JPH0122991Y2 - - Google Patents
Info
- Publication number
- JPH0122991Y2 JPH0122991Y2 JP15750283U JP15750283U JPH0122991Y2 JP H0122991 Y2 JPH0122991 Y2 JP H0122991Y2 JP 15750283 U JP15750283 U JP 15750283U JP 15750283 U JP15750283 U JP 15750283U JP H0122991 Y2 JPH0122991 Y2 JP H0122991Y2
- Authority
- JP
- Japan
- Prior art keywords
- belt
- pulley
- teeth
- tooth
- region
- 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
- 230000007423 decrease Effects 0.000 claims description 4
- 230000003068 static effect Effects 0.000 claims description 2
- 238000010008 shearing Methods 0.000 description 4
- 210000004513 dentition Anatomy 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000036346 tooth eruption Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 238000005336 cracking Methods 0.000 description 2
- 101100537937 Caenorhabditis elegans arc-1 gene Proteins 0.000 description 1
- 229920006231 aramid fiber Polymers 0.000 description 1
- 239000013013 elastic material Substances 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 239000003365 glass fiber Substances 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 229920000728 polyester Polymers 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Landscapes
- Pulleys (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (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の改良に関するものであ
る。[Detailed Description of the Invention] The present invention relates to an improvement of a toothed belt drive device consisting of a combination of a toothed belt and a pulley.
今日、一般に使用されている歯付ベルトとプー
リと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。 The drive device consisting of a combination of a toothed belt and a pulley that is commonly used today is as follows:
RMA (Rubber Manufacturers Association) IP
24 (1978), there is a transmission system that uses belt teeth with a trapezoidal cross section and a pulley with a similar shape to mesh with the teeth. 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 a 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。（米国特許第3756091号
明細書参照）
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が、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。 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. (See US Pat. No. 3,756,091.) However, one of the major drawbacks of this device is that the backlash between the root of the belt teeth and the pulley is designed to be large. As the travel distance increases, the belt groove surface is easily rubbed by the pulleys and is easily 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 and 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. be.
そのため、更にこれを改善すべく、例えば米国
特許第4233852号明細書に開示されているように、
ベルト歯部の高さをプーリ溝部の深さより大きく
して、ごく限られたベルト歯の先端部をプーリ溝
部の底面で干渉させることによつて、ベルト溝部
をプーリの歯部表面によつてこすられるのを防止
すると共にベルト溝部とプーリ歯部とのたたき音
を防止している。 Therefore, in order to further improve this, for example, as disclosed in US Pat. No. 4,233,852,
By making the height of the belt teeth larger than the depth of the pulley groove and interfering with the very limited tips of the belt teeth at the bottom of the pulley groove, the belt groove can be rubbed against the surface of the pulley teeth. This also prevents the belt groove from hitting the pulley teeth.
しかし、上記の装置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、歯付ベルトとプーリ間のバツクラツシユはベ
ルト歯元部あるいはベルト歯部の中央部で最も大
きく、ベルトの歯先で小さくなるように設計さ
れ、そのためベルト駆動中、ベルト歯は中央部分
から歯先に至つて徐々に大きな圧縮応力を受け、
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。その結果、ベルト歯元にかかる剪断力
（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る。 However, the major drawback of the above-mentioned device is that tooth root cracks of the belt teeth occur in a short period of time, i.e., the crack between the toothed belt and the pulley is greatest at the belt tooth root or in the center of the belt teeth. , is designed to be smaller at the tips of the belt teeth, so during belt driving, the belt teeth are subjected to gradually larger compressive stress from the center to the tips of the teeth.
When the belt comes off the pulley, the pulley tooth tip rotates while gradually applying a larger force to the side surface of the belt tooth. As a result, the shearing force (the force that tries to separate the tensile member and the teeth) applied to the belt teeth increases,
Dental cracks are more likely to occur.
