JPS6126659Y2 - - Google Patents
Info
- Publication number
- JPS6126659Y2 JPS6126659Y2 JP1982058728U JP5872882U JPS6126659Y2 JP S6126659 Y2 JPS6126659 Y2 JP S6126659Y2 JP 1982058728 U JP1982058728 U JP 1982058728U JP 5872882 U JP5872882 U JP 5872882U JP S6126659 Y2 JPS6126659 Y2 JP S6126659Y2
- Authority
- JP
- Japan
- Prior art keywords
- belt
- pulley
- teeth
- center
- tooth
- 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
- 230000005540 biological transmission Effects 0.000 description 5
- 238000005336 cracking Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
Landscapes
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
- Gears, Cams (AREA)
- Pulleys (AREA)
Description
【考案の詳細な説明】
本考案は歯付ベルトとプーリとの組合せからな
る歯付ベルトの駆動装置に係り、更に詳しくはプ
ーリ溝が実質的に１つの曲率半径を有する円弧か
ら形成されるプーリに対し、これに適応しうる所
要のベルト歯をもつ歯付ベルトを組合せベルト溝
部表面の摩耗及びベルト歯元クラツクを防止した
駆動装置に関するものである。[Detailed Description of the Invention] The present invention relates to a toothed belt drive device consisting of a combination of a toothed belt and a pulley, and more specifically to a pulley in which the pulley groove is formed from an arc having substantially one radius of curvature. On the other hand, the present invention relates to a drive device which combines a toothed belt with required belt teeth that can be adapted to this, thereby preventing wear on the surface of the belt groove and cracking of the belt teeth.
歯付ベルトは、平ベルトやＶベルトと異なり、
すべりの無い確実伝動が可能であり、又歯車やチ
エーンの確実伝動に比べて給油を必要としない等
の利点を有しているため、近年、その需要が急激
に増大ししきた。 Toothed belts are different from flat belts and V-belts,
In recent years, demand has increased rapidly because it enables reliable transmission without slippage and does not require lubrication compared to reliable transmission using gears or chains.
今日、一般に使用されている歯付ベルトとプー
リの組合せ体からなる駆動装置としては、RMA
（Rubber Manufactures Association）IP−24）
1978年）に定められているように、断面台形のベ
ルト歯部とその歯部と相似形のプーリとの噛み合
いによる伝動システムがある。ところがこの種の
ベルトはプーリと噛み合う場合、歪がベルト歯部
の歯元に集中し、ベルト歯部の歯先はプーリと完
全に係合した時でも歪むことが無く、ベルト歯部
は大部分不必要で本質的にほとんど荷重を受けて
いない。また、荷重はベルト歯部から抗張体へ不
均等に伝達され、かつベルト歯部の歯先がプーリ
歯側面と係合中に干渉が起る欠点が見られた。 RMA is a drive device consisting of a combination of a toothed belt and a pulley that is commonly used today.
(Rubber Manufacturers Association) IP−24)
(1978), there is a transmission system that uses belt teeth with a trapezoidal cross section and meshing pulleys with similar shapes. However, when this type of belt meshes with a pulley, the strain is concentrated at the base of the belt teeth, and the tips of the belt teeth do not become distorted even when fully engaged with the pulley, and most of the belt teeth are distorted. Unnecessary and essentially bearing little load. In addition, the load was unevenly transmitted from the belt teeth to the tensile member, and there was also the problem that interference occurred when the tips of the belt teeth engaged with the side surfaces of the pulley teeth.
かくして台形状のベルト歯部はこのような歪み
集中、荷重のベルト歯部から抗張体への不均等な
伝達及び歯の干渉を生じるため、改善が望まれて
いた。 Thus, the trapezoidal belt teeth cause such strain concentration, uneven transmission of load from the belt teeth to the tensile member, and tooth interference, so improvements have been desired.
