なくし、それに
よつて寿命を向上することが行われている。すな
わち、具体的には、
(i) 伝動負荷の単位当たりの受圧面積が大きくす
るために歯部を大きくする、つまり歯高さを高
く、歯幅を長く、かつベルト幅を広くする。
(ii) 歯部に圧力が均一に分散して加わるように、
インボリユート歯、直線歯、円弧歯などを用い
て噛合をスムーズにする。
(iii) 歯部の変形量を少なくするために歯部の剛性
を高める。例えば、(a)歯ゴムに単繊維を練り込
んで硬度を向上させること、(b)歯部の帆布の組
織を耐摩耗性としたり帆布を多数重積するこ
と、(c)プーリ溝よりもベルト歯を大きくし、そ
れによつてプーリ溝内でベルト歯部が圧縮され
剛性が高まるようにすること。
(iv) 歯部の摩耗係数を小さくする。例えば、プー
リとの接触界面に、減摩剤、滑材などを混入す
ること。
などの手法がある。
したがつて、歯付ベルトを使用条件に応じて、
歯部の大きさを決めるとともに、前記(i)〜(iv)の手
法を単独あるいは組合せて、ベルト寿命の向上を
図つていた。
（発明が解決しようとする課題）
上記の手法によつて、常温での高負荷伝動の場
合は、ある程度の効果は認められたが、雰囲気温
度の高い高負荷伝動の場合は、短時間でゴムが硬
化して割れたり、歯部帆布の摩耗が激しかつたり
して充分に満足した効果を得ていないのが現状で
あつた。
本発明はかかる点に鑑みてなされたもので、高
温高負荷条件下においても、十分なベルト寿命を
示す歯付ベルトを提供することを目的とする。
（課題を解決するための手段）
上記の目的を達成するため、本発明の解決手段
は、背ゴム層と抗張体層とが積層されてなる平ベ
ルト状のベルト基帯の該抗張体層側の面にほぼ一
定の厚さの緩衝ゴムシートが接合され、該緩衝ゴ
ムシートの表面に歯部を構成する複数の歯ゴムが
ベルト全周に亘つて等ピツチ間隔で接合され、更
に該歯ゴムの表面及び歯ゴム間の緩衝ゴムシート
の表面に沿つて帆布が貼付されてなるものとす
る。さらに、上記歯ゴムよりなる歯部はそのゴム
硬度が65゜〜80゜の範囲になるように設定され、前
記緩衝ゴムシートよりなる緩衝ゴム層はそのゴム
硬度が上記歯部のゴム硬度と同等もしくはそれ以
下に、かつその厚さが上記歯部の高さの13〜37％
の範囲になるように設定され、上記歯部は、その
歯高さｈと歯幅ｌとの関係が
ｈ／ｌ＝0.20〜0.30
の範囲になるように形成されているものとする。
（作用）
これにより、本発明では、歯部を構成する歯ゴ
ムはゴム硬度が65゜〜80゜と比較的軟らかいが、歯
部の歯幅に対して歯高さが0.2〜0.3と低いので、
抗張体層より歯部に動力を受けたりあるいは逆に
歯部より抗張体層に動力を与えたりするとき、歯
ゴムが軟らかい割に歯部の変形量は比較的少なく
てすみ、高負荷伝動が可能となる。また、上記歯
部は抗張体層に対して緩衝ゴム層を介して支持さ
れているので、高負荷使用時に該歯部に作用する
衝撃力（特に剪断力）を上記緩衝ゴム層によつて
も緩衝して歯部の摩耗を低減させることができ
る。
一方、歯部を構成する歯ゴムがゴム硬度65゜〜
80゜で比較的軟らかいことにより、使用時に圧縮
により硬度が上昇してもその絶対値はあまり大き
くならないので、ゴム弾性を長時間に亘つて保持
することになり、高温高負荷条件下でも硬化によ
る割れが生じ難い。
また、抗張体層と帆布との間には歯ゴムと同等
もしくはそれ以下のゴム硬度を有する緩衝ゴム層
が介在されているので、高負荷条件下での使用時
に、歯部間における谷部がプーリの山部で突き上
げられても、その突上げ力は緩衝ゴム層により効
果的に低減され、それによつて帆布の摩損が低減
し、高負荷条件下での長寿命化に通ずる。
尚、歯部のゴム硬度は、65゜以下では軟らかす
ぎて歯部の変形が大きくなり、歯飛び現象が生じ
る一方、80゜以上では熱劣化による歯ゴムの早期
割れ現象が生じるので、65゜〜80゜の範囲が望まし
い。また、緩衝ゴム層の厚さは、高負荷使用時、
該緩衝ゴム層に荷重が加わつた状態においてプー
リのピツチ径と外径との差の1/2（PLD）の範囲
内に収めることが伝動効率の上で好ましいので、
歯部及び緩衝ゴム層のゴム硬度を考慮して、歯部
の歯高さの13〜37％の範囲にする必要がある。さ
らに、歯部の歯高さｈと歯幅ｌとの比ｈ／ｌは、
0.20以下では歯高さが低くなりすぎてベルト歯部
のプーリ歯部に対する接触面積が小さくなり、か
えつて歯部の摩耗の点で不利となる一方、0.30以
上では歯高さが高くなり過ぎて歯部の変形が大き
くなり、歯飛び現象が生じるので、0.20〜0.30の
範囲が望ましい。
（実施例）
以下、本発明の実施例について、図面に沿つて
説明する。
第１図において、１は歯付ベルトで、背ゴム層
２と抗張体層３とが積層されてなる平ベルト状の
ベルト基帯５の該抗張体層３側の面に、ほぼ一定
の厚さの緩衝ゴムシートが接合されて緩衝ゴム層
４を構成し、該緩衝ゴムシートの表面に複数の歯
ゴムがベルト全周に亘つて等ピツチ間隔で接合さ
れて歯部６を構成し、該歯ゴムの表面及び歯ゴム
間の緩衝ゴムシートの表面に帆布が貼付されて帆
布層７を構成してなる。
歯部６は、歯高さをｈ、歯幅をｌとすると、そ
の比ｈ／ｌが、後述の実験結果より明らかなよう
にベルト寿命の面で0.2〜0.3の範囲が望ましく、
できればその他の性能、特に騒音低減の面からは
0.27〜0.29の範囲にあることが望ましい。また、
歯ゴム硬度が、実験により、65゜〜80゜（JISAによ
る）の範囲、望ましくは68゜〜72゜の範囲であるこ
とが、ベルト寿命の向上に対し有利であると確認
されている。
また、緩衝ゴム層４についても、実験により、
ゴム硬度が歯ゴム硬度と同一もしくはそれ以下で