本考案は上述の如き状況に対処して更にそのよ
うな点を改善することを課題とし、ベルトとプー
リとの噛み合い中にベルト歯部の側圧をベルト歯
元から歯先付近に至つて徐々に小さくしてベルト
がプーリから抜ける時にプーリ歯先をベルト歯部
側面に対して徐々に小さな力を与えつつ回転さ
せ、これによつて早期のベルト歯元クラツクを防
止し、また噛み合い時においてベルト歯の先端部
をプーリ溝部底面に接触させることを目的とする
ものである。 The purpose of this invention is to deal with the above-mentioned situation and to further improve such points.The purpose of this invention is to gradually reduce the lateral pressure of the belt teeth from the root of the belt tooth to the vicinity of the tooth tip during the engagement between the belt and the pulley. When the belt is pulled out from the pulley, the pulley tooth tip is rotated while gradually applying a small force to the side surface of the belt tooth. This prevents early belt tooth root cracking, and also prevents the belt tooth tip from rotating when the belt is pulled out from the pulley. The purpose of this is to bring the tip of the pulley into contact with the bottom surface of the pulley groove.
即ち、上記目的に適合する本考案の特徴はプー
リと歯付ベルトからなり、前記プーリは断面形状
において両端部の円弧とこれを連結する直線部分
の表面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
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、一方歯付ベルトはベルト長手方
向に一定ピツチで歯部と溝部を交互に有しベルト
歯部のうちベルト溝部表面からベルト歯部高さの
60〜90％までの第１領域がベルト歯元を円弧の一
部とし、残りの領域を互いに交差する２つの楕円
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、またベルト歯頂部に
至る残りの第２領域が円弧からなる歯付ベルトの
駆動装置であり、歯付ベルトとプーリの静的噛み
合い状態においてベルト歯部とプーリ溝部間のバ
ツクラツシユがベルト歯部の第１領域でベルト歯
元から直線的に増大し、また第２領域ではベルト
歯頂部付近に至つて徐々に小さくなる関係にある
歯付ベルトの駆動装置である。 That is, the features of the present invention that meet the above objectives include a pulley and a toothed belt. A toothed belt consists of an arcuate pulley groove with one center formed in the center, and a straight joint connecting the pulley teeth and the pulley groove.On the other hand, a toothed belt has teeth and grooves alternated at a constant pitch in the longitudinal direction of the belt. The height of the belt teeth from the belt groove surface to the belt teeth.
The first region of 60 to 90% makes the belt dentition part of an arc, and the remaining region consists of two elliptical arc regions that intersect with each other and a linear joint that connects this region and the belt dentition. , the remaining second region up to the top of the belt teeth is a toothed belt drive device in which the remaining second region is an arc, and when the toothed belt and the pulley are statically engaged, the backlash between the belt teeth and the pulley groove is caused by the friction of the belt teeth. This is a drive device for a toothed belt in which the relationship increases linearly from the root of the belt tooth in the first region, and gradually decreases in the second region near the top of the belt tooth.
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で形成されるプーリ歯先両端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の円弧８から形成
され、この溝部の中心点７はプーリ歯先両端３，
３′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。 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. The center point 7 of this groove is located at both ends 3 of the pulley tooth tip.
It is on the same line 10 as the center points 9, 9' of the arc 3'. 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 .
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。 The joint parts 11 and 11' connecting the pulley tooth part 1 and the pulley groove part 5 are straight lines, and the angle θ P formed by the joint parts 11 and 11' is approximately
It is 15~20°.
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の組合せにより決定される。 Incidentally, the area of the linear joint portions 11 and 11' is determined by the combination of the curvature radii r 1 and r 2 .
