JP3881722B2 - Belt design support method and design support apparatus - Google Patents

Description

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この式をマトリックス形式で書くと、
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［図６に示すモデルの運動方程式］
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この式をマトリックス形式で書くと、
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［図７に示すモデルの運動方程式］
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この式をマトリックス形式で書くと、
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［図８に示すモデルの運動方程式］
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この式をマトリックス形式で書くと、
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［図９に示すモデルの運動方程式］
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【００８１】
この式をマトリックス形式で書くと、
【数１１】

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［図１０に示すモデルの運動方程式］
【数１２】

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この式をマトリックス形式で書くと、
【数１３】

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［図１１に示すモデルの運動方程式］
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この式をマトリックス形式で書くと、
【数１７】

【数１８】

【数１９】

【００９７】
尚、以上に説明した実施形態１の例は、ベルトスパン部分及びカップリング部分をばねとしているが、ばね定数を表現できるものであれば何でもよく、例えばばね要素、トラス要素、梁要素、三角形要素、四角形要素、プリズム要素、れんが型要素等を単独又は複合させて用いた場合にも、同様の作用効果が得られ、本発明に含まれる。
【００９８】
また、上記のようなばね要素、粘性要素、慣性マス等の結合によって作られた振動系のモデルはオイラー法、線形加速度法、ニューマークのβ法、ウィルソンのθ法、フーボルト法、ルンゲクッタ法等の方法により、動的釣合い式を各時間増分で解く動的応答解析を行えばよい。
【００９９】
また、この発明の対象となるベルトは歯付ベルト、Ｖベルト、Ｖリブドベルト、平ベルトを含む伝動ベルトであり、特定の種類のベルトに限定されない。
【０１００】
さらに、一方向にのみトルクを伝達するカップリングについては、一方向クラッチ（シェルタイプ、ローラタイプ、スプラグタイプ、カムクラッチタイプ、ベアクラッチタイプ等）や一方向にのみトルクを伝達できるものであれば、全てに適用できる。
【０１０１】
【実施例】
最後に、図１５に示すように一方向にのみトルクを伝達するカップリングを含んだ２軸の伝動ベルト駆動系について実験を行い、本発明による計算値に対比すべき実験値を求めた。図１５は、実施形態１において図７に示される一方向にのみトルクを伝達するカップリングを含んだ２軸の伝動ベルト駆動系に対し（尚、図７と同じ部分については同じ符号を付して説明する）、各種のセンサが取り付けられている。
【０１０２】
すなわち、原動側プーリ３３は図外のエンジン又は可変速軸に連結されて回転変動が生じるものである。また、従動側プーリ３４にはエンジンに駆動される補機として例えばオルタネータ、空調用コンプレッサ、パワーステアリング用ポンプ、ウォータポンプ等のうち、一方向のみトルクが伝達するカップリング特性が顕著に現れるオルタネータ３６が駆動連結されている。従動側プーリ３４と補機３６（オルタネータ）との連結部には、一方向にのみトルクを伝達するカップリングが取り付けられている。
【０１０３】
これに対し、上記各プーリ３３，３４及び補機３６の軸にはそれぞれスリット円盤７６〜７８が回転一体に取り付けられ、これらスリット円盤７６〜７８に近接して光電スイッチ７９〜８１が配設され、この光電スイッチ７９〜８１の矩形波パルス信号出力は該光電スイッチ７９〜８１からの周波数信号を電圧に変換するＦＶコンバータ８６〜８８にそれぞれ接続されており、プーリ３３，３４と補機３６の軸の回転時、スリット円盤７６〜７８のスリットが光電スイッチ７９〜８１の位置を通過したときに該光電スイッチ７９〜８１でパルス電圧信号を生じさせ、その電圧信号を受けたＦＶコンバータ８６〜８８からスリット円盤７６〜７８のスリットの通過周期に応じたプーリ回転速度に対応する電圧を出力させるようにしている。
【０１０４】
また、上記原動側プーリ３３と従動側プーリ３４との間の第１のベルトスパンＢ１には第１のタッチプーリ８２が、また第２のベルトスパンＢ２には第２のタッチプーリ８３がそれぞれ設けられている。これらのタッチプーリ８２，８３は対応するベルトスパンＢ１，Ｂ２の背面を３〜２０°屈曲するように配置されており、接触するベルトに比例した反力がタッチプーリ８２，８３に作用するようになっている。そして、これらのタッチプーリ８２，８３の取付部にはロードセル８４，８５が取り付けられ、これらのロードセル８４，８５はそれぞれ歪ゲージ用アンプ８９，９０に接続されている。
【０１０５】
そして、上記各ＦＶコンバータ８６〜８８及び各歪ゲージ用アンプ８９，９０の出力信号は、Ａ／Ｄコンバータ９１でアナログ信号からディジタル信号に変換された後にその電圧値が計測コンピュータ９２に取り込まれて計測される。この計測値を出図するために、コンピュータ９２にプリンタ９３が接続されている。尚、実験上の諸元は表１及び表２に示すとおりである。
【０１０６】
【表１】