あつてその相対硬度差が15゜以内に形成されると
ともに、その厚さΔtが歯高さｈの13％〜37％に
形成されることが望ましいと確認されている。
上記歯付ベルト１の各部の材料の一例を示すと
次の通りである。
(i) 背ゴム層２…ネオプレンゴムをベースとした
公知の配合によるゴム。
(ii) 抗張体層３…公知の接着処理を施した硝子コ
ード、ケプラーコード、またはスチールワイヤ
コード。
(iii) 緩衝ゴム層４及び歯部６…ネオプレンゴムを
ベースとした公知の配合によるゴム。ただし、
ゴム硬度は70゜である（JISAによる）。
(iv) 帆布層７…公知の接着処理を施した６ナイロ
ンもしくは66ナイロンを用いた平織、綾織又は
朱子織の織布。
続いて、上記歯付ベルト１の製造方法について
簡単に説明する。
（工程１）
抗張体である例えばケプラーコードを中心にし
て上ゴム及び下ゴムを積層して、プレス加硫す
る。
（工程２）
前記下ゴムをバフ研摩して、ケプラーコードの
下側付近まで取除く。
（工程３）
バフによる研摩面にネオプレンゴム糊を塗布
し、緩衝ゴム層４となる未加硫ゴムシートと、歯
部６（歯ゴム）となる別の未加硫ゴムシートと、
帆布層７となる帆布とを順に貼付してロール状に
巻き取る。
（工程４）
ロール状に巻き取られた成形シートを引き出
し、歯付金型を載置したプレス装置により送り焼
きする。
（工程５）
加硫後、必要に応じて幅切りをする。しかして
歯付ベルト１が形成される。
上記構成によれば、歯部６を構成する歯ゴムは
ゴム硬度が65゜〜80゜と比較的軟らかいが、歯部６
の歯幅に対して歯高さが0.2〜0.3と低いので、抗
張体層３より歯部６に動力を受けたりあるいは逆
に歯部６より抗張体層３に動力を伝えたりすると
き、歯ゴムが軟らかに割に歯部６の変形量は比較
的少なくてすむ。したがつて、高負荷伝動が可能
となる。また、上記歯部６は抗張体層３に対して
緩衝ゴム層４を介して支持されているので、高負
荷使用時に該歯部６に作用する衝撃力（特に剪断
力）を上記緩衝ゴム層４によつても緩衝して歯部
６の摩耗を低減させることができる。
一方、歯部６を構成する歯ゴムがゴム硬度65゜
〜80゜で比較的軟らかいことにより、使用時に圧
縮により硬度が上昇してもその絶対値はあまり大
きくならないので、ゴム弾性を長時間に亘つて保
持することになる。その結果、高温高負荷条件下
で、硬化による割れが生じ難く、長時間に亘つて
使用することができる。
また、抗張体層３と帆布層７との間には、歯ゴ
ムと同等もしくはそれ以下のゴム硬度を有し抗張
体層３の接着を兼ねた緩衝ゴム層４が介在されて
いるので、高負荷条件下での使用時に、歯部６，
６間における谷部８がプーリ９の山部１０で突き
上げられても、その突上げ力は緩衝ゴム層４によ
り効果的に低減され、それによつて帆布層７（帆
布）の摩損が低減し、高負荷条件下での長寿命化
に通ずる（第６図参照）。すなわち、歯付ベルト
の谷部においては、従来の歯付ベルトａでは、抗
張体層の硬いコードｂと帆布ｃとが直接接触して
いたので、第８図に示すように、その接触部分が
集中的に荷重を受け、コード長手方向にその部分
だけ摩耗が進みベルト破損に至つていたが、本発
明に係わる歯付ベルト１では、緩衝ゴム層４によ
つて帆布層７と抗張体層３とが直接接触すること
もなく、第７図に示すように、ベルト幅全体でほ
ぼ一様に荷重負担するので、局所的な帆布層７の
異常摩耗も生ぜず、したがつてベルト破損にも至
らない。
次いで、上記歯付ベルト１を用いて行つた実験
について説明する。
（実験１）
代表的な従来の歯付ベルト（表１参照）と本発
(Industrial Application Field) The present invention mainly relates to a toothed belt for use at high temperatures and high loads. (Prior Art) Conventionally, toothed belts have been used in high-load transmission devices. However, since the belt is used under very high load conditions, for example, a load of 6 to 10 tons per belt, there has been a problem in that the toothed belt, especially the toothed portion, is significantly worn. Therefore, in order to cope with the above-mentioned high loads, attempts have been made to increase the strength of the tooth portions to reduce wear and thereby extend the service life. That is, specifically: (i) To increase the pressure receiving area per unit of transmitted load, the tooth portion is made larger, that is, the tooth height is increased, the tooth width is increased, and the belt width is increased. (ii) so that pressure is applied to the teeth in an evenly distributed manner;