そこで、これに対応し叙上の点を改善した装置
としてベルト歯部が互いに交差すると共にそれぞ
れ等しい半径を有する２つの円弧からなり、所定
荷重下で1/2次の等色しまの輪郭とほゞ等しい輪
郭をもつ歯付ベルトと、このベルト歯部とコンジ
ユゲートである円弧状の溝を有するプーリとを組
合せたものが提供された。 Therefore, as a device that improves the points mentioned above, the belt teeth intersect with each other and consist of two circular arcs each having the same radius. A combination of a toothed belt having the same contour and a pulley having an arcuate groove conduiting the teeth of the belt was provided.
しかしながらこの装置の大きな欠点の１つはベ
ルト歯部の歯元とプーリとのバツクラツシユが大
きく設計されているところから、ベルトの駆動開
示時、ベルトあるいはプーリの移動代が大きくな
つてベルト溝部表面はプーリにこすられて摩耗し
やすくなり、かつこのため、抗張体は痛められ、
ベルト寿命が短かくなることである。この現象は
歯付ベルトを小プーリに掛張した場合とか、逆運
転した場合には特に顕著であるが、ベルト溝部表
面がプーリ歯先に接するように設計したこともそ
の原因の１つである。 However, one of the major drawbacks of this device is that it is designed to have a large backlash between the root of the belt teeth and the pulley. The tensile body is easily rubbed against the pulley and worn out, and as a result, the tensile body is damaged.
This shortens the belt life. This phenomenon is particularly noticeable when the toothed belt is hung over a small pulley or when the belt is operated in reverse, but one of the reasons for this is that the belt groove surface is designed so that it comes into contact with the pulley tooth tip. .
また、更に上記の外、前記装置の第２の大きな
欠点はベルト歯部の歯元クラツクが短期間に生じ
ることである。即ち、歯付ベルトを駆動プーリに
平行移動して重ね合わせると、ベルトはベルト歯
部の中央部で最も大きく、ベルトの歯元及び歯元
で小さく重なるように設計されており、ベルトが
プーリから抜ける時、プーリ歯先はベルト歯側面
に対して徐々に大きな力を与えながら回転するた
め、ベルト歯元にかかる応力（抗張体と歯部を離
そうとする力）は大きくなり、歯元クラツクが生
じやすくなつたことである。 Furthermore, in addition to the above, a second major drawback of the device is that tooth root cracks of the belt teeth occur in a short period of time. In other words, when the toothed belt is moved parallel to the drive pulley and overlapped, the belt is designed so that it is largest at the center of the belt teeth and overlaps smaller at the root and root of the belt teeth, so that the belt does not move away from the pulley. When pulling out, the pulley tooth tip rotates while gradually applying a larger force to the side surface of the belt tooth, so the stress applied to the belt tooth base (the force that tries to separate the tensile body and the tooth part) increases, and the tooth base This means that cracks are more likely to occur.
かくて、以上のような点から更にその改善がひ
としく求められている。 Therefore, further improvements are equally required from the points mentioned above.
本考案はかかる状況に対処してこのような点を
改善するものであり、ベルト溝部表面の摩耗を防
止し、かつベルト歯部とプーリ歯の干渉を改善し
て早期のベルト歯元クラツクを防止した歯付ベル
トとプーリとの組合せ体を提供することを目的と
するものである。 The present invention addresses this situation and improves these points by preventing wear on the belt groove surface and improving interference between the belt teeth and pulley teeth to prevent early belt root cracks. The object of the present invention is to provide a combination of a toothed belt and a pulley.