【０１０７】
【表２】

【０１０８】
図１６は、補機軸であるオルタネータの発電負荷が、無負荷状態で回転負荷のみが生じているときの、原動側プーリ３３、従動側プーリ３４及び補機３６の軸の回転変動について計算結果（図１６（ａ））と実験結果（図１６（ｂ））とを示す。原動側プーリ３３の回転変動は計算又は実験のいずれとも同じで、計算ではこの回転変動を加振力として与えている。このような原動側プーリ３３の回転変動に対し、従動側プーリ３４及び補機３６の軸（オルタネータ軸）も回転変動を示しており、計算結果は実験結果に対し位相及び振幅量を共に近似できていることが判る。
【０１０９】
また、図１７は原動側プーリ３３と従動側プーリ３４との間のベルトスパン部分の張力を示している。これも同様に、計算結果（図１７（ａ））は実験結果（図１７（ｂ））に対し位相及び変動量とも近似できていることが判る。
【０１１０】
これらのデータによれば、従動側のプーリがカップリングのトルクを伝えない歪方向に回転したとき、補機軸は慣性マスにより回転慣性が生じていることから、補機軸は従動側プーリと絶縁されて空転している状態が示されており、計算においても実験値と同等の状態が再現されていることが判る。
【０１１１】
このことにより、ベルトスパン部分の要素には補機の回転慣性を制動・動作させる仕事エネルギーが生じないため、トルクを伝達しない回転方向時には張力変化が少なくなり、一方向にのみトルクを伝達するカップリングを含んだ伝動ベルト駆動系が従来の固定プーリを用いた伝動ベルト駆動系よりもベルトへの刺激が少なく、ベルトの故障や寿命にとって優位であることが、理論的に実証できたことになる。
【０１１２】
従来（特開平７−２２９５３９公報参照）の設計支援装置を用いて同様の計算を行うと、トルクを伝えない絶縁状態が計算されないために、図１８に示すように実験結果と異なる計算結果（図１８（ａ），（ｂ））となる。
【０１１３】
また、本発明装置はオルタネータのように発電により軸負荷が変化するような補機であっても、補機軸の負荷を運動方程式に付加してやることにより、そのときのプーリや補機軸の回転変動やベルトスパン間の張力変動を計算することができる。
【０１１４】
図１９及び図２０は、補機軸であるオルタネータの発電負荷を２０アンペアの負荷としたときの原動側プーリ３３、従動側プーリ３４及び補機３６の軸の回転変動と、原動側プーリ３３及び従動側プーリ３４の間のベルトスパン部分の張力変動とについて計算結果（図１９（ａ），図２０（ａ））と実験結果（図１９（ｂ），図２０（ｂ））とを示す。
【０１１５】
また、図２１及び図２２は、補機軸であるオルタネータの発電負荷を４０アンペアの電流が発電されるように４０アンペアの負荷としたときの原動側プーリ３３、従動側プーリ３４及び補機３６の軸の回転変動と、原動側プーリ３３及び従動側プーリ３４の間のベルトスパン部分の張力変動とについて計算結果（図２１（ａ），図２２（ａ））と実験結果（図２１（ｂ），図２２（ｂ））とを示す。このときもまた、実験値と同等の状態が再現されていることが判る。
【０１２２】
【発明の効果】
以上説明したように、請求項１〜１２の発明では、一方向にのみトルクを伝達するカップリングを含んだ伝動ベルト駆動系のベルト長手方向の振動計算モデルにより振動計算を行う場合に、一方向にのみトルクを伝達するカップリング部分のばね要素又はスライダ要素をトルクが伝達する歪作用時とトルクが伝達しない歪作用時とで変更するようにした。すなわち、請求項１又は７の発明では、カップリングにトルクが伝達しない歪が生じた場合には、ばね定数をカップリングのばね定数よりも低いばね定数に変更することとした。また、請求項３又は９の発明では、カップリングにトルクが伝達しない歪が生じた場合には、該要素を取り除くこととした。さらに、請求項５又は１１の発明では、カップリングにトルクが伝達しない歪が生じたときにはばね定数を零の値に変更することとした。さらにまた、請求項２又は８の発明では、カップリングにトルクが伝達しない歪が生じた場合には、スライダの力をトルクを伝える歪の値よりも低い値に変更することとした。また、請求項４又は１０の発明では、カップリングにトルクが伝達しない歪が生じた場合には、ばねとスライダ要素を取り除くこととした。さらに、請求項６又は１２の発明では、カップリングにトルクが伝達しない歪が生じたときにはスライダの力を零の値に変更することとした。
【０１２３】
したがって、これら発明によると、一方向にのみトルクを伝達するカップリングを含んだ伝動ベルト駆動系が実際の現象に極めて近い状態の計算を行うことができ、ベルトの張力変動や従動側の補機の回転変動、一方向のみにトルクを伝達するカップリングに連結された補機軸の回転変動等を正確に計算できるようになり、振動によるベルト駆動系各部品や一方向にのみトルクを伝達するカップリングの疲労寿命やベルトスリップ等の判断指針に適確に用いることができる。
【図面の簡単な説明】
【図１】２軸の伝動ベルト駆動系の振動モデルを示す概略図である。
【図２】２軸の伝動ベルト駆動系の振動モデルを詳細に示す図である。
【図３】２軸の伝動ベルト駆動系の別の振動モデルを示す図である。
【図４】２軸の伝動ベルト駆動系の別の２番目の振動モデルを示す図である。
【図５】２軸の伝動ベルト駆動系の別の３番目の振動モデルを示す図である。
【図６】本発明の実施形態１において２軸の一方向にのみトルクを伝達するカップリングを含んだ伝動ベルト駆動系を示す図である。
【図７】２軸の一方向にのみトルクを伝達するカップリングを含んだ伝動ベルト駆動系の別の第１の振動モデルを示す図である。
【図８】３軸の一方向にのみトルクを伝達するカップリングを含んだ伝動ベルト駆動系を示す図である。
【図９】３軸の一方向にのみトルクを伝達するカップリングを含んだ伝動ベルト駆動系の別の第１の振動モデルを示す図である。
【図１０】多軸のオートテンショナと一方向にのみトルクを伝達するカップリングを含んだ伝動ベルト駆動系を示す図である。
【図１１】多軸のオートテンショナと一方向にのみトルクを伝達するカップリングを含んだ伝動ベルト駆動系の別の第１の振動モデルを示す図である。
【図１２】一方向にのみトルクを伝達するカップリングを含んだ伝動ベルト駆動系のトラス要素による振動モデルを示す図である。
【図１３】コンピュータでの振動計算処理の前半部を示すフローチャート図である。
【図１４】同振動計算処理の後半部を示すフローチャート図である。
【図１５】実施形態１に係る実験装置の全体概略図である。
【図１６】補機負荷を無負荷にしたときの原動側プーリ、従動側プーリ、補機軸の回転変動を示す特性図である。
【図１７】補機負荷を無負荷にしたときの原動側プーリと従動側プーリとの間のベルトスパン部分の張力変動を示す特性図である。
【図１８】従来の設計支援装置を用いて、振動計算を行ったときの原動側プーリ、従動側プーリ、補機軸の回転変動と原動側プーリと従動側プーリとの間のベルトスパン部分の張力変動を示す特性図である。
【図１９】補機負荷を２０アンペアの負荷としたときの原動側プーリ、従動側プーリ、補機軸の回転変動を示す特性図である。
【図２０】補機負荷を２０アンペアの負荷としたときの原動側プーリと従動側プーリとの間のベルトスパン部分の張力変動を示す特性図である。
【図２１】補機負荷を４０アンペアの負荷としたときの原動側プーリ、従動側プーリ、補機軸の回転変動を示す特性図である。
【図２２】補機負荷を４０アンペアの負荷としたときの原動側プーリと従動側プーリとの間のベルトスパン部分の張力変動を示す特性図である。
【符号の説明】
２８，３３，３９，４９，６０，７０ 原動側プーリ
２９，３４，４０，４１，５０，５１，６１，６２，７１，７２ 従動側プーリ
３０，３５，４２，５２，６５，７５ 補機軸
６３，７３ オートテンショナプーリ
１０１ 判定手段
１０２ カップリング特性変更手段
Ｂ ベルト
Ｂ１，Ｂ２ ベルトスパン部分[0001]
BACKGROUND OF THE INVENTION
  The present invention relates to a coupling that transmits torque in only one direction.GThe present invention belongs to a technical field related to a method and an apparatus for supporting the design of a drive system when rotational fluctuation or torque fluctuation is applied to the included transmission belt drive system.
[0002]
[Prior art]
In general, when designing a drive system that transmits power using a transmission belt, the transmission belt will not have a short life in consideration of load, belt tension, pulley rotation speed, belt speed, pulley diameter, pulley layout, etc. Ingenuity to make is done. Usually, the device includes, for example, change of belt layout, pulley diameter, belt type, change of belt width or number of belts, and the like.
[0003]
In particular, transmission belt systems and camshafts that drive engine auxiliary equipment (such as air conditioner compressors, power steering oil pumps, cooling water pumps, power generator alternators, engine lubrication oil pumps) used in automobiles, etc. In a transmission belt system that uses a driving timing belt, the engine crankshaft is used as the drive source. Therefore, rotational fluctuations occur according to the engine ignition cycle, crankshaft torsional vibrations, and torque fluctuations at each pulley. However, the belt drive system receives vibrations in the belt longitudinal direction due to the rotation fluctuation and torque fluctuation. As a result, the maximum tension of the belt increases, resulting in a shorter service life, premature belt damage due to excessive shear force on the pulley circumference, generation of slip noise due to increased belt slip, or heat generation due to slip and shortening of service life. There are problems such as.
[0004]
In order to deal with these problems, the applicant has previously made it possible to accurately calculate the tension, acceleration, speed, displacement, etc. that are actually applied to the transmission belt drive system, and using these values, A belt design support method and apparatus that can be used for the drive system design of a transmission belt and the design of a unidirectional coupling have been proposed (see Japanese Patent Laid-Open No. 7-229539).
[0005]
[Problems to be solved by the invention]
  By the way, in a transmission belt drive system, by attaching a coupling that transmits torque only in one direction (rotation direction) to an auxiliary machine having a large moment of inertia (such as an alternator for power generation)., TimesIt is possible to reduce an increase in belt tension fluctuation due to an increase in inertia of the auxiliary machine caused by rotation fluctuation and torque fluctuation, thereby greatly extending the life of the transmission belt.
[0006]
However, in the transmission belt drive system, when the switching cycle of the torque of the coupling that transmits torque only in one direction and the natural period due to the spring characteristics in the belt longitudinal direction coming from the belt layout are synchronized, The degree of stimulation that the transmission belt receives depends on the engine condition, such as when the rotational speed of the auxiliary shaft decreases when the coupling is not transmitting torque due to an increase in rotational load due to the alternator power generation included in the power generator alternator. Therefore, it is necessary to predict the performance degradation and effects of the transmission belt drive system including a coupling that transmits torque only in one direction, and to design the drive system of the transmission belt.
