JPH0126928Y2 - - Google Patents
Info
- Publication number
- JPH0126928Y2 JPH0126928Y2 JP1984105433U JP10543384U JPH0126928Y2 JP H0126928 Y2 JPH0126928 Y2 JP H0126928Y2 JP 1984105433 U JP1984105433 U JP 1984105433U JP 10543384 U JP10543384 U JP 10543384U JP H0126928 Y2 JPH0126928 Y2 JP H0126928Y2
- Authority
- JP
- Japan
- Prior art keywords
- toothed
- pulley
- belt
- toothed belt
- teeth
- 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
- 230000002093 peripheral effect Effects 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 230000007423 decrease Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000010998 test method Methods 0.000 description 2
- 238000004804 winding Methods 0.000 description 2
- 238000007796 conventional method Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 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】
（産業上の利用分野）
本考案は、歯付プーリに歯付ベルトが歯付プー
リに巻回されてなる歯付ベルト駆動装置に関する
ものである。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a toothed belt drive device in which a toothed belt is wound around a toothed pulley.
（従来の技術）
従来、歯付プーリに歯付ベルトが巻回されてな
る歯付ベルト駆動装置において、噛合時に発生す
る騒音を低減するために、例えば特開昭52−
76554号公報に示されるように、ベルト歯及び溝
と、プーリ歯及び溝との寸法関係が、プーリ間の
ベルト長手方向の範囲に亘つてベルト歯の高さが
プーリ溝の深さよりも大きく、一方ベルトがプー
リの周囲にきた際、プーリと対向するベルト歯の
一番外方向に向いた部分が、プーリ歯の間に配置
されたプーリの溝の底部を形成する歯の形成され
たプーリの部分と接触し、同時にベルト歯が圧縮
されて高さを減少し、プーリの歯の最も半径方向
外側に向いた部分がベルト歯間に配置されベルト
溝を形成するベルトの部分と接触するようにな
し、ベルトとプーリの噛合時にベルト歯とプーリ
溝とを干渉させて衝突エネルギを吸収する技術は
知られている。(Prior Art) Conventionally, in a toothed belt drive device in which a toothed belt is wound around a toothed pulley, in order to reduce the noise generated during meshing, for example, Japanese Patent Application Laid-Open No.
As shown in Publication No. 76554, the dimensional relationship between the belt teeth and grooves and the pulley teeth and grooves is such that the height of the belt teeth is greater than the depth of the pulley grooves over the range in the belt longitudinal direction between the pulleys, On the other hand, when the belt comes around the pulley, the outermost part of the belt teeth facing the pulley is the part of the pulley with teeth forming the bottom of the pulley groove located between the pulley teeth. and at the same time the belt teeth are compressed and reduced in height such that the most radially outwardly facing portion of the pulley teeth is in contact with the portion of the belt disposed between the belt teeth and forming the belt groove. A known technique is to absorb collision energy by causing belt teeth and pulley grooves to interfere with each other when the belt and pulley engage.
また、実公昭57−6823号公報において、多数の
撚糸をロープ状に巻回してベルトの長手方向に螺
旋状に巻回埋設された抗張体の解撚巻力によつて
生ずるベルトのスラスト力を相殺する反スラスト
力を生ずるはす歯角を有するはす歯タイミングベ
ルトが提案されている。 In addition, in Japanese Utility Model Publication No. 57-6823, a thrust force of the belt is generated by the untwisting and winding force of a tensile body which is spirally wound and buried in the longitudinal direction of the belt by winding a large number of twisted yarns into a rope shape. Helical timing belts have been proposed that have helical tooth angles that create anti-thrust forces that offset the .
（考案が解決しようとする課題）
上述した従来の技術では、何れも、高速駆動時
における噛合安定性に欠けており、騒音の低減効
果も微少であるので、実用性に問題がある。(Problems to be Solved by the Invention) The above-mentioned conventional techniques all lack meshing stability during high-speed driving, and the noise reduction effect is minimal, so there are problems in practicality.
本考案はかかる点に鑑みてなされたもので、ベ
ルト駆動時において、安定性よく噛合し、かつ騒
音の低減を図ることができる歯付ベルト駆動装置
を提供することを目的とする。 The present invention has been made in view of these points, and an object of the present invention is to provide a toothed belt drive device that can mesh with good stability and reduce noise when the belt is driven.