即ち、本考案の特徴とするところは断面形状に
おいて両端部の円弧と中央部の直線部からなるプ
ーリ歯部、この歯部間に形成される１つの中心を
もつ円弧のプーリ溝部そして上記プーリ歯部とプ
ーリ溝部を連結する直線状の接合部から構成され
るプーリと、ベルト長手方向に一定ピツチで歯部
と溝部を交互に有し、ベルト歯部としてベルト歯
元を円弧の一部とし、残りの領域を少なくとも、
互いに交差するそれぞれ等しい半径を有する２つ
の円弧を含み、この領域とベルト歯元を連結する
直線状の接合部から構成されるベルト歯部を有す
る歯付ベルトからなる歯付ベルトの駆動装置にお
いて、上記プーリと歯付ベルトの寸法関係が次の
条件を満足することにある。 In other words, the features of the present invention include a pulley tooth section which is made up of circular arcs at both ends and a straight section at the center in cross-sectional shape, a pulley groove section having an arc having one center formed between the tooth sections, and the above-mentioned pulley teeth. A pulley consisting of a linear joint connecting a part and a pulley groove, and a belt having teeth and grooves alternately at a constant pitch in the longitudinal direction of the belt, with the tooth base of the belt as a part of an arc as a belt tooth, The remaining area is at least
In a drive device for a toothed belt, the toothed belt includes two circular arcs having the same radius and intersects with each other, and has a belt toothed portion composed of a straight joint portion connecting this region and a belt tooth base, The dimensional relationship between the above-mentioned pulley and toothed belt satisfies the following conditions.
１ ベルト歯部の半径をプーリ溝部の半径より大
きくすること、
２ ベルト歯部の半径の中心点がプーリ溝部の半
径の中心点よりベルト歯元側にあること、
３ ベルト歯の接合部の角度をプーリ歯の接合部
の角度より大きくすること、
しかして、上記１，２，３を満足する歯付ベル
トとプーリの寸法関係になると歯付ベルトとプー
リを噛み合せた際のベルト歯元のバツクラツシユ
が小さくなり、更にベルト歯部の先端がプーリ溝
部に当るため、ベルト走行開始時ならびにベルト
走行中においてもベルト溝部表面がプーリ歯先に
こすられて摩耗することもなくなる。また、歯付
ベルトを歯元のバツクラツシユ分だけ平行移動し
てプーリと重ね合せるとベルトはベルト歯元で最
も大きく重なるため、ベルトがプーリから抜ける
時、プーリ歯先はベルト歯側面に対して徐々に小
さな力を与えながら回転し、ベルト歯元から遠く
なるにつれて小さな力をベルト歯側面に与える。1. The radius of the belt teeth should be larger than the radius of the pulley groove. 2. The center point of the radius of the belt teeth should be closer to the root of the belt than the center point of the radius of the pulley groove. 3. The angle of the joint of the belt teeth. If the dimensional relationship between the toothed belt and the pulley satisfies 1, 2, and 3 above, then the backlash of the belt teeth when the toothed belt and the pulley are meshed will decrease. is small, and since the tips of the belt teeth come into contact with the pulley grooves, the surface of the belt grooves will not be rubbed by the pulley teeth tips and worn out even when the belt starts running and while the belt is running. In addition, if the toothed belt is moved in parallel by the amount of backlash at the root of the teeth and overlapped with the pulley, the belt will overlap most at the root of the belt teeth, so when the belt comes off the pulley, the tips of the pulley teeth will gradually move toward the sides of the belt teeth. The belt rotates while applying a small force to the belt, and as it gets farther from the belt teeth, a smaller force is applied to the sides of the belt teeth.
従つて、ベルト歯元にかかる応力は小さくな
り、歯元クラツクが生じにくくなり、所期の改善
の目的は達成される。 Therefore, the stress applied to the belt root is reduced, tooth root cracks are less likely to occur, and the intended purpose of improvement is achieved.
以下、更に本考案の具体的特徴を添付図面に示
す実施例を参照しつつ説明する。 Hereinafter, specific features of the present invention will be further explained with reference to embodiments shown in the accompanying drawings.
