JPS6142136B2 - - Google Patents
Info
- Publication number
- JPS6142136B2 JPS6142136B2 JP57172033A JP17203382A JPS6142136B2 JP S6142136 B2 JPS6142136 B2 JP S6142136B2 JP 57172033 A JP57172033 A JP 57172033A JP 17203382 A JP17203382 A JP 17203382A JP S6142136 B2 JPS6142136 B2 JP S6142136B2
- Authority
- JP
- Japan
- Prior art keywords
- belt
- toothed
- toothed belt
- teeth
- layer
- 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
Links
- 229920001971 elastomer Polymers 0.000 claims description 28
- 239000010410 layer Substances 0.000 description 32
- 238000002474 experimental method Methods 0.000 description 11
- 230000000694 effects Effects 0.000 description 7
- 230000005540 biological transmission Effects 0.000 description 4
- 239000002344 surface layer Substances 0.000 description 3
- 239000004809 Teflon Substances 0.000 description 2
- 229920006362 Teflon® Polymers 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive 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
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 238000004898 kneading Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 229920001084 poly(chloroprene) Polymers 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000002195 synergetic effect Effects 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
- 238000012360 testing method Methods 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
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/02—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts
- F16H7/023—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts with belts having a toothed contact surface or regularly spaced bosses or hollows for slipless or nearly slipless meshing with complementary profiled contact surface of a pulley
-
- 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)
- Gears, Cams (AREA)
- Pulleys (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Description
本発明は主として高負荷用歯付ベルト駆動装置
の改良に関するものである。
従来、高負荷伝動装置において、歯付ベルトが
使用されているが、非常な高負荷条件下、例え
ば、
負荷：ベルト１本当り6t〜10t
での使用であるため、歯付ベルト、特に歯部の摩
耗が著しいという欠点があつた。
そこで、前述したような高負荷に対抗するため
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を大きくす
るために歯部を大きくする、つまり歯部を高
く、歯幅を大きく、かつベルト幅を広くする、
(ii) 歯部に均一な圧力が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、(b)歯部の帆布の組織を
耐摩耗性とする、あるいは帆布を多数重積す
る、(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、
(iv) 歯部の摩擦係数を小さくする。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、
などの手法がある。
したがつて、歯付ベルトの使用条件に応じて、
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。
それによつて、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、短時間で歯ゴムが硬化し
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
示す歯付ベルト駆動装置を提供することを主目的
とする。
以下、本発明の構成を、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、抗張体層３および緩衝ゴム層４が順に積層さ
れてなるベルト基帯５の該緩衝ゴム層４側に、歯
部６がベルト全周に亘つて規則的に配設され、そ
の上に帆布層７が重積されてなる。したがつて、
歯部６においては勿論、谷部８においても帆布層
７と抗張体層３との間には緩衝ゴム層４が介在し
ていることになる。
なお、ベルト寿命において有利になるように、
歯部６は、歯部高さｈと歯部長さｌとの比が0.15
〜0.35（好ましくは0.27〜0.29）で、歯ゴム硬度
（JISAによる）が65゜〜75゜（好ましくは68゜〜
72゜）となるように形成されている。また、緩衝
ゴム層４についても、ベルト寿命において有利と
なるように、そのゴム硬度が歯ゴム硬度と同一若
しくはそれ以下であつてそれらの相対硬度差が15
゜以内であるとともに、その厚さΔｔが歯部高さ
ｈの13％〜17％に相当するようになつている。
前記歯付ベルト１が回転自在に懸回する歯付プ
ーリ９は、その外表面に摩擦係数の低い合成樹脂
（例えばテフロン）による表面薄層を有する。ま
た、歯付ベルト１の歯部６と噛合する凹溝１０の
深さＤが歯部深さｈによりも若干大きくなるよう
に、換言すれば歯部６の歯先と凹溝１０の底面と
の間に空間１１が存するように構成されている。
その空間１１は、深さ方向の長さΔｄが静止状態
で歯部高さｈの０〜５％の範囲となつており、そ
の値は歯付ベルト１の緩衝ゴム層４のゴム硬度を
考慮して設定される。
それによつて、静止状態において存在する空間
１１が、負荷状態では歯付ベルト１の緩衝ゴム層
４が圧縮変形されるので、消滅して歯部６の歯先
と凹溝１０の底面と接触することになる。
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