（課題を解決するための手段）
本考案は、上記目的を達成するために、歯付プ
ーリに歯付ベルトが巻回されてなるもので、前記
歯付プーリ又は歯付ベルトの一方の歯部のフラン
ク面が、歯筋方向中央部が歯筋方向端部に対して
周方向に偏位しかつ歯筋方向中央に関して対称と
なるように形成され、前記一方の歯部のフランク
面が、他方の歯部のフランク面に対し、歯付ベル
トとプーリとの噛合当初歯付ベルトの歯部とプー
リの歯部との接触が歯筋方向において１位置又は
２位置で、その後全体が接触するように構成され
ていることを特徴とする。(Means for Solving the Problems) In order to achieve the above object, the present invention comprises a toothed belt wound around a toothed pulley, and one toothed portion of the toothed pulley or the toothed belt. The flank surface of the one tooth portion is formed such that the center portion in the tooth trace direction is offset in the circumferential direction from the end portion in the tooth trace direction and is symmetrical with respect to the center in the tooth trace direction, and the flank surface of the one tooth portion is When the toothed belt and pulley first engage, the teeth of the toothed belt and the teeth of the pulley contact each other at one or two positions in the direction of the tooth trace, and then the entire teeth contact each other. It is characterized by being configured as follows.
（作用）
歯付ベルトとプーリとの噛合当初、歯付ベルト
の歯部とプーリの歯部との接触が、歯筋方向にお
いて、１位置又は２位置で、その後全体が接触す
る。したがつて、歯付ベルトとプーリとの噛合時
間が長くなり、衝突エネルギが分散され、騒音が
低減される。また、噛合安定性がよくなり、歯付
ベルトが蛇行しなくなる。(Function) At the beginning of meshing between the toothed belt and the pulley, the teeth of the toothed belt and the teeth of the pulley come into contact at one or two positions in the direction of the tooth trace, and then the entire teeth come into contact. Therefore, the meshing time between the toothed belt and the pulley becomes longer, collision energy is dispersed, and noise is reduced. In addition, meshing stability is improved and the toothed belt does not meander.
（実施例）
以下、本考案の実施例を図面に沿つて詳細に説
明する。(Example) Hereinafter, an example of the present invention will be described in detail with reference to the drawings.
第１図に、、歯付ベルト駆動装置を構成する歯
付プーリ１の一例を示す。 FIG. 1 shows an example of a toothed pulley 1 constituting a toothed belt drive device.
この歯付プーリ１の歯部２のフランク面２ａ，
２ｂすなわち周方向の前後面は何れも歯筋方向Ｓ
の中央部２ｃが同方向の端部２ｄ，２ｅに対して
同一周方向に略同一量だけ偏位し、かつ歯筋方向
Ｓの中央に関して対称となるように形成されてい
る。なお、この歯付プーリ１に巻回される歯付ベ
ルトは、ストレートの歯部を有する周知のベルト
である。 The flank surface 2a of the toothed portion 2 of this toothed pulley 1,
2b, that is, both the front and rear surfaces in the circumferential direction are in the tooth trace direction S
The central portion 2c is deviated by approximately the same amount in the same circumferential direction with respect to the end portions 2d and 2e in the same direction, and is formed so as to be symmetrical with respect to the center in the tooth trace direction S. The toothed belt wound around the toothed pulley 1 is a well-known belt having straight teeth.
上記のように構成すれば、先ず、歯付プーリ１
と歯付ベルト３との噛合当初は、第２図に示すよ
うに、歯付プーリ１の歯部２のフランク面２ａと
歯付ベルト３の歯部４のフランク面４ａすなわち
前後面（第１４図参照）とが、２位置すなわち
P1，P2において接触する。 If configured as above, first, the toothed pulley 1
At the beginning of meshing between the toothed belt 3 and the toothed belt 3, as shown in FIG. (see figure) is in two positions, i.e.
Contact occurs at P 1 and P 2 .