Smooth meshing using involute teeth, straight teeth, circular arc teeth, etc. (iii) Increase the rigidity of the teeth to reduce the amount of tooth deformation. For example, (a) kneading single fibers into the tooth rubber to improve its hardness, (b) making the structure of the canvas in the tooth part more wear-resistant or stacking many canvases, and (c) making the pulley groove more To enlarge the belt teeth so that the belt teeth are compressed within the pulley groove and the rigidity is increased. (iv) Reduce the wear coefficient of the teeth. For example, adding anti-friction agents, lubricants, etc. to the contact interface with the pulley. There are methods such as Therefore, depending on the usage conditions of the toothed belt,
In addition to determining the size of the tooth portion, the above-mentioned methods (i) to (iv) are used alone or in combination to improve belt life. (Problems to be Solved by the Invention) Although the above method was effective to some extent in the case of high-load transmission at room temperature, in the case of high-load transmission at high ambient temperature, the rubber At present, the material hardens and cracks, and the tooth canvas is severely worn, making it impossible to obtain a fully satisfactory effect. The present invention has been made in view of this point, and an object of the present invention is to provide a toothed belt that exhibits a sufficient belt life even under high temperature and high load conditions. (Means for Solving the Problems) In order to achieve the above object, the solving means of the present invention provides a tensile material of a flat belt-like belt base band in which a back rubber layer and a tensile material layer are laminated. A buffer rubber sheet with a substantially constant thickness is bonded to the layer side surface, and a plurality of tooth rubbers constituting tooth portions are bonded to the surface of the buffer rubber sheet at equal pitch intervals over the entire circumference of the belt. A canvas is pasted along the surface of the tooth rubber and the surface of the buffer rubber sheet between the tooth rubbers. Furthermore, the rubber hardness of the teeth made of the tooth rubber is set to be in the range of 65° to 80°, and the rubber hardness of the buffer rubber layer made of the buffer rubber sheet is equivalent to the rubber hardness of the teeth. or less, and its thickness is 13 to 37% of the height of the tooth above.