The present invention primarily relates to improvements in high-load toothed belt drive devices. Conventionally, toothed belts have been used in high-load transmission devices, but since they are used under very high load conditions, e.g., a load of 6t to 10t per belt, toothed belts, especially the toothed parts, The disadvantage was that there was significant wear. 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. Specifically, (i) the teeth are made larger in order to increase the pressure-receiving area per unit of transmitted load; that is, the teeth are made higher, the tooth width is made larger, and the belt width is made wider; (ii) To ensure that even pressure is distributed and applied to the teeth,
Smooth meshing by 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, (c) making the pulley groove more (iv) To reduce the coefficient of friction of the teeth by increasing the size of the belt teeth, thereby compressing the belt teeth in the pulley groove and increasing the rigidity. For example, there are methods such as adding anti-friction agents, lubricants, etc. to the contact interface with the pulley. 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. Therefore, in the case of high-load transmission at room temperature,
Although some effect was observed, in the case of high-load transmission with high ambient temperature, the tooth rubber hardened and cracked in a short period of time, and the tooth cloth was severely worn, making the effect less than satisfactory. The current situation is that we are not getting it. The present invention has been made in view of these points, and its main object is to provide a toothed belt drive device that exhibits a sufficient belt life even under high temperature and high load conditions. DESCRIPTION OF THE PREFERRED EMBODIMENTS The configuration of the present invention will be described below with reference to the drawings. In FIG. 1, reference numeral 1 denotes a toothed belt, and a toothed portion 6 is provided on the side of the buffer rubber layer 4 of a belt base band 5, which is made up of a back rubber layer 2, a tensile layer 3, and a buffer rubber layer 4 laminated in this order. They are arranged regularly over the entire circumference of the belt, and the canvas layer 7 is stacked thereon. Therefore,
The buffer rubber layer 4 is interposed between the canvas layer 7 and the tensile layer 3 not only in the tooth portion 6 but also in the trough portion 8 . In addition, in order to be advantageous in belt life,
The tooth portion 6 has a ratio of tooth height h to tooth length l of 0.15.
~0.35 (preferably 0.27~0.29), tooth rubber hardness (according to JISA) of 65°~75° (preferably 68°~
72°). Also, regarding the buffer rubber layer 4, in order to be advantageous in terms of belt life, its rubber hardness is the same as or lower than the tooth rubber hardness, and the relative hardness difference between them is 15.
The thickness Δt corresponds to 13% to 17% of the tooth height h. The toothed pulley 9 around which the toothed belt 1 is rotatably suspended has a thin surface layer made of a synthetic resin (for example, Teflon) having a low coefficient of friction on its outer surface. In addition, the depth D of the groove 10 that meshes with the teeth 6 of the toothed belt 1 is slightly larger than the depth h of the teeth, in other words, the tips of the teeth 6 and the bottom of the groove 10 are It is configured such that a space 11 exists between them.
The length Δd of the space 11 in the depth direction is in the range of 0 to 5% of the tooth height h in a stationary state, and this value takes into account the rubber hardness of the buffer rubber layer 4 of the toothed belt 1. is set. As a result, the space 11 that exists in a static state disappears because the buffer rubber layer 4 of the toothed belt 1 is compressed and deformed in a loaded state, and comes into contact with the tips of the teeth 6 and the bottom surface of the groove 10. It turns out. Examples of materials for each part of the toothed belt 1 are as follows. (i) Back rubber layer 2......Based on neoprene rubber.