第１図は本考案の歯付ベルトの駆動装置に使用
するプーリの歯部を直線状に展開した断面図であ
り、プーリＡのプーリ歯部１は曲率半径r1の円弧
２で形成される両端部３，３′と、直線で形成さ
れる歯先表面部４から構成され、またこのプーリ
歯部間のプーリ溝部５は溝部の中心線６上に中心
点７を有する曲率半径r2の円径８から形成され、
この溝部の中心点７はプーリ歯両端部の円弧の中
心点９，９′と同一ライン１０上にある。従つ
て、プーリ溝部の高さＨPはr1とr2を加えたもの
であり、又、r2はr1の約３倍である。そして、上
記プーリ歯部１とプーリ溝部５を連結する両接合
部１１，１１′は直線からなつており、この両接
合部１１，１１′のなす角度θPは約15〜20゜であ
る。 FIG. 1 is a linear cross-sectional view of the teeth of a pulley used in the toothed belt drive device of the present invention, and the pulley teeth 1 of pulley A are formed by an arc 2 with a radius of curvature r 1 . The pulley groove 5 between the pulley teeth has a radius of curvature r 2 with a center point 7 on the center line 6 of the groove. formed from a circle with a diameter of 8,
The center point 7 of this groove is on the same line 10 as the center points 9, 9' of the circular arcs at both ends of the pulley teeth. Therefore, the height H P of the pulley groove is the sum of r 1 and r 2 , and r 2 is approximately three times r 1 . The joints 11, 11' connecting the pulley teeth 1 and the pulley groove 5 are straight lines, and the angle θ P formed by the joints 11, 11' is about 15 to 20 degrees.
尚、この直線状の接合部１１，１１′の領域は
上記曲率半径r1とr2の組合せによつて決定する。 Incidentally, the area of the linear joint portions 11, 11' is determined by the combination of the curvature radii r1 and r2 .
一方、上記のようなプーリに適用できる歯付ベ
ルトは第２図に示されるように、上記第１図に示
されたプーリの形状を基礎にして設計される。し
かして、該ベルトＢはベルト長手方向に一定ピツ
チで設けた歯１２，溝１３そしてピツチライン１
４を有しており、ベルト歯部１２は曲率半径R1
の円弧１５からなるベルト歯元１６，１６′と、
このベルト歯元の円弧１５に連結した直線状の接
合部１７，１７′そして、互いに交差するそれぞ
れ等しい曲率半径R2を有する２つの円弧１８，
１８′の領域から構成される。そしてこのベルト
歯の中心線１９上には前述したプーリ溝部曲率半
径の中心点７が存在しており、ベルト溝部表面２
０からプーリ歯部の両端部の曲率半径r1分だけ離
れた位置にある。 On the other hand, a toothed belt applicable to the pulley as described above is designed, as shown in FIG. 2, based on the shape of the pulley shown in FIG. 1. The belt B has teeth 12, grooves 13 and pitch lines 1 provided at a constant pitch in the longitudinal direction of the belt.
4, and the belt tooth portion 12 has a radius of curvature R 1
Belt teeth roots 16, 16' consisting of circular arcs 15,
Linear joints 17, 17' connected to the circular arc 15 at the root of the belt teeth, and two circular arcs 18 having the same radius of curvature R 2 that intersect with each other,
It consists of an area of 18'. The above-mentioned center point 7 of the radius of curvature of the pulley groove exists on the center line 19 of the belt teeth, and the belt groove surface 2
The radius of curvature r of both ends of the pulley teeth is 1 minute away from 0.