It is assumed that the tooth portion is formed so that the relationship between the tooth height h and the tooth width l is in the range of h/l=0.20 to 0.30. (Function) As a result, in the present invention, the tooth rubber constituting the tooth portion has a relatively soft rubber hardness of 65° to 80°, but the tooth height is low at 0.2 to 0.3 relative to the tooth width. ,
When power is applied to the teeth from the tensile layer, or conversely, when power is applied from the teeth to the tensile layer, the amount of deformation of the teeth is relatively small considering the softness of the tooth rubber, allowing high loads to be applied. Transmission becomes possible. In addition, since the tooth portion is supported by the tensile layer through the buffer rubber layer, the shock force (particularly shear force) acting on the tooth portion during high load use is absorbed by the buffer rubber layer. It can also buffer the teeth and reduce wear on the teeth. On the other hand, the tooth rubber that makes up the teeth has a rubber hardness of 65°~
Because it is relatively soft at 80 degrees, even if the hardness increases due to compression during use, the absolute value does not increase so much, so the rubber elasticity is maintained for a long time, and even under high temperature and high load conditions, it does not harden due to hardening. Hard to crack. In addition, since a buffer rubber layer with a rubber hardness equal to or lower than that of the tooth rubber is interposed between the tensile layer and the canvas, the troughs between the teeth can be easily removed when used under high load conditions. Even if the canvas is pushed up by the peak of the pulley, the pushing up force is effectively reduced by the buffer rubber layer, thereby reducing wear and tear on the canvas and extending its life under high load conditions. If the rubber hardness of the teeth is less than 65°, it will be too soft and deformation of the teeth will increase, resulting in tooth skipping, while if it is more than 80°, premature cracking of the tooth rubber will occur due to thermal deterioration. A range of ~80° is desirable. In addition, the thickness of the buffer rubber layer should be adjusted when using high loads.
In terms of transmission efficiency, it is preferable to keep the load within the range of 1/2 (PLD) of the difference between the pitch diameter and the outer diameter of the pulley when a load is applied to the buffer rubber layer.
Considering the rubber hardness of the tooth portion and the buffer rubber layer, it is necessary to set the rubber hardness within the range of 13 to 37% of the tooth height of the tooth portion. Furthermore, the ratio h/l of the tooth height h and the tooth width l of the tooth portion is:
If it is less than 0.20, the tooth height will be too low and the contact area of the belt teeth with the pulley teeth will be small, which will be disadvantageous in terms of wear of the teeth. On the other hand, if it is more than 0.30, the tooth height will be too high. A range of 0.20 to 0.30 is desirable because the deformation of the tooth portion becomes large and tooth skipping occurs. (Example) Examples of the present invention will be described below with reference to the drawings. In FIG. 1, reference numeral 1 denotes a toothed belt, which is attached almost uniformly to the surface on the tensile layer 3 side of a flat belt base belt 5 made by laminating a back rubber layer 2 and a tensile layer 3. A buffer rubber sheet with a thickness of A canvas layer 7 is formed by pasting canvas on the surface of the tooth rubber and on the surface of the buffer rubber sheet between the tooth rubbers. Assuming that the tooth height of the tooth portion 6 is h and the tooth width is l, the ratio h/l is preferably in the range of 0.2 to 0.3 in terms of belt life, as is clear from the experimental results described below.
If possible, improve other performance, especially in terms of noise reduction.
It is desirable to be in the range of 0.27 to 0.29. Also,
It has been confirmed through experiments that a tooth rubber hardness in the range of 65° to 80° (according to JISA), preferably in the range of 68° to 72°, is advantageous for improving belt life. Also, regarding the buffer rubber layer 4, through experiments,
It is desirable that the rubber hardness is the same as or lower than the tooth rubber hardness, the relative hardness difference is within 15 degrees, and the thickness Δt is 13% to 37% of the tooth height h. It has been confirmed. Examples of materials for each part of the toothed belt 1 are as follows. (i) Back rubber layer 2: Rubber with a known composition based on neoprene rubber. (ii) Tensile layer 3: Glass cord, Kepler cord, or steel wire cord subjected to known adhesive treatment. (iii) Buffer rubber layer 4 and tooth portion 6: Rubber with a known composition based on neoprene rubber. however,
Rubber hardness is 70° (according to JISA). (iv) Canvas layer 7: Plain weave, twill weave, or satin weave fabric using nylon 6 or nylon 66, which has been subjected to a known adhesive treatment. Next, a method for manufacturing the toothed belt 1 will be briefly described. (Step 1) An upper rubber and a lower rubber are laminated around a tensile material such as Kepler cord, and press vulcanization is performed. (Step 2) Buff the lower rubber to remove it up to the bottom of the Kepler cord. (Step 3) Apply neoprene rubber glue to the polished surface by buffing, and create an unvulcanized rubber sheet that will become the buffer rubber layer 4 and another unvulcanized rubber sheet that will become the teeth 6 (tooth rubber).