その後、歯付ベルト３の歯部４に負荷が加わ
り、第３図に示すように、前記歯部４が歯付プー
リ１の歯部２のフランク面２ａの形状に沿うよう
に弾性変形し、歯付ベルト３の歯部４のフランク
面４ａが歯付プーリ１の歯部２のフランク面２ａ
に許容弾性範囲内で略全面接触し、完全に噛合
う。したがつて、歯付ベルト３の歯部４が歯付プ
ーリ１の歯部２と接触してから完全に噛合うまで
時間を要することとなり、その結果、衝突エネル
ギが分散され、駆動時（特に高速駆動時）に生じ
る騒音の低減が図れる。 Thereafter, a load is applied to the teeth 4 of the toothed belt 3, and as shown in FIG. 3, the teeth 4 are elastically deformed to follow the shape of the flank surface 2a of the teeth 2 of the toothed pulley 1. The flank surface 4a of the toothed portion 4 of the toothed belt 3 is the flank surface 2a of the toothed portion 2 of the toothed pulley 1.
Almost the entire surface contacts within the permissible elastic range and meshes perfectly. Therefore, it takes time for the teeth 4 of the toothed belt 3 to completely mesh with the teeth 2 of the toothed pulley 1, and as a result, the collision energy is dispersed, and during driving (especially The noise generated during high-speed driving can be reduced.
しかして、歯付ベルト３が歯付プーリ１より離
れるときは、第３図に示す状態から第２図に示す
状態に移行し、それから離れる。 When the toothed belt 3 separates from the toothed pulley 1, it shifts from the state shown in FIG. 3 to the state shown in FIG. 2, and then leaves.
続いて、本考案形の装置と従来形の装置とにつ
いて行つた試験について説明する。 Next, tests conducted on the device of the present invention and the conventional device will be explained.
−試験１−
〈試験方法〉
試験ベルトはＨタイプ（ピツチ127mm）で、ベ
ルト長さは833mmで、試験プーリは駆動側、従動
側とも26歯で、その他の寸法は第４図及び第５図
に示す通りである。すなわち、試験プーリ１１
（歯部１２）のプーリ幅L1＝40mm、試験ベルト１
３（歯部１４）のベルト幅L2＝38mm、試験プー
リ１１の歯部１２のフランク面１２ａにおける歯
筋方向中央部の歯筋方向端部に対する偏位量δ＝
0.8mmである。なお、第４図は２位置で、第５図
は１位置で接触する場合である（以下、凹当り、
凸当りという）。-Test 1- <Test method> The test belt is H type (pitch 127mm), belt length is 833mm, test pulley has 26 teeth on both drive side and driven side, other dimensions are as shown in Figures 4 and 5. As shown. That is, the test pulley 11
(tooth section 12) pulley width L 1 = 40 mm, test belt 1
3 (teeth portion 14) belt width L 2 = 38 mm, deviation amount δ of the center portion in the tooth trace direction on the flank surface 12a of the tooth portion 12 of the test pulley 11 with respect to the end portion in the tooth trace direction =
It is 0.8mm. Note that Fig. 4 shows the case of contact in the 2nd position, and Fig. 5 shows the case of contact in the 1st position (hereinafter referred to as concave contact,
(This is called a convex hit).
しかして、第６図ａ，ｂに示すように、駆動側
試験プーリ１１Ａ（2000〜7000rpm）と従動側試
験プーリ１１Ｂ（負荷0.72Kgｆ・ｍ）との間に試
験ベルト１３を巻回し、ベルト周速を10〜40m／
ｓへと変化させたとき、駆動側試験プーリ１１Ａ
からL4＝100mmだけ離れた所に精密騒音計１５
（1/3オクターブ周波数分析計）を配設し、騒音を
測定した。 As shown in FIGS. 6a and 6b, the test belt 13 is wound between the driving side test pulley 11A (2000 to 7000 rpm) and the driven side test pulley 11B (load 0.72 kgf m), and the belt circumference is Speed 10~40m/
When changing to s, the drive side test pulley 11A
Precision sound level meter 15 at a distance of L 4 = 100 mm from
(1/3 octave frequency analyzer) was installed to measure noise.
なお、従来形は、試験プーリの歯部をストレー
ト歯とした点を除いては同一である。 The conventional type is the same except that the teeth of the test pulley are straight teeth.