[0007]
Moreover, no predictable method has been found in the vibration prediction in the belt longitudinal direction of a transmission belt drive system including a coupling that transmits torque to at least one pulley in only one direction.
[0010]
  The present invention has been made in view of the above circumstances, and its purpose is to provide a coupling that transmits torque only in one direction that actually occurs.GIt is possible to calculate the tension, acceleration, speed, displacement, etc. applied to the included transmission belt drive system with high accuracy, and the drive system design and unidirectional coupling of the transmission belt in accordance with the actual values using the numerical values.OfIt is to make it available for design.
[0011]
[Means for Solving the Problems]
In order to achieve the above object, the invention of claims 1 to 12 considers a spring of a coupling portion that transmits torque only in one direction or a friction law of a coupling portion that transmits torque only in one direction. The contact model was changed during the calculation.
[0012]
That is, when the strain applied to the spring of the coupling part that transmits torque only in one direction is the distortion that transmits torque, the spring constant of the coupling part that transmits torque only in one direction is calculated as the value of the spring element. I do. On the other hand, when the strain applied to the spring of the coupling portion that transmits torque only in one direction is a strain that does not transmit torque, the spring constant of the coupling portion that transmits torque only in one direction is set in one direction. The calculation is performed in a state where the spring element is removed only when a value lower than or equal to the spring constant of the coupling portion that transmits torque, or when distortion that does not transmit torque occurs.
[0013]
On the other hand, if the friction direction applied to the contact model considering the friction law of the coupling part that transmits torque only in one direction is the direction that transmits torque, the frictional force of the coupling part that transmits torque only in one direction Is calculated as the value of the contact element considering the friction law. On the other hand, when the friction direction applied to the contact model considering the friction law of the coupling portion that transmits torque only in one direction is a direction that does not transmit torque, the coupling portion that transmits torque only in one direction The contact model that takes the friction law into consideration is removed only when the frictional force is lower or zero than the frictional force of the coupling part that transmits torque only in one direction, or when distortion that does not transmit torque occurs. Perform the calculation in the state where it has been.
[0014]
Specifically, the inventions of claims 1 to 6 are inventions of methods, and in the invention of claim 1, at least one pulley of the transmission belt drive system includes a coupling that transmits torque only in one direction. In the belt design support method for supporting the belt design by performing vibration calculation using the vibration calculation model in the belt longitudinal direction, the strain applied to the element modeled by using the coupling portion transmitting the torque only in the one direction as a spring is torque. The spring constant is used as the torque capacity characteristic of the coupling when the torque is transmitted, while the spring constant is changed to the idling torque characteristic of the coupling when the torque is not transmitted.
[0015]
With this configuration, when a distortion that transmits torque occurs in the torsion spring element of the coupling portion that transmits torque only in one direction, the torsion torque is retained, but distortion that does not transmit torque occurs. In this case, since the spring constant is changed to a spring constant having an idling torque characteristic lower than that of the coupling portion that transmits torque only in one direction, the idling torque is transmitted in the calculation by the vibration calculation model. The calculation of a state very close to the actual phenomenon can be performed.
[0016]
In the invention of claim 2, as described above, the direction of friction applied to the element modeled as a contact model in which the torque is transmitted in only one direction as a contact model considering the friction law is the direction in which torque is transmitted. In some cases, the friction force is used as a torque capacity characteristic of the coupling, and when the friction direction in which torque is not transmitted is reached, the friction force is changed to the idling torque characteristic of the coupling.
[0017]
According to this configuration, when friction occurs that transmits torque to the contact element considering the friction law of the coupling part that transmits torque only in one direction, the frictional force is maintained, but torque is transmitted. If friction occurs, the frictional force is changed to a frictional force with an idling torque characteristic that is lower than the frictional force of the coupling part that transmits torque in only one direction. It is possible to perform calculation in a state very close to the actual phenomenon.
[0018]
In the third aspect of the invention, as in the first aspect of the invention, when the strain applied to the element modeled by using a coupling portion that transmits torque only in one direction as a spring becomes a strain that transmits torque, While the constant is used as the torque capacity characteristic of the coupling, when the distortion does not transmit the torque, the above element is changed.
[0019]
In this configuration, when a strain that transmits torque occurs in the spring element of the coupling portion that transmits torque only in one direction, the element is removed. Therefore, the torsional torque on the side where no torque is transmitted is not held, and a calculation close to an actual phenomenon can be performed.
[0020]
In the invention of claim 4, as in the invention of claim 2, the friction direction applied to the element modeled as a contact model in which the torque is transmitted in only one direction as a contact model is considered to be the direction in which torque is transmitted. In this case, the frictional force is set to the torque capacity characteristic of the coupling, and when the frictional direction in which torque is not transmitted is reached, the above elements are removed.
[0021]
