JPS63106453A - Timing belt mechanism - Google Patents
Timing belt mechanismInfo
- Publication number
- JPS63106453A JPS63106453A JP24841186A JP24841186A JPS63106453A JP S63106453 A JPS63106453 A JP S63106453A JP 24841186 A JP24841186 A JP 24841186A JP 24841186 A JP24841186 A JP 24841186A JP S63106453 A JPS63106453 A JP S63106453A
- Authority
- JP
- Japan
- Prior art keywords
- pulley
- belt
- tension
- toothed
- timing belt
- 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.)
- Pending
Links
- 230000007246 mechanism Effects 0.000 title claims description 20
- 230000000694 effects Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005259 measurement 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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H2035/003—Gearings comprising pulleys or toothed members of non-circular shape, e.g. elliptical gears
-
- 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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
-
- 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
- F16H7/08—Means for varying tension of belts, ropes, or chains
- F16H7/0829—Means for varying tension of belts, ropes, or chains with vibration damping means
Landscapes
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明はタイミングベルト機構、特にタイミングベルト
機構におけるタイミングベルトの共振抑制装置に関する
ものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a timing belt mechanism, and particularly to a timing belt resonance suppressing device in a timing belt mechanism.
自動車等において駆動側から被駆動側に動力を正確に伝
達するためタイミングベルト機構が用いられている。こ
のタイミングベルト機構はローラチェーン、歯車等と同
様に、歯付きプーリとこれに噛み合う歯付きベルトから
なるものである（実開昭５７−１７２９５６号公報参照
）。Timing belt mechanisms are used in automobiles and the like to accurately transmit power from the driving side to the driven side. This timing belt mechanism consists of a toothed pulley and a toothed belt that meshes with the toothed pulley, similar to a roller chain, gears, etc. (see Japanese Utility Model Publication No. 172956/1983).
上記のタイミングベルト機構を例えば自動車の動弁機構
においてクランクシャフトとカムシャフトとの間に用い
た場合は、被駆動側のカムシャフトの負荷の変動に伴い
、タイミングベルトの張力が変動しこの変動が大きい共
振点において同ベルトは激しく振動し、そのためベルト
とプーリとの噛み合いが悪くなる。この影響でクランク
シャフトの回転とバルブ作動のタイミングにずれが生じ
、回転変動をひき起す原因となる。またベルトとプーリ
との噛み合いが不十分となりベルトの歯にかかる荷重が
増加しベルトの歯の寿命に悪影響を及ぼすことになる。When the above-mentioned timing belt mechanism is used between the crankshaft and the camshaft in a car's valve train, for example, the tension of the timing belt fluctuates as the load on the driven camshaft fluctuates. At large resonance points, the belt vibrates violently, resulting in poor engagement between the belt and the pulleys. This effect causes a lag between the rotation of the crankshaft and the timing of valve operation, causing rotational fluctuations. Furthermore, the meshing between the belt and the pulley becomes insufficient, increasing the load on the teeth of the belt, which has a negative effect on the life of the teeth of the belt.
したがって、このようなタイミングベルト機構は共振を
抑制する手段を講じる必要がある。Therefore, it is necessary for such a timing belt mechanism to take measures to suppress resonance.
本発明によれば上記の問題点は、歯付き駆動プーリと歯
付き被駆動プーリとの間に歯付きベルトを掛け渡したタ
イミングベルト機構において、前記駆動プーリと被駆動
プーリとの間にさらに前記歯付きベルトと噛み合う中間
歯付きプーリを介在させ、該中間歯付きプーリの歯先円
を非円形となして該プーリの中心から最小距離の歯先部
と最大距離の歯先部とを形成し、前記最小距離の歯先部
を前記歯付きベルトが最大張力となる時該ベルトとの噛
み合い部の中心位置に、前記最大距離の歯先部を前記歯
付きベルトが最小張力となる時該ベルトとの噛み合い部
の中心位置に、それぞれ位置させるよう配置したことを
特徴とするタイミングベルト機構によって解決される。According to the present invention, the above problem can be solved in a timing belt mechanism in which a toothed belt is stretched between a toothed drive pulley and a toothed driven pulley. An intermediate toothed pulley that meshes with the toothed belt is interposed, and the tooth tip circle of the intermediate toothed pulley is made non-circular to form a tooth tip portion having a minimum distance from the center of the pulley and a tooth tip portion having a maximum distance from the center of the pulley. , the tips of the teeth at the minimum distance are placed at the center of the meshing portion with the belt when the toothed belt is at maximum tension, and the tips of the teeth at the maximum distance are placed at the center position of the meshing part with the toothed belt when the toothed belt is at the minimum tension. This problem is solved by a timing belt mechanism characterized in that the timing belt mechanism is arranged so as to be located at the center of the meshing portion with the timing belt mechanism.