〈試験結果〉
第７図に示す通りである。すなわち、本考案形
は、ベルトスピードにかかわりなく、また、凹当
り、凸当りに関係なく音圧が従来形よりも小さ
く、騒音低減効果があることが判る。<Test results> As shown in Figure 7. In other words, it can be seen that the sound pressure of the present invention type is lower than that of the conventional type, regardless of the belt speed, and regardless of whether it hits a concave or a convex area, and has a noise reduction effect.
−試験２−
〈試験方法〉
試験ベルトはＨタイプで、ベルト幅25.4mm、ベ
ルト長さ833mmとする一方、駆動側及び従動側プ
ーリともに26歯とし、第６図に示すものと同様な
装置でもつて第４図に示す凹当りで負荷12HP，
4000rpmで走行試験を行い、偏位量δとベルト幅
Ｗとの比（δ／Ｗ）の騒音、ベルト寿命に対する
影響を調べた。なお、試験結果は、従来形（δ／
Ｗ＝０）の場合を100とし、指数表示した。-Test 2- <Test method> The test belt was an H type, with a belt width of 25.4 mm and a belt length of 833 mm, while both the drive side and driven side pulleys had 26 teeth. With the concave contact shown in Figure 4, the load is 12 HP.
A running test was conducted at 4000 rpm to investigate the effect of the ratio of deviation amount δ to belt width W (δ/W) on noise and belt life. The test results are based on the conventional type (δ/
W=0) was set as 100 and expressed as an index.
〈試験結果〉
第８図に示す通りである。すなわち、δ／Ｗの
増大に伴い、騒音指数が低下するが、寿命指数も
低下するため、実用上寿命指数の90％程度の低下
は許容できるから、０＜δ／Ｗ≦0.05が望まし
い。さらに、望ましくは、0.005≦δ／Ｗ≦0.05
である。<Test results> As shown in Figure 8. That is, as δ/W increases, the noise index decreases, but the life index also decreases, so a decrease of about 90% in the life index is practically acceptable, so it is desirable that 0<δ/W≦0.05. Furthermore, preferably 0.005≦δ/W≦0.05
It is.
上記実施例では歯付プーリ１の歯部２のフラン
ク面２ａ，２ｂが両方とも同一周方向に湾曲した
歯筋方向に曲面形状であるが、そのほか、第９図
ａに示すように、一方のフランク面２１ａを平坦
面、他方のフランク面２１ｂを周方向に突出した
湾曲面状とする歯部２１（片面凸当り）、第９図
ｂに示すように、一方のフランク面２２ａを平坦
面、他方のフランク面２２ｂを周方向にくぼんだ
湾曲面とする歯部２２（片面凹当り）、第９図ｃ
に示すように、両フランク面２３ａ，２３ｂとも
周方向に突出した歯部２３（両面凸当り）、第９
図ｄに示すように、両フランク面２４ａ，２４ｂ
とも周方向にくぼんだ歯部２４（両面凹当り）で
も、同様な効果が望める。 In the above embodiment, the flank surfaces 2a and 2b of the tooth portion 2 of the toothed pulley 1 are both curved in the same circumferential direction and curved in the direction of the tooth trace. Tooth portion 21 (convex on one side) in which the flank surface 21a is a flat surface and the other flank surface 21b is a curved surface projecting in the circumferential direction, as shown in FIG. 9b, one flank surface 22a is a flat surface, Tooth portion 22 with the other flank surface 22b being a curved surface concave in the circumferential direction (concave contact on one side), Fig. 9c
As shown in FIG. 2, both flank surfaces 23a and 23b have tooth portions 23 (convex contact on both sides) projecting in the circumferential direction, and a ninth
As shown in Figure d, both flank surfaces 24a, 24b
A similar effect can be expected even if the tooth portion 24 is recessed in the circumferential direction on both sides (concave contact on both sides).
また、湾曲面でなくとも、第１０図ａ〜ｃに示
すように、歯筋方向にＶ形状の歯部２５、中央部
２６ａが矩形状で両側にハの字形状の傾斜部２６
ｂ，２６ｃを有する歯筋方向に台形状の歯部２
６、ハの字形状の傾斜部２７ａ，２７ｂのみから
なる歯部２７であつても差支えない。そのほか、
歯筋方向に曲面と平面とを組合せて構成してもよ
い。また、プーリ製作上、２ケ又は３ケのプーリ
に分離し、それを組合わせ使用することもでき
る。 Even if the surface is not a curved surface, as shown in FIGS. 10a to 10c, the tooth portion 25 is V-shaped in the direction of the tooth trace, the central portion 26a is rectangular, and the inclined portions 26 are V-shaped on both sides.