The canvas that will become the canvas layer 7 is attached in order and wound up into a roll. (Step 4) The formed sheet wound up into a roll is pulled out, and sent and baked using a press device equipped with a toothed mold. (Step 5) After vulcanization, cut the width if necessary. Thus, a toothed belt 1 is formed. According to the above configuration, the tooth rubber constituting the tooth portion 6 has a relatively soft rubber hardness of 65° to 80°;
Since the tooth height is as low as 0.2 to 0.3 with respect to the tooth width, when power is received from the tensile layer 3 to the teeth 6, or vice versa, when power is transmitted from the teeth 6 to the tensile layer 3. Since the tooth rubber is soft, the amount of deformation of the tooth portion 6 is relatively small. Therefore, high load transmission is possible. In addition, since the tooth portion 6 is supported by the tensile layer 3 via the buffer rubber layer 4, the impact force (particularly shearing force) acting on the tooth portion 6 during high load use is absorbed by the buffer rubber layer. The layer 4 also provides a buffer and can reduce the wear of the teeth 6. On the other hand, since the tooth rubber that makes up the tooth portion 6 is relatively soft with a rubber hardness of 65° to 80°, even if the hardness increases due to compression during use, its absolute value does not increase so much, so the rubber elasticity can be maintained for a long time. It will be held for a long time. As a result, cracking due to hardening is less likely to occur under high temperature and high load conditions, and it can be used for a long time. In addition, a buffer rubber layer 4 is interposed between the tensile layer 3 and the canvas layer 7, which has a rubber hardness equal to or lower than tooth rubber and also serves as an adhesive for the tensile layer 3. , when used under high load conditions, the teeth 6,
Even if the trough 8 between the two spaces 6 is pushed up by the peak 10 of the pulley 9, the pushing up force is effectively reduced by the buffer rubber layer 4, thereby reducing wear and tear on the canvas layer 7 (canvas). This leads to longer life under high load conditions (see Figure 6). That is, in the troughs of the toothed belt, in the conventional toothed belt a, the hard cords b of the tensile layer and the canvas c were in direct contact, so as shown in FIG. is subjected to concentrated loads, and wear progresses in that portion in the longitudinal direction of the cord, leading to belt breakage.However, in the toothed belt 1 according to the present invention, the buffer rubber layer 4 has a tensile strength between the canvas layer 7 and the belt. Since there is no direct contact with the body layer 3 and the load is borne almost uniformly over the entire belt width as shown in FIG. 7, local abnormal wear of the canvas layer 7 does not occur. It does not lead to damage. Next, an experiment conducted using the toothed belt 1 will be explained. (Experiment 1) Typical conventional toothed belt (see Table 1) and this belt
【表】【table】
【表】
上記実験の結果を次の表２に示す。表２におい
て、V5は本発明に係る歯付ベルトを示し、ベル
ト寿命は、本発明に係る歯付ベルトV5を100とし
て基準とし、指数表示した。[Table] The results of the above experiment are shown in Table 2 below. In Table 2, V 5 indicates the toothed belt according to the present invention, and the belt life is expressed as an index with the toothed belt V 5 according to the present invention as a standard as 100.