上記の構成からなる本発明によれば、ベルトの張力が最
大となる位置で中間歯付きプーリの最小距離の歯先部が
前記ベルトとの噛み合い部の中心位置にくるので、ベル
ト全体の長さが収縮し、そのため張力の増加は抑制され
張力変動の最大値は小さくなる。一方、ベルトの張力が
最小となる位置では中間歯付きプーリの最大距離の歯先
部がベルトとの噛み合い部の中心位置にくるので、ベル
ド全体の長さは伸長しそのためベルトの張力は増太し張
力変動の最小値は大きくなる。According to the present invention having the above configuration, since the tip of the teeth of the intermediate toothed pulley at the minimum distance is located at the center position of the meshing portion with the belt at the position where the tension of the belt is maximum, the entire length of the belt is contracts, so the increase in tension is suppressed and the maximum value of tension fluctuation becomes smaller. On the other hand, at the position where the belt tension is minimum, the tooth tips of the intermediate toothed pulley with the longest distance are located at the center of the meshing part with the belt, so the overall length of the belt is elongated and the belt tension increases. Therefore, the minimum value of tension fluctuation becomes larger.
したがってベルト全体の張力変動の振幅が小さくなり、
この張力変動の減少により共振の度合が抑制されるもの
となる。Therefore, the amplitude of tension fluctuation across the belt becomes smaller,
This reduction in tension fluctuations suppresses the degree of resonance.
本発明の実施例を図面を参照して以下に説明する。第１
図は本発明の第１の実施例を示し、本実施例は、本発明
のタイミングベルト機構を４気筒エンジンの動弁系−１
すなわちクランクシャフトとバルブ駆動用のカムシャフ
トとの間に適用したものである。Embodiments of the present invention will be described below with reference to the drawings. 1st
The figure shows a first embodiment of the present invention, in which the timing belt mechanism of the present invention is applied to a valve train of a four-cylinder engine.
That is, it is applied between a crankshaft and a camshaft for driving valves.
図中、１は歯の設けられたカムシャフトプーリ、２は歯
の設けられたクランクシャフトプーリ、３は歯の設けら
れたタイミングベルトであって、プーリ１，２の歯がタ
イミングベルト３の歯に噛み合い、クランクシャフトプ
ーリ２からタイミングベルト３を介してカムシャフトプ
ーリｌに回転力が伝達されるようになっている。In the figure, 1 is a camshaft pulley with teeth, 2 is a crankshaft pulley with teeth, 3 is a timing belt with teeth, and the teeth of pulleys 1 and 2 are the teeth of timing belt 3. The rotational force is transmitted from the crankshaft pulley 2 to the camshaft pulley l via the timing belt 3.
両プーリ１，２の中間にさらに歯の設けられたオイルポ
ンププーリ４が設けられ、このプーリ４の歯がタイミン
グベルト３と噛み合いクランクシャフト（図示せず）か
らの回転力が伝達される。An oil pump pulley 4 having teeth is further provided between both pulleys 1 and 2, and the teeth of this pulley 4 mesh with the timing belt 3 to transmit rotational force from a crankshaft (not shown).
このプーリ４はオイルポンプ（図示しない）を駆動する
ためのプーリである。オイルポンププーリ４は従来のプ
ーリと異なり、その外周が非円形であり、その中心０か
らの距離が最大となる長径部Ｃ−Ｄと最小となる短径部
Ｆ−Ｅとが形成されている。５はアイドラプーリで、テ
ンシシンプーリ６によりタイミングベルト３の張力を調
節する。This pulley 4 is a pulley for driving an oil pump (not shown). The oil pump pulley 4 is different from conventional pulleys in that its outer periphery is non-circular, and has a long diameter section C-D where the distance from the center 0 is the maximum and a short diameter section FE where the distance is the minimum. . Reference numeral 5 denotes an idler pulley, which adjusts the tension of the timing belt 3 by means of a tension pulley 6.