A trapezoidal tooth portion 2 in the direction of the tooth trace having b and 26c.
6. The tooth portion 27 may be made of only the V-shaped inclined portions 27a and 27b. others,
It may be constructed by combining a curved surface and a flat surface in the direction of the tooth trace. In addition, when manufacturing the pulley, it is also possible to separate it into two or three pulleys and use them in combination.
上記歯部の形状は歯付プーリの歯部の形状とし
て説明したが、逆に歯付プーリの歯部はストレー
ト形状とし、歯付ベルトの歯部を上述した形状と
することもできる。 The shape of the toothed portion has been described as the shape of the toothed portion of a toothed pulley, but conversely, the toothed portion of the toothed pulley may have a straight shape, and the toothed portion of the toothed belt may have the above-mentioned shape.
また、第１１図ａ〜ｄに示すように、上述した
如き形状の歯部を有する歯付ベルトと歯付プーリ
とを組合せるようにしてもよい。すなわち、歯付
ベルト３１及び歯付プーリ３２ともに歯部３３，
３４が両フランク面３３ａ，３３ｂ，３４ａ，３
４ｂとも周方向に突出しているもの（第１１図ａ
参照）、歯付ベルト３５の歯部３８が両フランク
面３８ａ，３８ｂともに周方向に突出する一方、
歯付プーリ３７の歯部３６が両フランク面３６
ａ，３６ｂとも周方向にくぼんだもの（第１１図
ｂ参照）、歯付ベルト３９の歯部４０が両フラン
ク面４０ａ，４０ｂとも周方向にくぼむ一方、歯
付プーリ４１の歯部４２は両フランク面４２ａ，
４２ｂとも周方向に突出しているもの（第１１図
ｃ参照）、歯付ベルト４３、歯付プーリ４４とも
に歯部４５，４６のフランク面４５ａ，４５ｂ，
４６ａ，４６ｂが周方向にくぼんでいるもの（第
１１図ｄ参照）である。 Further, as shown in FIGS. 11a to 11d, a toothed belt having toothed portions having the shape described above and a toothed pulley may be combined. That is, both the toothed belt 31 and the toothed pulley 32 have toothed portions 33,
34 are both flank surfaces 33a, 33b, 34a, 3
4b both protrude in the circumferential direction (Fig. 11a)
), while the toothed portion 38 of the toothed belt 35 protrudes in the circumferential direction on both flank surfaces 38a and 38b,
The teeth 36 of the toothed pulley 37 are on both flank surfaces 36
Both flanks 40a and 36b are recessed in the circumferential direction (see FIG. 11b), and the toothed portion 40 of the toothed belt 39 is recessed in the circumferential direction on both flank surfaces 40a and 40b, while the toothed portion 42 of the toothed pulley 41 is recessed in the circumferential direction. are both flank surfaces 42a,
Both 42b protrude in the circumferential direction (see FIG. 11c), and the toothed belt 43 and toothed pulley 44 both have flank surfaces 45a, 45b of toothed portions 45, 46,
46a and 46b are recessed in the circumferential direction (see FIG. 11d).
さらに、第１２図ａに示すように、第１図に示
す歯付プーリ１の歯部２の歯先面である外周面
（ランド面）２ｆを、軸方向中央部が半径方向外
方に突出する湾曲面（いわゆるクラウン）とすれ
ば、ベルト駆動時において、フランク面による騒
音の減少と外周面によるベルトの横ずれ防止を図
ることもできる。また、第１２図ｂ〜ｅに示すよ
うに、第９図ａ〜ｄに示す歯付プーリの歯部２
１，２２，２３，２４の外周面２１ｃ，２２ｃ，
２３ｃ，２４ｃを湾曲面とした場合も同様であ
る。 Furthermore, as shown in FIG. 12a, the outer peripheral surface (land surface) 2f, which is the tooth tip surface of the tooth portion 2 of the toothed pulley 1 shown in FIG. If the belt has a curved surface (so-called crown), it is possible to reduce noise due to the flank surface and prevent the belt from shifting laterally due to the outer circumferential surface when the belt is driven. Moreover, as shown in FIGS. 12b to 12e, the toothed portion 2 of the toothed pulley shown in FIGS. 9a to d
1, 22, 23, 24 outer peripheral surfaces 21c, 22c,
The same applies when 23c and 24c are curved surfaces.