一方、上記のようなプーリに適用できる歯付ベ
ルトＢは第２図に示されるが、ゴム又はその他の
弾性体よりなり、ベルト長手方向に一定ピツチで
歯部１６と溝部１５を交互に有し、ベルトピツチ
ライン１４上にガラス繊維、ポリエステル繊維、
アラミド繊維等からなるロープの抗張体を埋設
し、更に上記歯部１６及び溝部１５の表面を織物
で被覆することによつて構成されそのベルト歯部
１６が第２図に示されるようにプーリ溝部の側壁
の形状に準じて形成されるものである。かかるベ
ルト歯部１６の構成はベルト溝部表面２４からベ
ルト歯部高さHBの60〜90％までの第１領域H1と
その末端からベルト歯の最先端即ち、歯頂部１７
に至る第２領域H2から構成され、このうち上記
第１領域H1はプーリ溝部側壁から側圧を受ける
ところであり、中心点２９をもつ曲率半径R1の
円弧（ただし、R1＜r1）からなるベルト歯元２
２，２２と、このベルト歯元の円弧に連結した角
度θBの直線状の接合部２１，２１及び第２領域
H2内で交差するような２つの楕円弧２８，２８
からなり、また第２領域H2はプーリ溝部底面２
０から圧力を受けるところであり、ベルト歯の中
心線２６上に中心点１８をもつ半径R2の円弧１
３で形成されている。なお第１領域H1と第２領
域H2の結合部は直線１２，１２で結んでも差支
えない。 On the other hand, a toothed belt B applicable to the pulley as described above is shown in FIG. 2, and is made of rubber or other elastic material and has teeth 16 and grooves 15 alternately at a constant pitch in the longitudinal direction of the belt. , glass fiber, polyester fiber on the belt pitch line 14,
The belt is constructed by embedding a tensile rope made of aramid fiber or the like, and further covering the surfaces of the teeth 16 and grooves 15 with a fabric, and the teeth 16 of the belt are attached to a pulley as shown in FIG. It is formed according to the shape of the side wall of the groove. The configuration of the belt tooth portion 16 is as follows: a first region H 1 extending from the belt groove surface 24 to 60% to 90% of the belt tooth height H B ;
The first region H 1 receives lateral pressure from the side wall of the pulley groove, and is an arc with a radius of curvature R 1 having a center point 29 (where R 1 < r 1 ) . Belt dentition 2 consisting of
2, 22, a linear joint part 21, 21 of angle θ B connected to the circular arc of this belt tooth base, and a second region.
Two elliptical arcs 28, 28 that intersect in H 2
The second region H2 is the bottom surface 2 of the pulley groove.
A circular arc 1 of radius R 2 that receives pressure from 0 and has a center point 18 on the center line 26 of the belt teeth.
It is formed by 3. Note that the connecting portion between the first region H 1 and the second region H 2 may be connected by straight lines 12 , 12 .
しかして、以上のようなプーリと歯付ベルトの
静的噛み合いにおいて、ベルト歯部１６とプーリ
溝部側壁８間のバツクラツシユａは、第３図に図
示される如く、第１領域H1においてベルト歯元
２２の分離点ｂから第２領域の境界点Ｃに至るま
で直線的に増大し、また第２領域H2では上記境
界点Ｃからベルト歯先に向つて徐々に小さくなつ
ている。 Therefore, in the static engagement between the pulley and the toothed belt as described above, the backlash a between the belt teeth 16 and the pulley groove side wall 8 is caused by the belt teeth in the first region H1, as shown in FIG. It increases linearly from the separation point b of the source 22 to the boundary point C of the second region, and in the second region H2 , it gradually decreases from the boundary point C toward the tip of the belt tooth.
そして、上記第１領域H1内のバツクラツシユ
ａの勾配θは一般に15″〜20゜好ましくは１〜4゜の
範囲に設定され、また、ベルト歯部の高さHBは
プーリ溝部の深さHPより２〜15％程度大きくし
てベルト歯部をプーリ溝部底面と圧接せしめるこ
とも可能である。 The gradient θ of the backlash a in the first region H1 is generally set in the range of 15'' to 20 degrees, preferably 1 to 4 degrees, and the height H of the belt teeth is the depth of the pulley groove. It is also possible to make the belt teeth larger by about 2 to 15% than H P so that the belt teeth come into pressure contact with the bottom surface of the pulley groove.
更に、ベルト歯元の曲率半径R1についてはプ
ーリ歯先の曲率半径r1より約０〜20％小さくす
る。 Furthermore, the radius of curvature R 1 of the root of the belt tooth is approximately 0 to 20% smaller than the radius of curvature r 1 of the tip of the pulley tooth.