同図において矢印Ｇはクランクシャフトプーリ２の回転
方向を示す。またカムシャフトプーリ１上の点Ａが点Ｂ
の位置にある時バルブの負荷が最大（クランク角度で上
死点から約７０°のところ）となりベルト３の張力が最
大となるものとする。In the figure, arrow G indicates the direction of rotation of the crankshaft pulley 2. Also, point A on camshaft pulley 1 is point B
At this position, the load on the valve is maximum (approximately 70° from top dead center in terms of crank angle) and the tension on the belt 3 is maximum.
本実施例では、第１図に示すように、ベルト３の張力が
最大となる位置において、オイルポンププーリ４は、そ
の短径部Ｆ−Ｅの一方の端部Ｅ又はＦがベルト３との噛
み合い部の中心位置に（るように配置する。またバルブ
の負荷が最小となりベルト３の張力が最小となる位置（
カムシャフトプーリｌが第１図の位置から９０°回転し
た位置）では、オイルポンプブー＋７４はその長径部Ｃ
−Ｄの一方の端部Ｃ又はＤがベルト３との噛み合い部の
中心位置にくるように配置する。In this embodiment, as shown in FIG. 1, at the position where the tension of the belt 3 is maximum, the oil pump pulley 4 has one end E or F of its short diameter portion FE that is in contact with the belt 3. It is located at the center position of the meshing part (.Also, it is located at the position where the load on the valve is minimum and the tension on the belt 3 is minimum (
At a position where the camshaft pulley l is rotated 90 degrees from the position shown in Figure 1), the oil pump boo
-D is arranged so that one end C or D is located at the center of the meshing part with the belt 3.
このようにオイルポンププーリ４を配置することにより
、ベルト３の張力の最大の時はオイルポンププーリ４の
短径部Ｆ−Ｅがベルト３と噛み合うのでベルト３全体の
長さは収縮し、そのためベルトの張力の増加は抑制され
張力変動の最大値は小さくなる。一方、ベルト３の張力
の最小の時はオイルポンププーリ４はその長径部Ｃ−Ｄ
がベルト３と噛み合うのでベルト３全体の長さは伸長し
、そのためベルトの張力は増大し張力の最小値を増加さ
せるものとなる。この結果ベルト３の張力の最大値と最
小値との差が少なくなり、張力変動の振幅は減少し共振
の度合は抑制されることとなる。By arranging the oil pump pulley 4 in this way, when the tension of the belt 3 is at its maximum, the short diameter portion F-E of the oil pump pulley 4 engages with the belt 3, so that the entire length of the belt 3 contracts. The increase in belt tension is suppressed and the maximum value of tension fluctuation is reduced. On the other hand, when the tension of the belt 3 is minimum, the oil pump pulley 4 is
meshes with the belt 3, the overall length of the belt 3 is elongated, so that the tension in the belt increases and the minimum value of the tension increases. As a result, the difference between the maximum and minimum tension values of the belt 3 is reduced, the amplitude of tension fluctuations is reduced, and the degree of resonance is suppressed.
さらに本実施例におけるオイルポンププーリ４のような
非円形プーリを用いた場合の、同プーリ４の形状及び歯
数について説明する。Furthermore, when a non-circular pulley like the oil pump pulley 4 in this embodiment is used, the shape and number of teeth of the oil pump pulley 4 will be explained.