In the present invention, when friction that transmits torque occurs in the contact element considering the friction law of the coupling portion that transmits torque only in one direction, the element is removed, so friction on the side that does not transmit torque at all. The force is not held, and a calculation close to the actual phenomenon can be performed.
[0022]
In the fifth aspect of the invention, as in the case of the first aspect of the invention, when the strain applied to the element modeled by using a coupling portion that transmits torque only in one direction as a spring becomes a strain that transmits torque, the spring constant Is a torque capacity characteristic of the coupling, and when the torque does not transmit, the spring constant is changed to zero.
[0023]
As a result, when a distortion that transmits torque occurs in the spring element of the coupling portion that transmits torque only in one direction, the spring constant is changed to a value of zero. The torsional torque on the side where no torque is transmitted is not held, and a calculation close to an actual phenomenon can be performed.
[0024]
In the sixth aspect of the invention, as in the second aspect of the invention, the friction direction applied to the element modeled as a contact model in which the torque is transmitted in only one direction as a contact model in consideration of the friction law is the direction in which the torque is transmitted. The frictional force is set to the torque capacity characteristic of the coupling at the time of, while the frictional force is changed to a zero value when the frictional direction in which torque is not transmitted is reached.
[0025]
As a result, the frictional force is changed to a zero value when the friction that transmits torque occurs in the contact element in consideration of the friction law of the coupling portion that transmits torque only in one direction. Therefore, as in the fourth aspect of the invention, the frictional force on the side that does not transmit torque is not held at all, and a calculation close to an actual phenomenon can be performed.
[0026]
The invention of the seventh to twelfth aspects is an invention of the device. In the seventh aspect of the invention, the vibration in the longitudinal direction of the belt including a coupling that transmits torque in only one direction to at least one pulley of the transmission belt drive system. The premise is a belt design support device that supports vibration design by performing vibration calculation using a calculation model.
[0027]
Then, when performing vibration calculation of a transmission belt drive system including a coupling that transmits torque only in one direction by the vibration calculation model, the coupling part that transmits torque only in one direction is modeled as a spring. A determination means for determining applied strain, and when the determination means determines that the strain applied to the element is a distortion that transmits torque, the spring constant is used as a torque capacity characteristic of the coupling, while the distortion that does not transmit torque is determined. And a spring constant changing means for changing the spring constant to the idling torque characteristic of the coupling. Thus, the same effect as that attained by the 1st aspect can be attained.
[0028]
According to the eighth aspect of the present invention, belt design is supported by performing vibration calculation using a vibration calculation model in the belt longitudinal direction including a coupling that transmits torque in only one direction to at least one pulley of the transmission belt drive system. As a premise, when performing vibration calculation of a transmission belt drive system that includes a coupling that transmits torque only in one direction by a vibration calculation model, a coupling portion that transmits torque only in one direction A determination unit that determines a friction direction applied to an element modeled as a contact model in consideration of a friction law, and when the determination unit determines that the friction direction applied to the element is a direction to transmit torque, the friction force is cupped. While the torque capacity characteristics of the ring, when the friction direction does not transmit torque, the friction force is converted to the idling torque of the coupling. And a frictional force changing means for changing the characteristics. Thus, the same effect as that attained by the 2nd aspect can be attained.
[0029]
According to the ninth aspect of the present invention, belt design is supported by performing vibration calculation using a vibration calculation model in the belt longitudinal direction including a coupling that transmits torque in only one direction to at least one pulley of the transmission belt drive system. In the belt design support apparatus, when the vibration calculation of the transmission belt drive system including the coupling that transmits the torque only in one direction is performed by the vibration calculation model, the coupling portion that transmits the torque only in one direction. Determining means for determining the strain applied to the element modeled as a torsion spring, and when the determination means determines that the strain applied to the element is a distortion that transmits torque, the spring constant is determined as the torque capacity characteristic of the coupling. On the other hand, when the distortion becomes such that torque is not transmitted, the spring constant is changed so that the above elements are removed. Characterized by comprising a stage.
[0030]
With this, the spring constant changing means, when performing the vibration calculation of the transmission belt drive system including the coupling that transmits the torque only in one direction by the vibration calculation model, the coupling portion that transmits the torque only in one direction. When the strain applied to the element modeled as a torsion spring becomes a strain that does not transmit torque, unlike the seventh aspect, the modification is made so as to remove the element, so that the same effect as the invention of the third aspect can be obtained.
[0031]
According to the invention of claim 10, the belt design is supported by performing the vibration calculation by the vibration calculation model in the belt longitudinal direction including the coupling for transmitting the torque only in one direction to at least one pulley of the transmission belt drive system. In such a belt design support device, when performing vibration calculation of a transmission belt drive system including a coupling that transmits torque only in one direction by a vibration calculation model, a coupling portion that transmits torque only in one direction is provided. Determining means for determining the friction direction applied to the element modeled as a contact model in consideration of the friction law; and when the determination means determines that the friction direction applied to the element is a direction for transmitting torque, While the torque capacity characteristics of the coupling are used, the above elements are removed when the friction direction does not transmit torque. Configuration to which a frictional force changing means for changing manner.