【表】
上記結果より、本発明に係る歯付ベルトは、従
来の歯付ベルトに比して、ほぼ50％以上もベルト
寿命が延びていることが判る。
（実験２）
本発明に係る歯付ベルトについて、ｈ／ｌ
（ｈ：歯高さ、ｌ：歯幅）とベルト寿命との関係
を調べた。本実験に用いた歯付ベルトは、ｈ／ｌ
の値を除けば、基本的には（実験１）において用
いた本発明に係る歯付ベルトと同一である。な
お、ｈ／ｌの変化は、歯幅ｌを一定値に固定して
歯高さｈを変化させることにより行つている。
(i) ベルト寿命は歯部のゴム硬度が60゜、65゜、
70゜、75゜、80゜のものについて行い、そのベルト
寿命の評価は、（実験１）と同様に行つた。
(ii) 帆布摩耗量は、実験開始前における歯付ベル
トの歯部平坦部の帆布層の厚さを100とし、（実
験１）と同一の方法で一定時間走行後、前記歯
部平坦部の厚さを、顕微鏡を用いて計測し、そ
の減少量を摩耗量として指数で表示した。
(iii) 歯部の変形量は、第３図に示すように、アム
スラー型万能試験機の加重部材２１に歯付ベル
ト１を噛合させるとともに該歯付ベルト１の背
面側を添え板２２（金属片）に支持し、しかし
て所定の荷重Ｗを加重部材２１を介して歯付ベ
ルト１の歯部６に加えて、歯先部分の変位量
ΔAを測定した。それによつて、Ｐ＝（ΔA／
Ｓ）×100（％）でもつて変形量とした。ここで、
Ｓは歯部平坦部の幅である。
かくして得られた結果を、第２図に示す。これ
により、ｈ／ｌが大きくなるにしたがつて、帆布
の摩耗量は減少する一方、歯部の変形量は増加す
る。また、ベルト寿命は、歯ゴム硬度が65゜〜80゜
のものにおいてｈ／ｌが0.20〜0.30の範囲におい
て十分に大きくなることが判る。
（実験３）
本発明に係る歯付ベルトにおいて、歯部を構成
する歯ゴムの硬度とベルト寿命との関係とを調べ
た。本実験に用いた本発明に係る歯付ベルト（た
だし、ｈ／ｌ＝0.28）と、実験（走行）条件と
は、（実験１）と同一で行つた。
その実験結果を、第４図に示す。これにより、
歯ゴムの硬度が70゜付近でベルト寿命はピークと
なり、その硬度が65゜〜80゜（好ましくは、68゜〜
72゜）の範囲にあることが、ベルト寿命の点から
望ましいといえる。なお、前記歯ゴムの硬度が
65゜以下のときには、歯飛び現象が生ずる一方、
硬度が80゜以上のときには熱劣化による歯ゴムの
割れ現象が生ずる。
（実験４）
本発明に係る歯付ベルトにおいて、緩衝ゴム層
の厚さΔtとベルト寿命との関係について調べた。
本実験に用いた本発明に係る歯付ベルト（ただ
し、ｈ／ｌ＝0.28）と、実験（走行）条件とは、
（実験１）と同一にして行つた。
その実験結果を、第５図に示す。これにより、
緩衝ゴム層の厚さΔtはベルト寿命の点から、0.95
mm〜2.75mm、換言すれば歯高さｈの13％〜37％の
範囲にあることが望ましいことが判る。これは、
緩衝ゴム層が、それに荷重が加わつた状態で、プ
ーリのピツチ径と外径との差の1/2（PLD）の範
囲内の厚さで使用すると効果があると考えられ
る。
（発明の効果）
本発明は上記のように構成したから、高温高負
荷条件下においても、歯部の変形量及び摩耗量が
少なく、かつ帆布の摩耗量が少ないとともに、歯
ゴムの熱劣化による割れも生じ難いので、高温高
負荷条件下のベルト寿命が著しく向上した歯付ベ
ルトを提供できるという実用上優れた効果を有す
る。[Table] From the above results, it can be seen that the toothed belt according to the present invention has a belt life that is approximately 50% longer than that of the conventional toothed belt. (Experiment 2) Regarding the toothed belt according to the present invention, h/l
The relationship between (h: tooth height, l: tooth width) and belt life was investigated. The toothed belt used in this experiment was h/l
Except for the value of , it is basically the same as the toothed belt according to the present invention used in (Experiment 1). Note that h/l is changed by fixing the tooth width l to a constant value and changing the tooth height h. (i) Belt life depends on the rubber hardness of the teeth being 60°, 65°,
The belt life was evaluated in the same manner as in (Experiment 1). (ii) The amount of canvas wear is calculated by assuming that the thickness of the canvas layer on the flat part of the teeth of the toothed belt before the start of the experiment is 100, and after running for a certain period of time in the same manner as in (Experiment 1). The thickness was measured using a microscope, and the amount of reduction was expressed as an index as the amount of wear. (iii) To determine the amount of deformation of the toothed portion, as shown in FIG. A predetermined load W was applied to the toothed portion 6 of the toothed belt 1 via the weighting member 21, and the displacement ΔA of the tooth tip portion was measured. Thereby, P=(ΔA/
The amount of deformation was also expressed as S) x 100 (%). here,
S is the width of the tooth flat part. The results thus obtained are shown in FIG. As a result, as h/l increases, the amount of wear on the canvas decreases, while the amount of deformation of the teeth increases. Further, it can be seen that the belt life is sufficiently increased when h/l is in the range of 0.20 to 0.30 for tooth rubber hardness of 65° to 80°. (Experiment 3) In the toothed belt according to the present invention, the relationship between the hardness of the tooth rubber constituting the tooth portion and the belt life was investigated. The toothed belt (h/l=0.28) according to the present invention used in this experiment and the experimental (running) conditions were the same as in (Experiment 1). The experimental results are shown in FIG. This results in