−ｉに、非円形プーリ４の歯数Ｚａ及び同プーリ４の中
心０から歯までの距離が最大となる箇所の数ｎはＮ気筒
およびクランクシャフトプーリの歯数が２であるエンジ
ンに適用した場合、Ｚａ＝ｋ・Ｚ （ｋ＝１，２．３−
）
ｎ＝（ｋ−Ｎ）／２
となる。ただしＮおよびｋが奇数の場合ｎは整数でな（
なるので、気筒数が奇数個の時はｋは偶数でなければな
らない。-i, the number of teeth Za of the non-circular pulley 4 and the number n of points where the distance from the center 0 to the teeth of the same pulley 4 is maximum are applied to an engine with N cylinders and a crankshaft pulley with 2 teeth. In the case, Za=k・Z (k=1, 2.3−
) n=(k-N)/2. However, if N and k are odd numbers, n must be an integer (
Therefore, when the number of cylinders is odd, k must be an even number.
なお、歯を有しないアイドラプーリを用いた場合はアイ
ドラプーリの回転数とクランクシャフトプーリの回転数
とが完全には一致しないためベルトの張力変動にタイミ
ングを合せることが不可能であるので効果はない。Note that if an idler pulley without teeth is used, the rotation speed of the idler pulley and the rotation speed of the crankshaft pulley will not completely match, so it will be impossible to match the timing to belt tension fluctuations, so it will not be effective. do not have.
本実施例のように４気筒エンジンではカムシャフトプー
リ１を回転させ吸排気パルプを開閉するためのベルト張
力変動のピークはカムシャフトプーリ１の１回転、ある
いはクランクシャフトプーリ２の２回転につき４回現れ
ることになる。そこで図に示すようにクランクシャフト
プーリ２と同歯数の非円形プーリ４を用いた場合、プー
リ４の中心Ｏから歯までの距離は、互いに対称となる２
箇所Ｃ及びＤで最大となり、Ｅ及びＦで最小となる。In a 4-cylinder engine as in this example, the peak of the belt tension fluctuation for rotating the camshaft pulley 1 to open and close the intake and exhaust pulps is 4 times per 1 revolution of the camshaft pulley 1 or 2 revolutions of the crankshaft pulley 2. It will appear. Therefore, as shown in the figure, when a non-circular pulley 4 with the same number of teeth as the crankshaft pulley 2 is used, the distances from the center O of the pulley 4 to the teeth are symmetrical to each other.
It is maximum at locations C and D, and minimum at locations E and F.
第２図、第３図に、４気筒エンジンにおけるベルト３の
張力の測定結果を示す。第２図は円形オイルポンププー
リを用い（従来例）、第３図は本実施例の非円形オイル
ポンププーリ４を用いた結果をそれぞれ示すものである
。円形オイルポンププーリを用いた時に見られた共振に
よる張力増加Ｇが非円形オイルポンププーリ４を用いた
本実施例では見られず共振が抑制されているのがわかる
。FIG. 2 and FIG. 3 show the measurement results of the tension of the belt 3 in a four-cylinder engine. FIG. 2 shows the results using a circular oil pump pulley (conventional example), and FIG. 3 shows the results using the non-circular oil pump pulley 4 of this embodiment. It can be seen that the increase in tension G due to resonance, which was observed when a circular oil pump pulley was used, was not observed in this example using a non-circular oil pump pulley 4, and resonance was suppressed.
第４図は本発明の第２実施例における非円形プーリの形
状を示すものである。FIG. 4 shows the shape of a non-circular pulley in a second embodiment of the invention.
第２実施例は本発明のタイミングベルト機構を６気筒エ
ンジンの動弁機構に適用したものである。In the second embodiment, the timing belt mechanism of the present invention is applied to a valve mechanism of a six-cylinder engine.
６気筒エンジンは前記の張力変動のピークが６回あるた
め、クランクシャフトプーリ２と同歯数のプーリ４を用
いた場合、プーリ４の中心Ｏから歯までの距ＭＯ−ａ
ｐ Ｏ−ｂ 、 Ｏ−ｃの３箇所で最大となり、Ｏ−ｄ
、Ｏ−ｅ、Ｏ−ｆの３箇所で最小となる。また中心を通
る線分２−ｅ、ｂ−ｆ。In a 6-cylinder engine, the above-mentioned tension fluctuation peaks six times, so when using a pulley 4 with the same number of teeth as the crankshaft pulley 2, the distance from the center O of the pulley 4 to the teeth MO-a
p is maximum at three locations, O-b and O-c, and O-d
, O-e, and Of. Also, line segments 2-e and b-f passing through the center.