[0032]
With this, the frictional force changing means, when performing the vibration calculation of the transmission belt drive system including the coupling that transmits the torque only in one direction by the vibration calculation model, the coupling portion that transmits the torque only in one direction. Unlike the invention of claim 8, if the friction direction applied to the element modeled as a contact model considering the friction law becomes a friction direction not transmitting torque, the element is changed so as to remove the element. The same effects as the invention can be obtained.
[0033]
In the invention of claim 11, when the vibration calculation of the transmission belt drive system including the coupling that transmits the torque only in one direction is performed by the vibration calculation model, the coupling portion that transmits the torque only in one direction is the spring. Determining means for determining the strain applied to the element modeled as follows, and when the determination means determines that the distortion applied to the element has become a distortion for transmitting torque, the spring constant is used as the torque capacity characteristic of the coupling, A spring constant changing means is provided for changing the spring constant to a zero value when the torque does not transmit torque. Thus, the same effect as that attained by the 5th aspect can be attained.
[0034]
In the invention of claim 12, when performing vibration calculation of a transmission belt drive system including a coupling that transmits torque only in one direction by the vibration calculation model, a coupling portion that transmits torque only in one direction, A determination unit that determines a friction direction applied to an element modeled as a contact model in consideration of a friction law, and when the determination unit determines that the friction direction applied to the element is a direction to transmit torque, the friction force is cupped. On the other hand, the torque capacity characteristic of the ring is provided, and a frictional force changing means is provided for changing the frictional force to a zero value when the frictional direction in which torque is not transmitted is reached. Thus, the same effect as that attained by the 5th aspect can be attained.
[0037]
DETAILED DESCRIPTION OF THE INVENTION
First, an example of a conventional transmission belt drive system vibration calculation model (see JP-A-7-229539) applied in a belt vibration calculation model including a coupling that transmits torque in only one direction will be described with reference to FIGS. FIG. 5 shows an example of a two-shaft transmission belt drive system according to the conventional transmission belt drive system vibration calculation model. Reference numerals 1, 8, 16, and 23 denote a driving side (drive side) pulley in which rotational fluctuation occurs, , 17 and 24 are driven pulleys having an axis parallel to the driving pulleys 1, 8, 16, and 23, and a transmission belt B is wound between the pulleys.
[0038]
FIG. 2 shows a diagram when the belt span portions B1 and B2 of this transmission belt drive system are modeled by springs. In the power transmission belt drive system, the belt core wire around the pulleys 1 and 2 and the rubber portion located between the pulleys 1 and 2 serve as springs as places to be replaced as springs in the belt B. . FIG. 3 shows a vibration model in the case where a spring is added at a rubber portion between the belt core wire of the belt B wound around the pulleys 8 and 9 and the pulleys 8 and 9.
[0039]
FIG. 4 is a diagram in which a damping element is added to express the internal damping of the vibration model shown in FIG. FIG. 5 is a diagram in which a damping element is added to express the internal damping of the vibration model shown in FIG.
[0040]
In this vibration model, when the strain applied to the belt span portions B1 and B2 is a compressive strain, the spring constant is set to a lower value or zero than the tensile strain, or a compressive strain is generated. Only when the components of the belt spans B1 and B2 are removed, the calculation is performed.
[0041]
That is, the belt span portions B1 and B2 shown in FIGS. 4 and 5 are composed of a combination of a spring element and a damping element. Therefore, in these combined states, the belt span portions B1 and B2 are added. When the strain becomes a tensile strain, the tensile load is maintained, but when the strain becomes a compressive strain, the spring constant becomes a value lower or zero than the value of the tensile strain, or the compressive strain is reduced. Only when this occurs, the calculation is performed with the elements of the belt span portions B1 and B2 removed.
[0042]
(Embodiment 1)
In any calculation method of the vibration calculation model as described above, a coupling that transmits torque only in one direction is included by attaching the above model to a pulley including a coupling that transmits torque only in one direction. A belt drive system is obtained.
[0043]
That is, FIG. 6 shows an example of a transmission belt drive system according to Embodiment 1 of the present invention that includes a coupling that transmits torque only in one direction, and 28 is a drive side (drive side) pulley in which rotational fluctuation occurs. , 29 is a driven pulley having an axis parallel to the driving pulley 28, and 30 is a coupling that transmits torque only in one direction attached to the driven pulley 29. Belt B is wound around. In this example, a damping element is added to express the internal damping of the vibration model, and the coupling 30 that transmits torque only in one direction attached to the driven pulley 29 is modeled by a spring.
[0044]
In this embodiment, in a coupling model that transmits torque only in one direction, when a distortion that does not transmit torque occurs, the spring constant is set to a value that is lower or zero than the value of distortion that transmits torque, Alternatively, the calculation is performed in a state in which the coupling element that transmits the torque only in one direction is removed only when a distortion that does not transmit the torque occurs.
[0045]