一方、この場合のベルト歯部曲線半径R2の中
心点２１，２１′は同一ライン上でしかもプーリ
溝部曲率半径の中心点７より上側に位置し、かつ
その間隔ａは前記中心点７を通過するプーリ溝部
の間隔Ｌの１％〜20％であり、またベルト歯部曲
率半径の中心点２１，２１′を通過するラインと
プーリ溝部曲率半径の中心点７を通過するライン
との間隔ｂは、該プーリ歯部両端部の曲率半径r1
の０〜50％にある。更に、ベルト歯部の曲率半径
R2はプーリ溝部の曲率半径r2より約１〜30％大き
くしてベルト歯部の先端２２をプーリ溝部５と重
ねるかもしくは接触するようにする。また、ベル
ト歯部の接合部１７，１７′のなす角度θBはプー
リの接合部１１，１１′の角度θPより約15″〜10
゜大きくし、そしてベルト歯元の曲率半径R1は
プーリ歯端部の曲率半径r1より約０〜20％小さく
する。 On the other hand, in this case, the center points 21 and 21' of the belt tooth curve radius R 2 are located on the same line and above the center point 7 of the radius of curvature of the pulley groove, and the distance a between them passes through the center point 7. The distance b between the line passing through the center points 21 and 21' of the radius of curvature of the belt teeth and the line passing through the center point 7 of the radius of curvature of the pulley groove is 1% to 20% of the distance L between the pulley grooves. , the radius of curvature r 1 of both ends of the pulley teeth
It is in the range of 0-50%. Furthermore, the radius of curvature of the belt teeth
R 2 is approximately 1 to 30% larger than the radius of curvature r 2 of the pulley groove so that the tip 22 of the belt tooth overlaps or contacts the pulley groove 5. Also, the angle θ B formed by the joint parts 17 and 17' of the belt teeth is about 15" to 10" from the angle θ P of the joint parts 11 and 11' of the pulley.
The radius of curvature R 1 at the root of the belt tooth is approximately 0 to 20% smaller than the radius of curvature r 1 at the end of the pulley tooth.
以上のようにして、予め設計されたプーリに上
記寸法条件を満足する歯付ベルトを組み合せる
と、例えば第３図のようになりベルト歯部の先端
２２がプーリ溝部５と重なり、該中心点７を通過
するプーリ溝部の間隔Ｌとベルト歯部の間隔の
差（−Ｌ）がの0.1〜１％と小さくなり、バ
ツクラツシユは減少する。そのため、ベルト溝部
表面２０は摩耗しにくくなる。 When a toothed belt that satisfies the above dimensional conditions is combined with a pre-designed pulley in the above manner, the result will be, for example, as shown in FIG. The difference (-L) between the interval L between the pulley grooves passing through the belt 7 and the interval between the belt teeth becomes as small as 0.1 to 1%, and the backlash is reduced. Therefore, the belt groove surface 20 becomes less susceptible to wear.
更に、第４図に図示するように、該歯付ベルト
Ｂを平行移動して駆動プーリＡとの重なり状態を
見るとベルト歯部１２はプーリＡと斜線部分２３
で重なり、ベルト歯元１６で大きくベルト歯部の
中心部２４で小さくなる。従つて、ベルトが駆動
プーリから抜ける時、プーリの歯先はベルト歯側
面に対して徐々に小さな力を与えながら回転する
ため、ベルト歯元にかかる応力は小さくなり歯元
クラツクが生じにくくなる。しかし、もし仮にベ
ルトがベルト歯元で小さくベルト歯部の中央部で
大きく干渉すると、ベルト歯元にかかる応力は
徐々に大きくなつて歯元クラツクが生じやすくな
るが、これは従来の駆動装置に見られるところで
ある。 Further, as shown in FIG. 4, when the toothed belt B is moved in parallel and the overlapping state with the driving pulley A is seen, the belt toothed portion 12 is in the shaded area 23 with the pulley A.
They overlap at the belt tooth root 16 and become smaller at the center 24 of the belt teeth. Therefore, when the belt comes off the drive pulley, the tooth tip of the pulley rotates while gradually applying a small force to the side surface of the belt tooth, so the stress applied to the belt tooth base is reduced and tooth root cracks are less likely to occur. However, if the belt is small at the base of the belt tooth and there is a large interference at the center of the belt tooth, the stress applied to the belt tooth will gradually increase and tooth base cracks are likely to occur. This is where you can see it.