ｃ−ｄはそれぞれ６０°で交わる。c and d intersect at 60°.
また６気筒エンジンの場合、タイミングベルト３の張力
の最大となる位置、すなわちバルブの負荷が最大となる
クランク角度は上死点から約８０゜ずれたところにある
ため、その点で非円形オイルポンププーリの点ｄ、ｅ、
ｆのいずれかがベルト３との噛み合いの中心位置にくる
よう配設する。In addition, in the case of a 6-cylinder engine, the position where the tension of the timing belt 3 is maximum, that is, the crank angle where the valve load is maximum, is approximately 80° away from top dead center, so at that point, the non-circular oil pump Pulley points d, e,
f is located at the center of engagement with the belt 3.
またタイミングベルト３の張力が最小となる点は前述の
最大張力の点からクランク角で６０°のところにあり、
非円形オイルポンププーリ４上の、ａ、ｂ、ｃ点のいず
れかがベルト３との噛み合いの中心位置にくるようにす
る。Furthermore, the point at which the tension of the timing belt 3 is at its minimum is at a crank angle of 60 degrees from the point of the maximum tension mentioned above.
Make sure that any one of points a, b, and c on the non-circular oil pump pulley 4 is at the center of engagement with the belt 3.
このようなオイルポンプブーＩ７４の配置により、第１
実施例の場合と同様に、ベルト３の最大張力時にベルト
の全長は収縮し、そのため張力の最大値は減少し、ベル
ト３の最小張力時には逆にベルトの全長は伸長し、張力
の最小値は増大し、その結果ベルト張力の変動の振幅が
減少するものとなる。With this arrangement of the oil pump boo I74, the first
As in the case of the embodiment, when the belt 3 has the maximum tension, the total length of the belt contracts, so the maximum value of the tension decreases, and when the belt 3 has the minimum tension, the total length of the belt expands, and the minimum value of the tension decreases. This results in a decrease in the amplitude of the belt tension fluctuations.
第５図、第６図は本発明の第３実施例における非円形プ
ーリの形状を示すものである。5 and 6 show the shape of a non-circular pulley in a third embodiment of the present invention.
同図に示す実施例はプーリ４のピッチ径を増減するので
はなく、特定の歯の高さを増加させることによりタイミ
ングベルト３の共振を抑制するものである。４気筒エン
ジンの場合ＲとＳの２ケ所、６気筒エンジンの場合はＲ
，Ｔ、Ｕの３ケ所の歯の高さを増加させる。ここで図中
αは１２０゛である。この高さを増加させた歯を張力変
動が最小となる点、すなわち上死点からの角度が４気筒
エンジンでは約１６０°、６気筒エンジンでは約１７０
゜の点でかみ合いの中心にくるよう配設すると前述と同
様の作用によりタイミングベルト３の振幅は減少し、共
振が抑制されるものとなる。In the embodiment shown in the figure, resonance of the timing belt 3 is suppressed by increasing the height of a specific tooth, rather than increasing or decreasing the pitch diameter of the pulley 4. For a 4-cylinder engine, there are two locations, R and S. For a 6-cylinder engine, there are two locations, R and S.
, T, and U are increased in height. Here, α in the figure is 120°. The point where the tension fluctuation is minimum, that is, the angle from top dead center of the tooth with increased height, is approximately 160° for a 4-cylinder engine and approximately 170° for a 6-cylinder engine.
If the timing belt 3 is disposed so as to be located at the center of meshing at the point .degree., the amplitude of the timing belt 3 will be reduced by the same effect as described above, and resonance will be suppressed.
本発明は以上のように、タイミングベルト機構において
、ベルトの張力が最大となる時はベルトの全長を減少さ
せてその張力を減少させ、ベルトの張力が最小となる時
には逆にベルトの全長を伸長してその張力を増大するよ
うにしているので、ベルトの最大張力と最小張力との差
を少なくする、すなわちベルトの加振要因の１つである
張力変動の振幅を減少することができ、共振の度合を抑
制することができる。As described above, in a timing belt mechanism, the present invention reduces the total length of the belt to reduce the tension when the belt tension is at a maximum, and conversely increases the total length of the belt when the belt tension is at a minimum. This makes it possible to reduce the difference between the maximum and minimum belt tensions, that is, to reduce the amplitude of tension fluctuations, which is one of the causes of belt vibration, and to reduce resonance. It is possible to suppress the degree of
またそのため、プーリとベルトとの噛み合いは確実とな
りベルトの歯にかかる荷重の増加は回避されベルトの寿
命を延長することができる。Furthermore, the engagement between the pulley and the belt is ensured, an increase in the load applied to the teeth of the belt is avoided, and the life of the belt can be extended.