そのほか、騒音の減少と横ずれの防止を図るこ
とができる歯付プーリと歯付ベルトとの組合せと
しては、第１３図ａ〜ｆに示すものがある。すな
わち、外周面５１ａが湾曲面であるストレートの
歯部５１を有する歯付プーリ５２と、歯部５３の
両フランク面５３ａ，５３ｂが周方向において突
出する歯付ベルト５４との組合せ（第１３図ａ参
照）、第１３図ａの歯付プーリ５２と、歯部５５
の両フランク面５５ａ，５５ｂが周方向において
くぼんでいる歯付ベルト５６との組合せ（第１３
図ｂ参照）、第１２図ｃの歯付プーリと第１３図
ａの歯付ベルト５４との組合せ（第１３図ｃ参
照）、第１２図ｃの歯付プーリと第１３図ｂの歯
付ベルト５６との組合せ（第１３図ｄ参照）、第
１２図ｅの歯付プーリと第１３図ａの歯付ベルト
５４との組合せ（第１３図ｅ参照）、第１２図ｅ
の歯付プーリと第１３図ｂの歯付ベルト５６との
組合せ（第１３図ｆ参照）がある。 In addition, there are combinations of toothed pulleys and toothed belts that can reduce noise and prevent lateral slippage, as shown in FIGS. 13a to 13f. That is, a combination of a toothed pulley 52 having a straight toothed portion 51 whose outer peripheral surface 51a is a curved surface, and a toothed belt 54 in which both flank surfaces 53a and 53b of the toothed portion 53 protrude in the circumferential direction (Fig. 13). a), the toothed pulley 52 and toothed portion 55 in FIG. 13a.
A combination with a toothed belt 56 in which both flank surfaces 55a and 55b of the
(see Figure b), a combination of the toothed pulley in Figure 12c and the toothed belt 54 in Figure 13a (see Figure 13c), a combination of the toothed pulley in Figure 12c and the toothed belt 54 in Figure 13b Combination with belt 56 (see Figure 13 d), combination of toothed pulley in Figure 12 e and toothed belt 54 in Figure 13 a (see Figure 13 e), Figure 12 e
There is a combination of the toothed pulley shown in FIG. 13 and the toothed belt 56 shown in FIG. 13b (see FIG. 13f).
なお、上記実施例において、歯付プーリの歯部
の外周面が湾曲面のときは、その歯溝の底面も湾
曲面である。また、試験１と同一条件で凹当りで
外周面の突出量0.2mmとし、ベルトスピード
34m／secで試験したところ、音圧は106dBAであ
つた。このことから、外周面を湾曲面とすること
により、さらに2dBA程度音圧が小さくなること
がわかる。又、プーリの外周面が凹状でも、その
効果を有している。 In the above embodiment, when the outer peripheral surface of the teeth of the toothed pulley is a curved surface, the bottom surface of the tooth groove is also a curved surface. In addition, under the same conditions as Test 1, the protrusion amount of the outer peripheral surface was 0.2 mm at the concave contact, and the belt speed was
When tested at 34 m/sec, the sound pressure was 106 dBA. From this, it can be seen that by making the outer peripheral surface a curved surface, the sound pressure can be further reduced by about 2 dBA. Further, even if the outer circumferential surface of the pulley is concave, the same effect can be obtained.