【表】
上記実験の結果を次の表に示す。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 the following table. 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
寿命が延びいていることが判る。
（実験２）
本発明に係る歯付ベルトについて、ｈ／ｌ
（ｈ：歯部高さ、ｌ：歯部長さ）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を同一であ
る。なお、ｈ／ｌの変化は、歯部の長さｌを一定
に固定させ歯部の高さ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、実験開始時における歯付ベル
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を噛合す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
は歯部平坦部の長さである。
かくして得られた結果を、第２図に示す。これ
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、歯部の形量は増加する。
また、ベルト寿命は、ｈ／ｌのある範囲におい
て、十分に大きくなることが判る。
したがつて、ｈ／ｌは、0.15〜0.35の範囲、望
ましくは0.27〜0.29の範囲にあることがよいと言
える。
（実験３）
本発明に係る歯付ベルトV5もしくは従来の歯
付ベルトV1と、使用時に歯部歯先と凹溝底面と
の間に空間が存する従来の歯付プーリP1、使用時
に前記空間が存しない従来の歯付プーリP2、使用
時に前記空間が存する本発明に係る歯付プーリP3
もしくは使用時に前記空間が存しない本発明に係
る歯付プーリP4との組合せによる、ベルト寿命へ
の影響を調べた。なお、実験に用いた歯付ベルト
および走行条件は（実験１）と同一とし、歯付ベ
ルトV5と歯付プーリP1とを組合せたときのベル
ト寿命を100として指数表示した。
その実験結果が、表３である。[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 length) and belt life was investigated. The toothed belt used in this experiment was
The toothed belt according to the present invention used in (Experiment 1) is basically the same except for the value of h/l. Note that h/l is changed by fixing the length l of the tooth portion constant and changing the height h of the tooth portion. (i) Evaluation of belt life was performed 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 toothed belt at 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 of the canvas layer on the flat part of the toothed belt at the start of the experiment is Measure the thickness using a microscope,
The amount of decrease was expressed as an index as the amount of wear. (iii) The amount of deformation of the toothed portion is determined by meshing the toothed belt 1 with the weighting member 21 of the Amsler type universal testing machine and attaching the back side of the toothed belt 1 to the splint plate 22 (metallic A predetermined load W is applied to the tooth portion 6 of the toothed belt 1 via the weighting member 21, and the displacement amount ΔA of the tooth tip portion is
was measured. Thereby, P=(ΔA/S)
Even 100 (%) was taken as the amount of deformation. Here, S
is the length of the flat part of the tooth. The results thus obtained are shown in FIG. From this, as h/l increases, the amount of wear on the canvas decreases, while the amount of shape of the tooth portion increases.
Further, it can be seen that the belt life becomes sufficiently long within a certain range of h/l. Therefore, it can be said that h/l is preferably in the range of 0.15 to 0.35, preferably in the range of 0.27 to 0.29. (Experiment 3) The toothed belt V 5 according to the present invention or the conventional toothed belt V 1 and the conventional toothed pulley P 1 in which a space exists between the tooth tips of the teeth and the bottom surface of the concave groove when in use. A conventional toothed pulley P 2 in which the space does not exist, and a toothed pulley P 3 according to the present invention in which the space exists during use.
Alternatively, the influence on the belt life was investigated in combination with the toothed pulley P4 according to the present invention in which the space does not exist during use. The toothed belt and running conditions used in the experiment were the same as (Experiment 1), and the belt life when toothed belt V 5 and toothed pulley P 1 were combined was expressed as an index of 100. Table 3 shows the experimental results.