以上詳述したように本考案の駆動装置は一般に
知られた形状のプーリとこのプーリを基礎した改
善した歯付ベルトとを組合せたもので、前述の如
き組合せ状態においてベルト歯元とプーリ歯部間
のバツクラツシユを小さくし、かつ歯付ベルトを
平行移動してプーリ側面との重なり具合を見ると
ベルト歯元で大きくベルト歯中央部で小さくな
り、そしてこのような状態になると、ベルトが駆
動プーリから抜ける時、ベルト歯元にかかる応力
が小さくなつて歯元クラツクが生じにくくなる等
の効果を奏することができ、歯付ベルトとプーリ
との噛み合い駆動においてベルトの破損を防止
し、その耐久性を良好ならしめて駆動の正確性を
高め相互干渉を阻止して長期確実伝動に大きく寄
与することが期待されるものである。 As described in detail above, the drive device of the present invention is a combination of a pulley of a generally known shape and an improved toothed belt based on this pulley. If you reduce the bump between the teeth and move the toothed belt in parallel to see how it overlaps with the side of the pulley, it will be large at the root of the belt tooth and small at the center of the belt tooth. When the toothed belt is pulled out of the belt, the stress applied to the tooth base of the belt is reduced, making tooth root cracks less likely to occur. This also prevents damage to the belt when the toothed belt engages with the pulley and increases its durability. It is expected that this will improve drive accuracy, prevent mutual interference, and greatly contribute to long-term reliable transmission.
第１図は本考案の駆動装置に使用するプーリの
歯部を直線状に展開した断面図、第２図は本考案
の駆動装置に使用する歯付ベルトの歯部を直線状
に展開した断面図、第３図は第１図及び第２図で
示されたプーリと歯付ベルトを組み合せた状態
図、第４図は第３図に示された組み合せ状態にお
いて歯付ベルトを平行移動してプーリ側面との重
なり具合を見た説明図である。
Ａ……プーリ、Ｂ……歯付ベルト、１……プー
リ歯部、２……両端部円弧、３，３′……プーリ
歯部両端部、５……プーリ溝部、７……溝部の中
心点、８……溝部円弧、９，９′……プーリ歯両
端部中心点、１１，１１′……プーリ歯の直線状
接合部、１７，１７′……ベルト歯元直線状接合
部、１８，１８′……ベルト歯部円弧、２１，２
１′……ベルト歯部円弧中心点。
Fig. 1 is a linear cross-sectional view of the teeth of the pulley used in the drive device of the present invention, and Fig. 2 is a linear cross-section of the teeth of the toothed belt used in the drive device of the present invention. Figure 3 shows a state in which the pulley and toothed belt shown in Figures 1 and 2 are combined, and Figure 4 shows a state in which the toothed belt is moved in parallel in the combined state shown in Figure 3. FIG. 3 is an explanatory diagram showing how it overlaps with the side surface of the pulley. A...Pulley, B...Toothed belt, 1...Pulley teeth, 2...Circular arc at both ends, 3, 3'...Both ends of pulley teeth, 5...Pulley groove, 7...Center of groove Point, 8... Groove arc, 9, 9'... Center point of both ends of pulley teeth, 11, 11'... Linear joint of pulley teeth, 17, 17'... Linear joint of belt tooth base, 18 , 18'... Belt tooth arc, 21, 2
1'... Center point of the belt tooth arc.