第１図は本発明の第１実施例の概略図、第２図は従来の
タイミングベルト機構におけるベルト張力の変動を示す
グラフ、第３図は本発明のタイミングベルトａ構におけ
るベルト張力の変動を示すグラフ、第４図は本発明の第
２実施例における非円形プーリの拡大正面図、第５図は
本発明の第３実施例における非円形プーリの拡大正面図
、第６図は第５図のＨ部の拡大図である。
１…カムシャフトプーリ、
２…クランクシャフトプーリ、
３…タイミングベルト、
４…オイルポンププーリ。FIG. 1 is a schematic diagram of the first embodiment of the present invention, FIG. 2 is a graph showing variations in belt tension in a conventional timing belt mechanism, and FIG. 3 is a graph showing variations in belt tension in the timing belt a structure of the present invention. 4 is an enlarged front view of a non-circular pulley in a second embodiment of the present invention, FIG. 5 is an enlarged front view of a non-circular pulley in a third embodiment of the present invention, and FIG. 6 is an enlarged front view of a non-circular pulley in a third embodiment of the present invention. It is an enlarged view of the H section. 1...Camshaft pulley, 2...Crankshaft pulley, 3...Timing belt, 4...Oil pump pulley.
Claims (2)
付きベルトを掛け渡したタイミングベルト機構において
、前記駆動プーリと被駆動プーリとの間にさらに前記歯
付きベルトと噛み合う中間歯付きプーリを介在させ、該
中間歯付きプーリの歯先円を非円形となして該プーリの
中心から最小距離の歯先部と最大距離の歯先部とを形成
し、前記最小距離の歯先部を前記歯付きベルトが最大張
力となる時該ベルトとの噛み合い部の中心位置に、前記
最大距離の歯先部を前記歯付きベルトが最小張力となる
時該ベルトとの噛み合い部の中心位置に、それぞれ位置
させるよう配置したことを特徴とするタイミングベルト
機構。1. In a timing belt mechanism in which a toothed belt is stretched between a toothed drive pulley and a toothed driven pulley, an intermediate toothed pulley that meshes with the toothed belt is further interposed between the drive pulley and the driven pulley. The tooth tip circle of the intermediate toothed pulley is made non-circular to form a tooth tip portion having a minimum distance from the center of the pulley and a tooth tip portion having a maximum distance from the center of the pulley, and the tooth tip portion having the minimum distance is formed as When the toothed belt has the maximum tension, the tooth tips at the maximum distance are located at the center of the meshing part with the belt, and when the toothed belt has the minimum tension, the tooth tips are located at the center of the meshing part with the belt, respectively. A timing belt mechanism characterized by being arranged so as to
駆動プーリの歯数をＺとした場合、前記中間歯付きプー
リが、Ｚａ＝ｋ・Ｚ（ｋ＝１，２，３…）なる歯数Ｚａ
を有し、かつｎ＝ｋ・Ｎを満足する個数ｎの前記最大距
離及び最小距離の歯先部を有している特許請求の範囲第
１項記載のタイミングベルト機構。2. When the number of load fluctuations per rotation of the drive pulley is N and the number of teeth of the drive pulley is Z, the intermediate toothed pulley has a number of teeth of Za=k・Z (k=1, 2, 3...) Za
2. The timing belt mechanism according to claim 1, wherein the timing belt mechanism has a number n of tooth tip portions having the maximum distance and the minimum distance satisfying n=k·N.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24841186A JPS63106453A (en) | 1986-10-21 | 1986-10-21 | Timing belt mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24841186A JPS63106453A (en) | 1986-10-21 | 1986-10-21 | Timing belt mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63106453A true JPS63106453A (en) | 1988-05-11 |
Family
ID=17177714
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24841186A Pending JPS63106453A (en) | 1986-10-21 | 1986-10-21 | Timing belt mechanism |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63106453A (en) |
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|---|---|---|---|---|
| WO2003046413A1 (en) * | 2001-11-27 | 2003-06-05 | Litens Automotive | Synchronous drive apparatus with non-circular drive elements |