FIG. 7 shows another example of a transmission belt drive system including a coupling that transmits torque only in one direction. In FIG. 7, reference numeral 33 denotes a driving side (driving side) pulley in which rotational fluctuation occurs, 34 denotes a driven side pulley having an axis parallel to the driving side pulley 33, and 35 denotes only in one direction attached to the driven side pulley 34. A transmission belt B is wound around the pulleys 33 and 34 in a coupling for transmitting torque. In this example, a damping element is added to express the internal damping of the vibration model, and the coupling 30 that transmits torque in only one direction attached to the driven pulley 34 is modeled by a spring and a slider element. This is an example.
[0046]
In this example, in a coupling model that transmits torque only in one direction, when the distortion does not transmit torque, the slider force is set to a value that is lower or zero than the value of distortion that transmits torque, Alternatively, the calculation is performed in a state where the coupling spring and the slider element that transmit torque only in one direction are removed only when distortion that does not transmit torque occurs.
[0047]
In this way, in any of the examples shown in FIGS. 6 and 7, when a strain that does not transmit torque occurs, a small constant load is transmitted, and calculation of a state close to the phenomenon of actual idling torque characteristics is performed. It can be performed.
[0048]
8 and 9 show an example of a three-axis transmission belt drive system including a coupling that transmits torque only in one direction. In these drawings, reference numerals 39 and 49 denote driving pulleys, reference numerals 40 and 50 denote one driven pulley having an axis parallel to the driving pulleys 39 and 49, and reference numerals 41 and 51 denote driving pulleys 39 and 49, respectively. A transmission belt B is wound around the pulleys 39 to 41, 4 to 51 in the other driven pulley having a parallel axis. A rubber portion between the belt core wire of the span portion of the transmission belt B and the portion of the belt wound around the pulleys 39 to 41 and 49 to 51 and the pulleys 39 to 41 and 49 to 51 is modeled by a spring. This model is a vibration model with a damping element added to express the internal damping of the vibration model. Couplings 42 and 52 that transmit torque only in one direction attached to the driven pulley of the vibration model are connected by springs. Modeling.
[0049]
In FIG. 9, a coupling model that transmits torque only in one direction of FIG. 8 is modeled by a spring and a slider. A plurality of coupling models that transmit torque only in one direction can be used as well as one driven pulley. It can also be used for a driving pulley.
[0050]
In the vibration model shown in FIG. 8, when the coupling model that transmits torque only in one direction has a distortion that does not transmit torque, the spring constant is set to a value that is lower than the distortion value that transmits torque or zero. Alternatively, the calculation is performed in a state where the coupling element that transmits torque only in one direction is removed only when distortion that does not transmit torque occurs.
[0051]
Also, in the vibration model shown in FIG. 9, when the coupling model that transmits torque only in one direction has a distortion that does not transmit torque, the slider force is lower than the distortion value that transmits torque or The calculation is performed with the coupling spring and the slider element that transmit torque only in one direction removed, only when zero or a distortion that does not transmit torque occurs.
[0052]
Therefore, even in the case of this example, when a strain that does not transmit torque occurs, a small constant load is transmitted, and a state close to the phenomenon of actual idling torque characteristics can be calculated.
[0053]
10 and 11 show an example of a four-axis transmission belt drive system including an auto tensioner including a coupling that transmits torque only in one direction. In these drawings, reference numerals 60 and 70 denote driving pulleys that cause rotational fluctuations, reference numerals 61 and 71 denote one driven pulley having an axis parallel to the driving pulleys 60 and 70, and reference numerals 62 and 72 denote the other driven follower. The pulleys 63 and 73 of the auto tensioner urged by the springs 64 and 74 are disposed between the driving pulleys 60 and 70 and the other driven pulleys 62 and 72, and these pulleys 60 to 63 are disposed on the side pulleys. , 70 to 73, the transmission belt B is wound around the auto tensioner pulleys 63 and 73 as a back cover. The rubber part between the belt core wire of the span part of the transmission belt B and the part of the belt wound around the pulleys 60 to 63 and 70 to 73 and the pulleys 60 to 63 and 70 to 73 is modeled by a spring. This model is a vibration model with damping elements added to express the internal damping of the vibration model, and the coupling that transmits torque in only one direction attached to the driven pulley of this vibration model is modeled by a spring. ing. FIG. 11 shows an example in which a coupling model that transmits torque only in one direction of FIG. 10 is modeled by a spring and a slider.
[0054]
Next, FIG. 12 shows an element shape when a transmission belt drive system including a coupling that transmits torque only in one direction shown in FIG. 7 is modeled by a truss element according to the coupling method shown in FIGS. Is shown. In the figure, N1 and N2 indicate nodes at the centers of the pulleys 33 and 34, respectively. N4 to N7 are nodes located where the belt span portions B1, B2 and the pulleys 33, 34 are in contact. Elements E1 and E2 correspond to the belt span portions B1 and B2, and are one-dimensional truss elements. One end of each of the elements E4 to E7 is coupled to the nodes N1 and N2 at the pulley center, and the other end is coupled to the truss element of the belt spans B1 and B2. The elements E4 to E7 are connected to the pulley center nodes. It is constrained to follow rotation about the Z axis. Further, the lengths of the elements E4 to E7 do not change.
[0055]
The element E3 hits a coupling 35 that transmits torque only in one direction, one end of which is coupled to the center node N2 of the pulley 34 to which the coupling 35 is mounted, and the other end is coupled to the node N3 at the center of the accessory shaft. ing. A torsional moment corresponding to an auxiliary load is applied to the central node N2 of the driven pulley 34 and the node where the coupling 35 is not coupled.
[0056]
The inertia mass is connected to the nodes N1 and N2 at the centers of the pulleys 33 and 34 and the node N3 at the center of the accessory shaft.
[0057]
After setting as described above, a predetermined rotational fluctuation is applied to the driving pulley 33 to apply vibration to the vibration system. When the vibration becomes steady, it is determined that the belt drive system is in a vibration state.
[0058]