（考案の効果）
本考案は、上記のように、歯付プーリ又は歯付
ベルトの一方の歯部のフランク面が、歯筋方向中
央部が歯筋方向端部に対して周方向に偏位しかつ
歯筋方向中央に関して対称となるように形成さ
れ、前記一方の歯部のフランク面が、他方の歯部
のフランク面に対し、歯付ベルトとプーリとの噛
合当初歯付ベルトの歯部とプーリの歯部との接触
が歯筋方向において１位置又は２位置で、その後
全体が接触するように構成したから、ベルト駆動
時において、安定性よく噛合し、効果的に騒音の
低減を図ることができる。(Effect of the invention) As described above, the present invention has the advantage that the flank surface of one of the teeth of a toothed pulley or a toothed belt is such that the central part in the tooth trace direction is offset in the circumferential direction with respect to the end part in the tooth trace direction. In addition, the toothed belt is formed symmetrically with respect to the center in the tooth trace direction, and the flank surface of the one toothed portion is symmetrical with respect to the flank surface of the other toothed portion at the time of meshing of the toothed belt and the pulley. Since the contact between the pulley and the teeth of the pulley is made in one or two positions in the direction of the tooth trace, and then the entire contact is made, the mesh is stable and the noise is effectively reduced when the belt is driven. be able to.
図面は本考案の実施例を示し、第１図は歯付ベ
ルト駆動装置を構成する歯付プーリの斜視図、第
２図及び第３図は動作を示す説明図、第４図乃至
第６図は試験についての説明図、第７図及び第８
図は試験結果を示す図、第９図乃至第１３図は変
形例の説明図、第１４図は歯付ベルトの説明図で
ある。
１……歯付プーリ、２……歯部、２ａ，２ｂ…
…フランク面、２ｃ……中央部、２ｄ，２ｅ……
端部、２ｆ……外周面、３……歯付ベルト、４…
…歯部。
The drawings show an embodiment of the present invention, in which Fig. 1 is a perspective view of a toothed pulley constituting a toothed belt drive device, Figs. 2 and 3 are explanatory diagrams showing the operation, and Figs. 4 to 6. are explanatory diagrams for the test, Figures 7 and 8.
The figure shows test results, FIGS. 9 to 13 are explanatory views of modified examples, and FIG. 14 is an explanatory view of a toothed belt. 1...Toothed pulley, 2...Tooth portion, 2a, 2b...
...Flank surface, 2c...Central part, 2d, 2e...
End, 2f...Outer peripheral surface, 3...Toothed belt, 4...
...Tooth area.
Claims (1)
ので、前記歯付プーリ又は歯付ベルトの一方の
歯部のフランク面が、歯筋方向中央部が歯筋方
向端部に対して周方向に偏位しかつ歯筋方向中
央に関して対称となるように形成され、前記一
方の歯部のフランク面が、他方の歯部のフラン
ク面に対し、歯付ベルトとプーリとの噛合当初
歯付ベルトの歯部とプーリの歯部との接触が歯
筋方向において１位置又は２位置で、その後全
体が接触するように構成されていることを特徴
とする歯付ベルト駆動装置。 (2) 他方の歯部のフランク面がストレート形状に
形成され、歯付ベルトの幅をＷ、歯筋方向中央
部の歯筋方向端部に対するフランク面の周方向
の偏位量をδとするとき、 ０＜δ／Ｗ≦0.05 である実用新案登録請求の範囲第１項記載の歯
付ベルト駆動装置。 (3) 歯付ベルト又は歯付プーリの少なくとも一方
の歯部のフランク面が、歯筋方向に曲面形状で
あるところの実用新案登録請求の範囲第１項記
載の歯付ベルト駆動装置。 (4) 歯付ベルト又は歯付プーリの少なくとも一方
の歯部のフランク面が、歯筋方向にＶ形状であ
るところの実用新案登録請求の範囲第１項記載
の歯付ベルト駆動装置。 (5) 歯付ベルト又は歯付プーリの少なくとも一方
の歯部のフランク面が、歯筋方向に台形状であ
るところの実用新案登録請求の範囲第１項記載
の歯付ベルト駆動装置。 (6) 歯付ベルト又は歯付プーリの少なくとも一方
の歯部のフランク面が、歯筋方向に曲面と平面
とを組合せて構成されるところの実用新案登録
請求の範囲第１項記載の歯付ベルト駆動装置。 (7) 歯付ベルトの幅Ｗと、フランク面の周方向の
偏位量δとの関係は、 0.005≦δ／Ｗ≦0.05 であるところの実用新案登録請求の範囲第２項
記載の歯付ベルト駆動装置。 (8) 歯付プーリの歯部は、外周面が歯筋方向中央
部が半径方向外方に突出する凸面形状であると
ころの実用新案登録請求の範囲第１項乃至第７
項の何れかに記載の歯付ベルト駆動装置。[Claims for Utility Model Registration] (1) A toothed belt is wound around a toothed pulley, and the flank surface of one of the teeth of the toothed pulley or the toothed belt is located at the central part in the tooth trace direction. is formed so as to be offset in the circumferential direction with respect to the end in the tooth trace direction and symmetrical with respect to the center in the tooth trace direction, and the flank surface of the one tooth portion is symmetrical with respect to the flank surface of the other tooth portion. At the beginning of the meshing of the belt with the toothed belt and the pulley, the toothed part of the toothed belt and the toothed part of the pulley contact at one or two positions in the direction of the tooth trace, and then the whole part comes into contact with each other. Toothed belt drive device. (2) The flank surface of the