The belt life reaches its peak when the hardness of the tooth rubber is around 70°, and when the hardness is between 65° and 80° (preferably between 68° and
72°) is desirable from the viewpoint of belt life. In addition, the hardness of the tooth rubber is
When the angle is less than 65°, tooth skipping phenomenon occurs, while
When the hardness is 80° or more, cracking of the tooth rubber occurs due to thermal deterioration. (Experiment 4) In the toothed belt according to the present invention, the relationship between the thickness Δt of the buffer rubber layer and the belt life was investigated.
The toothed belt (h/l=0.28) according to the present invention used in this experiment and the experimental (running) conditions are as follows:
The experiment was conducted in the same manner as (Experiment 1). The experimental results are shown in FIG. This results in
The thickness Δt of the buffer rubber layer is 0.95 from the viewpoint of belt life.
It can be seen that it is desirable that the height be in the range of mm to 2.75 mm, in other words, 13% to 37% of the tooth height h. this is,
It is thought to be effective if the buffer rubber layer is used with a thickness within the range of 1/2 (PLD) of the difference between the pitch diameter and the outside diameter of the pulley when a load is applied to it. (Effects of the Invention) Since the present invention is constructed as described above, even under high temperature and high load conditions, the amount of deformation and abrasion of the tooth portion is small, the amount of abrasion of the canvas is small, and the thermal deterioration of the tooth rubber Since cracks are less likely to occur, it has the practical effect of providing a toothed belt with significantly improved belt life under high temperature and high load conditions.
第１図は本発明の実施例の歯付ベルトの断面
図、第２図はｈ／ｌと、ベルト寿命、歯部変形量
及び帆布摩耗量との関係を示すグラフ、第３図は
歯部変形量の側定系の説明図、第４図は歯ゴム硬
度とベルト寿命との関係を示すグラフ、第５図は
緩衝ゴム層とベルト寿命との関係を示すグラフ、
第６図は本発明に係る歯付ベルトと歯付プーリと
の噛合状態を示す説明図、第７図及び第８図はそ
れぞれ本発明に係る歯付ベルト及び従来の歯付ベ
ルトに対し歯付プーリより加わる荷重状態を示す
説明図である。
１……歯付ベルト、２……背ゴム層、３……抗
張体層、４……緩衝ゴム層、５……ベルト基帯、
６……歯部、７……帆布層。
Fig. 1 is a cross-sectional view of a toothed belt according to an embodiment of the present invention, Fig. 2 is a graph showing the relationship between h/l, belt life, tooth deformation amount, and canvas wear amount, and Fig. 3 is a graph showing the relationship between h/l, belt life, tooth deformation amount, and canvas wear amount. An explanatory diagram of the side-determined system of the amount of deformation, Fig. 4 is a graph showing the relationship between tooth rubber hardness and belt life, Fig. 5 is a graph showing the relationship between the buffer rubber layer and belt life,
FIG. 6 is an explanatory diagram showing the meshing state of the toothed belt according to the present invention and the toothed pulley, and FIGS. 7 and 8 are diagrams showing the toothed belt according to the present invention and the conventional toothed belt, respectively. FIG. 3 is an explanatory diagram showing a state of a load applied from a pulley. 1... Toothed belt, 2... Back rubber layer, 3... Tensile layer, 4... Buffer rubber layer, 5... Belt base band,
6...Tooth portion, 7...Canvas layer.