Claims (1)
状において両端部の円弧と中央部の直線部からな
るプーリ歯部、この歯部間に形成される１つの中
心をもつ円弧のプーリ溝部、そして上記プーリ歯
部とプーリ溝部を連結する直線状の接合部から構
成され、一方、歯付ベルトが、ベルト長手方向に
一定ピツチで歯部と溝部を交互に有し、ベルト歯
部としてベルト歯元を円弧の一部とし、残りの領
域を少なくとも互いに交差するそれぞれ等しい半
径を有する２つの円弧領域と、この領域と前記ベ
ルト歯元を連結する直線状の接合部から構成され
る歯付ベルトの駆動装置において、ベルト歯部の
２つの円弧１８，１８′の中心点２１，２１′をプ
ーリ溝部の円弧８の中心点７よりベルト歯元側へ
位置させ、ベルト歯部の両円弧１８，１８′の合
計長さをプーリ溝部の円弧８長さより１〜30％大
きくし、かつ、ベルト歯の接合部１７，１７′の
なす角度θBをプーリ歯の接合部１１，１１′のな
す角度θPより15″〜10゜大きくするように上記プ
ーリと歯付ベルトの寸法関係を形成したことを特
徴とする歯付ベルトの駆動装置。 The pulley consists of a pulley and a toothed belt, and the pulley has a cross-sectional shape consisting of circular arcs at both ends and a straight line at the center, a pulley groove portion having a single center formed between the teeth, and a pulley groove portion having one center. The toothed belt has teeth and grooves alternately at a constant pitch in the longitudinal direction of the belt. In a toothed belt drive device, the remaining region is composed of at least two arcuate regions having equal radii that intersect with each other, and a linear joint that connects this region and the belt tooth base. , the center points 21, 21' of the two circular arcs 18, 18' of the belt teeth are located closer to the belt teeth than the center point 7 of the circular arc 8 of the pulley groove, and the sum of both circular arcs 18, 18' of the belt teeth is The length should be 1 to 30% larger than the length of the arc 8 of the pulley groove, and the angle θ B formed by the joint parts 17 and 17' of the belt teeth should be 15 greater than the angle θ P formed by the joint parts 11 and 11' of the pulley teeth. A drive device for a toothed belt, characterized in that the dimensional relationship between the pulley and the toothed belt is set to be larger by 10 degrees.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5872882U JPS58161254U (en) | 1982-04-21 | 1982-04-21 | Toothed belt drive device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5872882U JPS58161254U (en) | 1982-04-21 | 1982-04-21 | Toothed belt drive device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58161254U JPS58161254U (en) | 1983-10-27 |
| JPS6126659Y2 true JPS6126659Y2 (en) | 1986-08-09 |
Family
ID=30069096
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5872882U Granted JPS58161254U (en) | 1982-04-21 | 1982-04-21 | Toothed belt drive device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58161254U (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4851155A (en) * | 1971-10-28 | 1973-07-18 | ||
| JPS5220629A (en) * | 1975-08-08 | 1977-02-16 | Matsushita Electric Works Ltd | Plane roof material |
| JPS5491655A (en) * | 1977-12-23 | 1979-07-20 | Us Rubber Co | Improved pulley for positive drive system |
| JPS5499854A (en) * | 1977-12-14 | 1979-08-07 | Uniroyal Inc | Mechanical power transmission mechanism |
| JPS56167955A (en) * | 1980-05-27 | 1981-12-23 | Mitsuboshi Belting Ltd | Transmission apparatus with toothed belt |
-
1982
- 1982-04-21 JP JP5872882U patent/JPS58161254U/en active Granted
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4851155A (en) * | 1971-10-28 | 1973-07-18 | ||
| JPS5220629A (en) * | 1975-08-08 | 1977-02-16 | Matsushita Electric Works Ltd | Plane roof material |
| JPS5499854A (en) * | 1977-12-14 | 1979-08-07 | Uniroyal Inc | Mechanical power transmission mechanism |
| JPS5491655A (en) * | 1977-12-23 | 1979-07-20 | Us Rubber Co | Improved pulley for positive drive system |
| JPS56167955A (en) * | 1980-05-27 | 1981-12-23 | Mitsuboshi Belting Ltd | Transmission apparatus with toothed belt |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58161254U (en) | 1983-10-27 |
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