【表】
したがつて、本発明に係る歯付ベルト駆動装置
に対応する組合せである（V5＋P3）では、著しく
ベルト寿命が向上することが判る。
上記構成によれば、歯付ベルト１の歯部６を構
成する歯ゴムは比較的軟かい歯部６の幅に対して
高さが低いので、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、歯ゴムが軟らかい割に歯
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。
一方、歯部６を構成する歯ゴムが比較的軟らか
いと、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、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、抗張
体層３の接着を兼ねた緩衝ゴム層４が介設されて
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が歯付プーリの山部１２によ
つて突上げられても、緩衝ゴム層４の圧縮変形に
よつて突上げ力は効果的に低減される。また、こ
の緩衝ゴム層４による突上げ力の低減効果と、歯
付プーリ９の表面薄層（テフロン）による摩擦力
の低減効果との相乗作用によつて、帆布層７（帆
布）の摩耗も著しく低減されることとなり、ベル
ト寿命は著しく延びる。
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とが直接に接触していたので、第５図に示
すように、その接触部分で集中的に荷重を受け、
それによつてコード長手方向にその部分だけ摩耗
が進展してベルト破損に至つていたのに対し、本
発明に係る歯付ベルト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４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とともに、歯付プーリ９の
表面薄層によつて摩擦力が低減されるので、帆布
層７の局所的な異常摩耗が惹起されず、したがつ
てベルト破損が防止される。
なお、本発明に係る歯付ベルトは、上述したこ
とから明らかなように、従来のプーリと組合せて
用いても十分な効果を発揮するが、本発明に係る
歯付プーリと組合せることにより、より一層優れ
た効果を発揮することになるのは言うまでもな
い。
本発明は上記のように構成したから、高負荷高
温条件下におけるベルト寿命が著しく向上すると
いう実用上優れた効果を有する。[Table] Therefore, it can be seen that the belt life is significantly improved in the combination (V 5 +P 3 ) corresponding to the toothed belt drive device according to the present invention. According to the above configuration, the tooth rubber constituting the tooth portion 6 of the toothed belt 1 is relatively soft and has a lower height than the width of the tooth portion 6, so power is applied to the tooth portion 6 from the tensile layer 3. When power is received or conversely transmitted from the toothed portion 6 to the tensile layer 3, the amount of deformation of the toothed portion 6 is relatively small since the toothed rubber is soft. Therefore, high load transmission is possible. On the other hand, if the tooth rubber constituting the tooth portion 6 is relatively soft, even if the hardness increases due to compression during use, its absolute value will not increase so much, so the rubber elasticity will be maintained for a long time. the result,
Can be used for long periods of time under high temperature and high load conditions. In addition, a buffer rubber layer 4 is interposed between the tensile layer 3 and the canvas layer 7, which also serves as adhesive for the tensile layer 3, so that when used under high load conditions, the tooth 6,
Even if the valley portion 8 between the grooves 6 is pushed up by the peak portion 12 of the toothed pulley, the pushing up force is effectively reduced by the compressive deformation of the buffer rubber layer 4. In addition, the wear of the canvas layer 7 (canvas) is also reduced due to the synergistic effect of the uplifting force reduction effect of the buffer rubber layer 4 and the friction force reduction effect of the toothed pulley 9's thin surface layer (Teflon). This results in a significant reduction, and the belt life is significantly extended. That is, in the troughs of the toothed belt, in the conventional toothed belt a, the hard cord b of the tensile layer and the canvas c were in direct contact, so as shown in FIG. The load is concentrated on some parts,
As a result, wear progresses in that portion in the longitudinal direction of the cord, leading to belt breakage.In contrast, in the toothed belt 1 according to the present invention, the buffer rubber layer 4 allows the canvas layer 7 to There is no direct contact with the layer 3, and as shown in FIG. 4, the load is borne almost uniformly over the entire width of the belt, and the frictional force is reduced by the thin surface layer of the toothed pulley 9. , local abnormal wear of the canvas layer 7 is not caused, and therefore belt damage is prevented. As is clear from the above, the toothed belt according to the present invention exhibits sufficient effects even when used in combination with conventional pulleys, but when combined with the toothed pulley according to the present invention, Needless to say, the effect will be even better. Since the present invention is configured as described above, it has a practically excellent effect of significantly improving the belt life under high load and high temperature conditions.