叙上のようにして予め設計されたプーリにベル
ト歯部の第１領域H1及び第２領域H2において上
記バツクラツシユの関係を満足する歯付ベルトを
組合せると、第４図に示されるように、噛み合い
中にベルト歯部１６における第１領域H1はプー
リ溝部側壁８によつてベルト歯元２２から第２領
域の境界点Ｃに至つて徐々に小さくなるような側
圧を受け、また第２領域H2はプーリ溝部側壁８
よりもむしろプーリ溝部底面２０から圧力Ｆを受
ける。そして、その後、ベルトが従動軸に取付け
たプーリから抜ける時、プーリ歯部の第１領域
H1はプーリ歯先３から徐々に小さな剪断力を受
けるため、モーメントの関係からベルト歯元２２
にかかる剪断力（抗張体とベルト歯部を離そうと
する力）が増大せず、歯元クラツクが生じにくく
なり、しかもベルトがプーリからスムーズに抜け
る効果がある。（第５図イ，ロ，ハ，ニ参照）し
かし、従来の如くベルト歯部がベルト歯先で小さ
く中央部付近から歯先方面にかけて大きな圧縮応
力を受けると、ベルト歯元にかかる剪断力は徐々
に大きくなつて設計予測値以上になり、そしてこ
れの繰り返しによつてベルト歯元が大きく疲労し
歯元クラツクが短期に生じやすくなるが、これは
従来の駆動装置で見られたところである。 When a toothed belt that satisfies the above-mentioned backlash relationship in the first region H1 and second region H2 of the belt teeth is combined with the pulley designed in advance as described above, as shown in FIG. During meshing, the first region H1 of the belt tooth portion 16 is subjected to a lateral pressure that gradually decreases from the belt tooth root 22 to the boundary point C of the second region by the pulley groove side wall 8, and 2 area H 2 is pulley groove side wall 8
Rather, the pressure F is applied from the bottom surface 20 of the pulley groove. Then, when the belt comes off the pulley attached to the driven shaft, the first area of the pulley teeth
Since H 1 receives a gradually smaller shearing force from the pulley tooth tip 3, the belt tooth root 22
The shearing force applied to the belt (the force that tries to separate the tensile member from the belt teeth) does not increase, tooth base cracks are less likely to occur, and the belt can come off the pulley smoothly. (See Figure 5 A, B, C, D) However, if the belt teeth are small at the tips of the belt teeth and receive large compressive stress from near the center to the tips of the teeth, as in the past, the shearing force applied to the roots of the belt teeth will be It gradually increases to exceed the design predicted value, and as this process is repeated, the belt tooth base is greatly fatigued and tooth root cracks tend to occur in a short period of time, as has been seen in conventional drive devices.
また、ベルト歯部の第２領域H2は円弧形をな
し、かつわずかに突出した状態になつているが、
プーリの歯先と干渉せず、しかも上記第２領域
H2はプーリ溝部底面２０と圧接してベルト歯部
１６をサポートするためベルト溝部表面２４がプ
ーリ歯部表面４と強くこすれ合うこともなく、ま
た圧接することにより上記第２領域H2は弾性的
に変形してプーリ溝部底面２０と当接すると共に
ベルト溝部表面２４とプーリ歯部表面４とのたた
き音も防止できる。 Further, the second region H2 of the belt tooth portion has an arc shape and is in a slightly protruding state.
Does not interfere with the tooth tip of the pulley, and the above second area
Since H 2 supports the belt teeth 16 by being in pressure contact with the bottom surface 20 of the pulley groove, the belt groove surface 24 does not rub strongly against the pulley tooth surface 4, and due to the pressure contact, the second region H 2 has elasticity. It deforms and comes into contact with the bottom surface 20 of the pulley groove, and also prevents the knocking sound between the belt groove surface 24 and the pulley tooth surface 4.