Claims (1)
ルト状のベルト基帯の該抗張体層側の面にほぼ一
定の厚さの緩衝ゴムシートが接合され、該緩衝ゴ
ムシートの表面に歯部を構成する複数の歯ゴムが
ベルト全周に亘つて等ピツチ間隔で接合され、更
に該歯ゴムの表面及び歯ゴム間の緩衝ゴムシート
の表面に沿つて帆布が貼付されてなり、 上記歯ゴムよりなる歯部はそのゴム硬度が65゜
〜80゜の範囲になるように設定され、 上記緩衝ゴムシートよりなる緩衝ゴム層はその
ゴム硬度が上記歯部のゴム硬度と同等もしくはそ
れ以下に、かつその厚さが上記歯部の高さの13〜
37％の範囲になるように設定され、 上記歯部は、その歯高さｈと歯幅ｌとの関係が ｈ／ｌ＝0.20〜0.30 の範囲になるように形成されていることを特徴と
する歯付ベルト。[Scope of Claims] 1. A cushioning rubber sheet having a substantially constant thickness is bonded to the surface of a flat belt base belt formed by laminating a back rubber layer and a tensile layer on the tensile layer side. , a plurality of toothed rubbers constituting toothed portions are joined to the surface of the buffer rubber sheet at equal pitch intervals along the entire circumference of the belt, and further along the surface of the toothed rubber sheets and the surface of the buffer rubber sheet between the toothed rubbers. The canvas is attached, and the tooth portion made of the tooth rubber is set so that its rubber hardness is in the range of 65° to 80°, and the rubber hardness of the buffer rubber layer made of the buffer rubber sheet is set to be in the range of 65° to 80°. The hardness of the rubber is equal to or lower than the hardness of the rubber, and the thickness is 13 to
37%, and the tooth portion is formed so that the relationship between the tooth height h and the tooth width l is in the range h/l = 0.20 to 0.30. Toothed belt.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17203282A JPS5962748A (en) | 1982-09-29 | 1982-09-29 | Toothed belt |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17203282A JPS5962748A (en) | 1982-09-29 | 1982-09-29 | Toothed belt |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5962748A JPS5962748A (en) | 1984-04-10 |
| JPH0222253B2 true JPH0222253B2 (en) | 1990-05-17 |
Family
ID=15934261
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17203282A Granted JPS5962748A (en) | 1982-09-29 | 1982-09-29 | Toothed belt |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5962748A (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5337851B2 (en) * | 1973-10-09 | 1978-10-12 | ||
| JPS56120847A (en) * | 1980-02-28 | 1981-09-22 | Yunitsuta Kk | Toothed belt |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5755560Y2 (en) * | 1976-09-08 | 1982-12-01 |
-
1982
- 1982-09-29 JP JP17203282A patent/JPS5962748A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5337851B2 (en) * | 1973-10-09 | 1978-10-12 | ||
| JPS56120847A (en) * | 1980-02-28 | 1981-09-22 | Yunitsuta Kk | Toothed belt |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5962748A (en) | 1984-04-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR880001745B1 (en) | Toothed positive drive power transmission belt with fabric reinforcement suspended within the belt teeth | |
| CA1202199A (en) | Toothed belt | |
| JP2562112B2 (en) | V-ribbed belt and grinder wheel for V-ribbed belt | |
| EP0176686A2 (en) | V-Belt | |
| WO2014030747A1 (en) | Conveyor belt | |
| CN101245827B (en) | Two-sided transmission unit belt | |
| US9677643B2 (en) | Notched transmission belt | |
| JPH0222253B2 (en) | ||
| US2071563A (en) | Abrading apparatus | |
| JP6007045B2 (en) | V-belt for transmission | |
| JP4995930B2 (en) | Toothed belt | |
| JP2005530098A (en) | Multi-rib belt with tip cross-sectional shape | |
| CN210265679U (en) | E-shaped combined belt | |
| JP3806495B2 (en) | V belt for high load transmission | |
| CN202484196U (en) | Base rubber and fabric combined V belt | |
| JPH0518514Y2 (en) | ||
| JPH0450250Y2 (en) | ||
| EP4004400B1 (en) | Center cord-line v-belt | |
| CN218207624U (en) | Wear-resistant synchronous belt | |
| CN219529702U (en) | Trimming type combined transmission belt | |
| JP4965775B2 (en) | Corrugated side conveyor belt | |
| CN214213472U (en) | Abrasive belt with three-dimensional reinforcing structure | |
| KR101385138B1 (en) | Steel cord for reinforcement of a tire | |
| JP2001263431A (en) | Low edge cog belt | |
| JP2529695Y2 (en) | V-ribbed belt |