Next, a belt design support apparatus that supports belt design as described above will be described. This apparatus is constituted by software on a computer, and an example of calculation procedure in this computer will be described with reference to flowcharts shown in FIGS.
[0059]
In this figure, the dynamic response repetition calculation step for the belt span portion is performed by using a conventional belt design support device (see Japanese Patent Laid-Open No. 7-229539), and the torque in only one direction of the present invention during the internal determination calculation. Enter the formula for determining the coupling that transmits
[0060]
That is, data is input in the first step S1, and an equation of motion of the transmission belt drive system is created for calculation in the next step S2. Then, it calculates | requires by calculating repeatedly the dynamic response when making it increment by minute time between steps S3-S12.
[0061]
First, in step S3, a state after Δt time from the current state being calculated is calculated. As described above, the vibration system model in step S3 can be performed by a method such as the Euler method, the linear acceleration method, the Newmark β method, the Wilson θ method, the Hoobolt method, and the Runge-Kutta method.
[0062]
The state after Δt time is calculated from the calculation result in step S3, and the strain applied to the belt span spring is examined in step S4 based on the calculation result. This determines whether the belt span strain at time t + Δt has changed from tensile strain to compression strain with respect to the belt span strain at time t. If there is a portion where the belt span strain is changed from the tensile strain to the compressive strain and the determination is YES, the spring constant of the belt span portion is set to zero, changed to a low value, or calculated in step S5. After making the shape with the spring removed from the model, the process proceeds to step S6. When the determination is NO, the process directly proceeds to step S6.
[0063]
In step S6, it is determined whether the coupling distortion is a distortion component that transmits torque or a distortion component that does not transmit torque. When the coupling distortion has changed to a distortion component that does not transmit torque and the determination in step S6 is YES, the coupling spring constant is made zero or changed to a low value in step S7, or Remove the spring from the calculation. When the slider is attached to the vibration model of the coupling, the sliding state is set by the value of the idling torque. After step S7, the process proceeds to step S8 when the determination in step S6 is NO.
[0064]
In step S8, the strain applied to the belt span spring is examined by the change in belt span strain after Δt time with respect to the belt span strain at time t. That is, it is determined whether or not the belt span strain at time t + Δt has changed from compression strain to tensile strain with respect to the belt span strain at time t. There is a part where the belt span strain changes from the compression strain to the tensile strain. If the determination is YES, in step S9, the belt constant is changed to the spring constant at the time of belt span tension, or the spring is removed from that portion. If it is in the shape, a belt span spring is attached, and then the process proceeds to step S10. If the determination is NO, the process proceeds directly to step S10.
[0065]
In step S10, as in step S6, it is determined whether the coupling distortion is a distortion component that transmits torque or a distortion component that does not transmit torque. Here, when the distortion of the coupling changes to a distortion component that transmits torque and the determination in step S10 is YES, the spring constant of the coupling is changed to a spring constant that transmits torque in step S11 or a low value. If the spring is removed from the calculation, install the coupling spring. When the slider is attached to the vibration model of the coupling, the slider is brought into a sliding state with the value of the torque capacity of the coupling, and then the process proceeds to step S12. If the determination in step S10 is no, the process proceeds directly to step S12.
[0066]
The determinations in steps S6 and S10 are made when the coupling spring or the slider is changed between the calculation in the immediately preceding step S3 and the calculation in the previous step S3. If the state is changed to a state of receiving a distortion that transmits torque, it is assumed that the state of receiving a distortion that transmits torque after t time, and if it is changed to a state of receiving a distortion that does not transmit torque. , It is treated as being subjected to distortion that does not transmit torque after t time.
[0067]
In step S12, it is determined in step S5, S7, S8, S10 whether or not the belt span spring or coupling spring or slider has been changed. If YES, the process returns to step S3. Recalculate. In the case where the calculation is simply performed or when the time increment Δt is small, the calculation may be performed according to the flow excluding step S12, and the procedure may proceed directly from step S11 to step S13.
[0068]
If it is determined in step S12 that the belt span spring or coupling spring or slider is not changed, the time t is increased by Δt in step S13, and the calculation result at that time is further determined in step S14. Record.
[0069]
Thereafter, in step S15, it is determined whether or not the calculation has been completed up to the specified time range. If NO is not the end time, the process returns to step S3, and YES is the end time. In step S16, the result is output and the calculation is terminated.
[0070]
In the embodiment of the present invention, in steps S6 and S10, the strain applied to the element modeled as a spring or a spring and a slider is determined for the vibration calculation model in the longitudinal direction of the transmission belt drive system belt. A determination unit 101 is configured.
[0071]
Further, when it is determined in steps S7 and S11 that the strain applied to the element by the determination means 101 is a strain that transmits torque, the spring constant is used as the spring characteristic of the coupling portion, or when the slider is attached. If the slider is made to be in a sliding state characteristic with the value of the torque capacity of the coupling, but if it is determined that the distortion does not transmit torque, the spring constant should be changed to a spring constant lower than the spring constant of the coupling part. The changing means 102 is configured such that it is set to zero, or the element is removed, and when the slider is attached, the slider 102 is made to be in a sliding state with the value of the idling torque.
[0072]
Here, other equations of motion in the above examples will be exemplified.
[Equation of motion of model shown in FIG. 5]
[Expression 1]