従つて、本考案の駆動装置では歯付ベルトの歯
部１６を２つの領域に区分し、しかも２つの領域
に夫々別の機能を分担させており、これを満足す
るためには前記のとおり第１領域H1はベルト歯
部高さHBの60〜90％であり、60％以下ではベル
ト歯部の中央部分から歯先方向にかけてベルト歯
部の受ける側圧が大きくなつて歯元クラツクが生
じやすくなり、また一方90％より大きくすると第
２領域H2を明確に出現させることが困難である。 Therefore, in the drive device of the present invention, the toothed portion 16 of the toothed belt is divided into two regions, and each of the two regions is assigned a different function. 1 area H1 is 60 to 90% of the belt tooth height H B , and when it is less than 60%, the lateral pressure that the belt tooth receives increases from the center of the belt tooth toward the tooth tip, causing root cracks. On the other hand, if it is larger than 90%, it is difficult to make the second region H2 appear clearly.
以上詳述したように本考案の駆動装置は一般に
知られた円弧形のプーリ溝部側壁をもつプーリと
第１領域と第２領域に機能的に区分された歯部を
有する歯付ベルトを組合せたものであるから上記
ベルト歯部の第１領域はプーリ歯先から徐々に小
さな応力を受けながらプーリから外れるために、
ベルトの歯元クラツクが起らずにスムーズに外
れ、またベルト歯部の第２領域の存在によつてベ
ルト歯部は噛み合い時においてプーリ溝部底面と
弾性的に圧縮変形し、これによつてベルト溝部表
面がプーリ歯部表面とこすれ合うことも少なくな
り、更にはこの間におけるたたき音も防止できる
等の特長を有し、きわめて効果的な駆動装置であ
る。 As detailed above, the drive device of the present invention combines a generally known pulley with an arc-shaped pulley groove side wall and a toothed belt having teeth functionally divided into a first region and a second region. Since the first region of the belt teeth is gradually released from the pulley while receiving a small stress from the tooth tip of the pulley,
The belt comes off smoothly without cracking, and due to the existence of the second region of the belt teeth, the belt teeth are elastically compressed and deformed with the bottom surface of the pulley groove when engaged, and the belt This is an extremely effective drive device, with features such as less friction between the groove surface and the pulley tooth surface, and also the ability to prevent knocking noise between the grooves and the pulley tooth surface.
第１図は本考案の駆動装置に使用するプーリの
歯部を直線的に展開した断面図、第２図は第１図
に示されたプーリと本考案に使用する歯付ベルト
とを組合せた状態図、第３図は第２図におけるプ
ーリとベルト間のバツクラツシユを示す図、第４
図は歯付ベルトとプーリの駆動時の係合状態にお
けるベルト歯部にかかる側圧分布状態を示し、第
５図イ，ロ，ハ，ニは歯付ベルトが従動軸に取付
けたプーリから外れる時の状態図である。
Ａ……プーリ、Ｂ……歯付ベルト、１……プー
リ歯部、２……円弧、３，３′……プーリ歯先両
端、４……歯先表面部、５……プーリ溝部、６…
…中心線、７，９，９′……中心点、８……円弧
（プーリ溝部側壁）、１１，１１′……接合部、１
５……ベルト溝部、１６……ベルト歯部、１７…
…ベルト歯頂部、２１……接合部、２２……ベル
ト歯元、２４……ベルト溝部表面、２８……楕円
弧、HB……ベルト歯部高さ、H1……第１領域、
H2……第２領域、ａ……バツクラツシユ。
Figure 1 is a linear cross-sectional view of the teeth of the pulley used in the drive device of the present invention, and Figure 2 is a combination of the pulley shown in Figure 1 and the toothed belt used in the present invention. The state diagram, Figure 3 is a diagram showing the backlash between the pulley and belt in Figure 2, and Figure 4 is a diagram showing the backlash between the pulley and belt in Figure 2.