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| US7125356B2 (en) | 2001-11-06 | 2006-10-24 | Borgwarner Inc. | Tension-reducing random sprocket |
| WO2007003329A1 (en) * | 2005-07-06 | 2007-01-11 | Schaeffler Kg | Flexible drive |
| DE102005031596A1 (en) * | 2005-07-06 | 2007-01-25 | Schaeffler Kg | Belt or chain drive for vehicle, comprises elliptical or polygonal tension pulley moved by off center element |
| EP1756448A1 (en) * | 2004-06-03 | 2007-02-28 | Schaeffler KG | Cost-optimized traction mechanism |
| JP2008039132A (en) * | 2006-08-09 | 2008-02-21 | Tsubakimoto Chain Co | Timing chain drive system |
| US8430775B2 (en) | 2007-09-28 | 2013-04-30 | Borgwarner Inc. | Multiple tension reducing sprockets in a chain and sprocket system |
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-
1986
- 1986-10-21 JP JP24841186A patent/JPS63106453A/en active Pending
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| WO2003046413A1 (en) * | 2001-11-27 | 2003-06-05 | Litens Automotive | Synchronous drive apparatus with non-circular drive elements |
| EP1664596A1 (en) * | 2003-09-18 | 2006-06-07 | Litens Automotive Partnership | Non-circular rotary component |
| US8042507B2 (en) | 2003-09-18 | 2011-10-25 | Litens Automotive Partnership | Non-circular rotary component |
| EP1664596A4 (en) * | 2003-09-18 | 2009-07-15 | Litens Automotive Inc | Non-circular rotary component |
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| WO2005119088A1 (en) * | 2004-06-03 | 2005-12-15 | Schaeffler Kg | Traction mechanism for an internal combustion engine |
| EP1756448A1 (en) * | 2004-06-03 | 2007-02-28 | Schaeffler KG | Cost-optimized traction mechanism |
| WO2005121603A1 (en) * | 2004-06-09 | 2005-12-22 | Schaeffler Kg | Wrap-around drive comprising eccentric toothed wheels |
| DE102004030287A1 (en) * | 2004-06-23 | 2006-01-12 | Ina-Schaeffler Kg | Belt drive for internal combustion engine with drive calming |
| WO2006018095A1 (en) * | 2004-08-12 | 2006-02-23 | Schaeffler Kg | Belt drive |
| DE102005008677B4 (en) * | 2005-02-25 | 2010-07-08 | Audi Ag | Gear for a sleeve or roller chain drive |
| DE102005008677A1 (en) * | 2005-02-25 | 2006-09-07 | Audi Ag | Gear wheel for sleeves or roller chain drive e.g. chain drive of internal combustion engine has axis of rotation and pitch circle and distance between both changes along the peripheral of gear wheel |
| DE102005008676A1 (en) * | 2005-02-25 | 2006-06-22 | Audi Ag | Toothed wheel for tooth chain drive has external teeth with internal spacing between teeth whereby distance between axis of rotation and pitch circle of toothed wheel changes sinusoidally along its circumference |
| DE102005031596A1 (en) * | 2005-07-06 | 2007-01-25 | Schaeffler Kg | Belt or chain drive for vehicle, comprises elliptical or polygonal tension pulley moved by off center element |
| WO2007003329A1 (en) * | 2005-07-06 | 2007-01-11 | Schaeffler Kg | Flexible drive |
| JP2008039132A (en) * | 2006-08-09 | 2008-02-21 | Tsubakimoto Chain Co | Timing chain drive system |
| US8430775B2 (en) | 2007-09-28 | 2013-04-30 | Borgwarner Inc. | Multiple tension reducing sprockets in a chain and sprocket system |
| US10907721B2 (en) | 2015-12-09 | 2021-02-02 | Borgwarner Inc. | Non-prevalent order random sprocket |
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