other toothed portion is formed in a straight shape, the width of the toothed belt is W, and the deviation amount of the flank surface in the circumferential direction from the end in the tooth trace direction of the central part in the tooth trace direction is δ. The toothed belt drive device according to claim 1, wherein: 0<δ/W≦0.05. (3) The toothed belt drive device according to claim 1, wherein the flank surface of the teeth of at least one of the toothed belt or the toothed pulley is curved in the tooth trace direction. (4) The toothed belt drive device according to claim 1, wherein the flank surface of the teeth of at least one of the toothed belt or the toothed pulley is V-shaped in the tooth trace direction. (5) The toothed belt drive device according to claim 1, wherein the flank surface of the teeth of at least one of the toothed belt or the toothed pulley is trapezoidal in the tooth trace direction. (6) The toothed belt according to claim 1, wherein the flank surface of at least one of the teeth of the toothed belt or the toothed pulley is composed of a combination of a curved surface and a flat surface in the tooth trace direction. Belt drive. (7) The toothed belt according to claim 2, wherein the relationship between the width W of the toothed belt and the deviation amount δ of the flank surface in the circumferential direction is 0.005≦δ/W≦0.05. Belt drive. (8) The toothed portion of the toothed pulley has a convex outer circumferential surface in which the central portion in the direction of the tooth trace protrudes outward in the radial direction.
The toothed belt drive device according to any one of Items 1 to 3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10543384U JPS6120948U (en) | 1984-07-11 | 1984-07-11 | Toothed belt drive device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10543384U JPS6120948U (en) | 1984-07-11 | 1984-07-11 | Toothed belt drive device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6120948U JPS6120948U (en) | 1986-02-06 |
| JPH0126928Y2 true JPH0126928Y2 (en) | 1989-08-11 |
Family
ID=30664759
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10543384U Granted JPS6120948U (en) | 1984-07-11 | 1984-07-11 | Toothed belt drive device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6120948U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10716912B2 (en) | 2015-03-31 | 2020-07-21 | Fisher & Paykel Healthcare Limited | User interface and system for supplying gases to an airway |
| US11324908B2 (en) | 2016-08-11 | 2022-05-10 | Fisher & Paykel Healthcare Limited | Collapsible conduit, patient interface and headgear connector |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100509602C (en) * | 2003-02-07 | 2009-07-08 | 奥蒂斯电梯公司 | Elevator strap and elevator system with the strap |
| JP2005351425A (en) * | 2004-06-11 | 2005-12-22 | Bando Chem Ind Ltd | Toothed pulley and belt-type transmission provided with the same |
| JP5803804B2 (en) * | 2012-05-16 | 2015-11-04 | トヨタ自動車株式会社 | Belt drive |
-
1984
- 1984-07-11 JP JP10543384U patent/JPS6120948U/en active Granted
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10716912B2 (en) | 2015-03-31 | 2020-07-21 | Fisher & Paykel Healthcare Limited | User interface and system for supplying gases to an airway |
| US11904097B2 (en) | 2015-03-31 | 2024-02-20 | Fisher & Paykel Healthcare Limited | User interface and system for supplying gases to an airway |
| US11324908B2 (en) | 2016-08-11 | 2022-05-10 | Fisher & Paykel Healthcare Limited | Collapsible conduit, patient interface and headgear connector |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6120948U (en) | 1986-02-06 |
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