The figure shows the side pressure distribution state applied to the belt teeth when the toothed belt and the pulley are engaged during driving, and Figure 5 A, B, C, and D show when the toothed belt comes off the pulley attached to the driven shaft. FIG. A...Pulley, B...Toothed belt, 1...Pulley teeth, 2...Circular arc, 3, 3'...Both ends of the pulley tooth tip, 4...Tooth tip surface, 5...Pulley groove, 6 …
... Center line, 7, 9, 9' ... Center point, 8 ... Arc (pulley groove side wall), 11, 11' ... Joint part, 1
5...Belt groove part, 16...Belt tooth part, 17...
... Belt tooth top, 21 ... Joint, 22 ... Belt tooth root, 24 ... Belt groove surface, 28 ... Elliptical arc, H B ... Belt tooth height, H 1 ... First region,
H 2 ...Second area, a...Battery.
Claims (1)
面形状において両端部の円弧と、これを連結する
直線部分の表面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、歯付ベルトは
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、ベルト歯部のうちベルト溝部表面からベ
ルト歯部高さの60〜90％までの第１領域がベルト
歯元を円弧とし、他の部分を互いに交差する２つ
の楕円弧領域そして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なり、またベルト歯
頂部に至る残りの第２領域が円弧であり、しかも
前記歯付ベルトとプーリの静的な噛み合い状態に
おけるベルト歯部とプーリ溝部間のバツクラツシ
ユがベルト歯部の第１領域でベルト歯元から第１
領域と第２領域間の境界点に至るまで直線的に増
大すると共に第２領域では上記境界点から徐々に
小さくなる関係にあり、更にベルト歯部の高さが
プーリ溝部の深さより大きく、ベルト駆動時ベル
ト歯部がプーリ溝部底面に圧接してなることを特
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 a circular arc at both ends, a pulley tooth section consisting of a surface section of a straight line connecting these ends, and an arc having one center formed between these tooth sections. It consists of a pulley groove, and a linear joint that connects the pulley teeth and the pulley groove.On the other hand, a toothed belt has teeth and grooves alternately at a constant pitch in the longitudinal direction of the belt. The first region from the belt groove surface to 60% to 90% of the belt tooth height has the belt tooth root as a circular arc, the other portions are two elliptical arc regions that intersect with each other, and a straight line connecting this region and the belt tooth root. The remaining second region reaching the top of the belt tooth is a circular arc, and the bump between the belt tooth and the pulley groove when the toothed belt and the pulley are in static engagement is the same as the belt tooth. from the belt teeth in the first region of
The relationship increases linearly up to the boundary point between the region and the second region, and gradually decreases from the boundary point in the second region, and furthermore, the height of the belt teeth is greater than the depth of the pulley groove, and the belt A toothed belt drive device characterized in that the belt teeth are in pressure contact with the bottom surface of the pulley groove during driving.
Priority Applications (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15750283U JPS6064355U (en) | 1983-10-12 | 1983-10-12 | Toothed belt drive device |
| IN762/MAS/84A IN162773B (en) | 1983-10-12 | 1984-10-10 | |
| DE8484306935T DE3461857D1 (en) | 1983-10-12 | 1984-10-11 | Toothed belt drive |
| US06/660,009 US4604080A (en) | 1983-10-12 | 1984-10-11 | Toothed drive belt |
| CA000465143A CA1227667A (en) | 1983-10-12 | 1984-10-11 | Toothed belt drive |
| EP84306935A EP0146224B1 (en) | 1983-10-12 | 1984-10-11 | Toothed belt drive |
| AT84306935T ATE24588T1 (en) | 1983-10-12 | 1984-10-11 | BELT DRIVE. |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15750283U JPS6064355U (en) | 1983-10-12 | 1983-10-12 | Toothed belt drive device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6064355U JPS6064355U (en) | 1985-05-07 |
| JPH0122991Y2 true JPH0122991Y2 (en) | 1989-07-13 |
Family
ID=30347230
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15750283U Granted JPS6064355U (en) | 1983-10-12 | 1983-10-12 | Toothed belt drive device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6064355U (en) |
-
1983
- 1983-10-12 JP JP15750283U patent/JPS6064355U/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6064355U (en) | 1985-05-07 |
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