第１図は本発明に係る歯付ベルト駆動装置の基
本構成を示す断面図、第２図はｈ／ｌ（ｈ：歯部
高さ、ｌ：歯部長さ）と、ベルト寿命、歯部変形
量および帆布摩耗量との関係を示すグラフ、第３
図は歯部変形量の測定系の説明図、第４図および
第５図はそれぞれ本発明に係る歯付ベルトおよび
従来の歯付ベルトに対し歯付プーリより加重状態
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、９……歯付プーリ、
１０……凹溝、１１……空間。
Fig. 1 is a sectional view showing the basic configuration of a toothed belt drive device according to the present invention, and Fig. 2 shows h/l (h: tooth height, l: tooth length), belt life, and tooth deformation. Graph showing the relationship between the amount and the amount of canvas wear, 3rd
The figure is an explanatory diagram of a measurement system for the amount of deformation of a toothed portion, and FIGS. 4 and 5 are explanatory diagrams showing states of loading by a toothed pulley on a toothed belt according to the present invention and a conventional toothed belt, respectively. 1... Toothed belt, 2... Back rubber layer, 3... Tensile layer, 4... Buffer rubber layer, 5... Belt base band,
6...Tooth portion, 7...Canvas layer, 9...Toothed pulley,
10...concave groove, 11...space.
Claims (1)
れてなる駆動装置であつて、前記歯付ベルトは、
背ゴム層、抗張体層および緩衝ゴム層が順に積層
されてなるベルト基帯の該緩衝ゴム層側に歯部が
ベルト全周に亘つて規則的に配設され、さらにそ
の上に帆布層が重積され、前記歯部がその高さｈ
と長さｌとの関係がｈ／ｌ＝0.15〜0.35でゴム硬
度が65゜〜75゜になるように構成される一方、前
記歯付プーリは、外表面に摩擦係数の低い合成樹
脂による表面薄層を有するとともに、歯付ベルト
の歯部と噛合する凹溝の深さが歯付ベルトの歯部
の高さｈよりも若干大きくなるように構成され、
それによつて歯付ベルトに負荷が加わつたとき、
歯付ベルトの歯部歯先が歯付プーリの凹溝底面に
接触することを特徴とする歯付ベルト駆動装置。1. A drive device in which a toothed belt is rotatably suspended around a toothed pulley, the toothed belt comprising:
A back rubber layer, a tensile layer, and a buffer rubber layer are laminated in this order, and teeth are regularly arranged around the entire belt circumference on the buffer rubber layer side of the belt base band, and a canvas layer is further provided on the belt base band. are piled up, and the tooth portion has a height h
The toothed pulley is constructed so that the relationship between h/l and the length l is 0.15 to 0.35, and the rubber hardness is 65° to 75°. It has a thin layer and is configured such that the depth of the groove that engages with the teeth of the toothed belt is slightly larger than the height h of the teeth of the toothed belt,
When a load is applied to the toothed belt due to this,
A toothed belt drive device characterized in that the tips of the teeth of the toothed belt come into contact with the bottom surface of the groove of the toothed pulley.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17203382A JPS5962757A (en) | 1982-09-29 | 1982-09-29 | Toothed belt drive device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17203382A JPS5962757A (en) | 1982-09-29 | 1982-09-29 | Toothed belt drive device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5962757A JPS5962757A (en) | 1984-04-10 |
| JPS6142136B2 true JPS6142136B2 (en) | 1986-09-19 |
Family
ID=15934280
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17203382A Granted JPS5962757A (en) | 1982-09-29 | 1982-09-29 | Toothed belt drive device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5962757A (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5276571A (en) * | 1975-12-18 | 1977-06-28 | Goodyear Tire & Rubber | Transmission belt and pulley |
| JPS578981A (en) * | 1980-06-20 | 1982-01-18 | Fujitsu Ltd | Magnetic bubble memory device |
| JPS5716048B2 (en) * | 1979-11-08 | 1982-04-02 |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55113852U (en) * | 1979-02-07 | 1980-08-11 | ||
| JPS5716048U (en) * | 1980-06-30 | 1982-01-27 |
-
1982
- 1982-09-29 JP JP17203382A patent/JPS5962757A/en active Granted
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5276571A (en) * | 1975-12-18 | 1977-06-28 | Goodyear Tire & Rubber | Transmission belt and pulley |
| JPS5716048B2 (en) * | 1979-11-08 | 1982-04-02 | ||
| JPS578981A (en) * | 1980-06-20 | 1982-01-18 | Fujitsu Ltd | Magnetic bubble memory device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5962757A (en) | 1984-04-10 |
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