[0073]
If this formula is written in matrix form,
[Expression 2]

[Equation 3]

[0074]
[Equation of motion of model shown in FIG. 6]
[Expression 4]

[0075]
If this formula is written in matrix form,
[Equation 5]

[0076]
[Equation of motion of model shown in FIG. 7]
[Formula 6]

[0077]
If this formula is written in matrix form,
[Expression 7]

[0078]
[Equation of motion of model shown in FIG. 8]
[Equation 8]

[0079]
If this formula is written in matrix form,
[Equation 9]

[0080]
[Equation of motion of model shown in FIG. 9]
[Expression 10]

[0081]
If this formula is written in matrix form,
## EQU11 ##

[0082]
[Equation of motion of model shown in FIG. 10]
[Expression 12]

[0083]
If this formula is written in matrix form,
[Formula 13]

[Expression 14]

[Expression 15]

[0084]
[Equation of motion of model shown in FIG. 11]
[Expression 16]

[0085]
If this formula is written in matrix form,
[Expression 17]

[Expression 18]

[Equation 19]

[0097]
  The embodiment described aboveExample 1The belt span portion and the coupling portion are springs, but any material can be used as long as it can express the spring constant, such as spring elements, truss elements, beam elements, triangular elements, square elements, prism elements, brick type elements, etc. When these are used alone or in combination, the same effects are obtained and included in the present invention.
[0098]
In addition, the vibration system model created by coupling spring elements, viscous elements, inertia mass, etc. as described above is Euler's method, linear acceleration method, Newmark's β method, Wilson's θ method, Hoobolt method, Runge-Kutta method, etc. In this way, a dynamic response analysis for solving the dynamic balance equation at each time increment may be performed.
[0099]
The belts to which the present invention is applied are transmission belts including toothed belts, V-belts, V-ribbed belts and flat belts, and are not limited to specific types of belts.
[0100]
  Furthermore, for couplings that transmit torque only in one direction, one-way clutches (shell type, roller type, sprag type, cam clutch type, bear clutch type, etc.) or any type that can transmit torque only in one direction Applicable to all.
[0101]
【Example】
  Finally,FIG.As shown in Fig. 2, an experiment was conducted on a two-axis transmission belt drive system including a coupling that transmits torque only in one direction, and an experimental value to be compared with the calculated value according to the present invention was obtained.FIG.Is a biaxial transmission belt drive system including a coupling that transmits torque only in one direction shown in FIG. 7 in the first embodiment (the same parts as those in FIG. Various sensors are attached.
[0102]
That is, the driving pulley 33 is connected to an unillustrated engine or a variable speed shaft to cause rotational fluctuation. In the driven pulley 34, for example, an alternator 36 that exhibits a coupling characteristic in which torque is transmitted in only one direction among an alternator, an air conditioning compressor, a power steering pump, a water pump, and the like as auxiliary machines driven by the engine. Are drive-coupled. A coupling for transmitting torque only in one direction is attached to a connecting portion between the driven pulley 34 and the auxiliary machine 36 (alternator).
[0103]
On the other hand, slit disks 76 to 78 are integrally attached to the shafts of the pulleys 33 and 34 and the auxiliary machine 36, respectively, and photoelectric switches 79 to 81 are disposed in the vicinity of the slit disks 76 to 78. The rectangular wave pulse signal outputs of the photoelectric switches 79 to 81 are connected to FV converters 86 to 88 for converting the frequency signals from the photoelectric switches 79 to 81 into voltages, respectively. When the shaft rotates, when the slits of the slit disks 76 to 78 pass through the positions of the photoelectric switches 79 to 81, the photoelectric switches 79 to 81 generate pulse voltage signals, and the FV converters 86 to 88 that receive the voltage signals. The voltage corresponding to the pulley rotational speed corresponding to the passage period of the slits of the slit disks 76 to 78 is output.
[0104]
Further, a first touch pulley 82 is provided in the first belt span B1 between the driving pulley 33 and the driven pulley 34, and a second touch pulley 83 is provided in the second belt span B2. Yes. These touch pulleys 82 and 83 are arranged so that the back surfaces of the corresponding belt spans B1 and B2 are bent by 3 to 20 °, and a reaction force proportional to the belt in contact acts on the touch pulleys 82 and 83. Yes. Load cells 84 and 85 are attached to the attachment portions of these touch pulleys 82 and 83, and these load cells 84 and 85 are connected to strain gauge amplifiers 89 and 90, respectively.
[0105]
The output signals of the FV converters 86 to 88 and the strain gauge amplifiers 89 and 90 are converted from analog signals to digital signals by the A / D converter 91, and then the voltage values are taken into the measurement computer 92. It is measured. In order to output this measured value, a printer 93 is connected to the computer 92. The experimental specifications are as shown in Tables 1 and 2.
[0106]
[Table 1]

[0107]
[Table 2]

[0108]
  FIG.Is a calculation result of the rotational fluctuations of the shafts of the driving pulley 33, the driven pulley 34, and the auxiliary device 36 when the power generation load of the alternator, which is the auxiliary machine shaft, is not loaded and only the rotational load is generated (FIG.(A)) and experimental results (FIG.(B)). The rotation fluctuation of the driving pulley 33 is the same as that in either calculation or experiment. In the calculation, this rotation fluctuation is given as an excitation force. The driven pulley 34 and the axis of the auxiliary machine 36 (alternator shaft) also show rotational fluctuation with respect to the rotational fluctuation of the driving pulley 33, and the calculation result can approximate both the phase and the amplitude with respect to the experimental result. You can see that
[0109]
  Also,FIG.Indicates the tension of the belt span portion between the driving pulley 33 and the driven pulley 34. Similarly, the calculation result (FIG.(A)) shows the experimental results (FIG.It can be seen that (b)) can be approximated both in phase and fluctuation.
[0110]
According to these data, when the driven pulley rotates in the direction of distortion that does not transmit the coupling torque, the auxiliary shaft is insulated from the driven pulley because the rotary inertia is generated by the inertia mass. It can be seen that in the calculation, a state equivalent to the experimental value is reproduced.
[0111]
As a result, work energy that brakes and operates the rotational inertia of the accessory is not generated in the elements of the belt span part, so that the change in tension is reduced in the rotational direction when torque is not transmitted, and the cup transmits torque only in one direction. It has been proved theoretically that the transmission belt drive system including the ring has less irritation to the belt than the conventional transmission belt drive system using a fixed pulley, and is superior to the failure and life of the belt. .
[0112]
  If the same calculation is performed using a conventional design support apparatus (see Japanese Patent Application Laid-Open No. 7-229539), an insulation state that does not transmit torque is not calculated.FIG.As shown in Fig.FIG.(A), (b)).
[0113]
Moreover, even if the device of the present invention is an auxiliary machine such as an alternator whose shaft load changes due to power generation, by adding the load of the auxiliary machine shaft to the equation of motion, the rotational fluctuation of the pulley or auxiliary machine shaft at that time The tension variation between belt spans can be calculated.
[0114]
  FIG.as well asFIG.Is the rotation fluctuation of the shafts of the driving pulley 33, the driven pulley 34, and the auxiliary device 36 when the power generation load of the alternator, which is the auxiliary shaft, is 20 amperes, and between the driving pulley 33 and the driven pulley 34. Calculation results of tension fluctuation in belt span part ofFIG.(A),FIG.(A)) and experimental results (FIG.(B),FIG.(B)).
[0115]
  Also,FIG.as well asFIG.Is the rotational fluctuation of the shafts of the driving pulley 33, the driven pulley 34, and the auxiliary machine 36 when the power generation load of the alternator, which is an auxiliary machine shaft, is 40 amps so that a 40 amp current is generated, The calculation result of the tension fluctuation in the belt span portion between the side pulley 33 and the driven pulley 34 (FIG.(A),FIG.(A)) and experimental results (FIG.(B),FIG.(B)). Also at this time, it can be seen that a state equivalent to the experimental value is reproduced.
[0122]
【The invention's effect】
As described above, in the inventions of claims 1 to 12, when the vibration calculation is performed by the vibration calculation model in the belt longitudinal direction of the transmission belt drive system including the coupling that transmits the torque only in one direction, The spring element or the slider element of the coupling part that transmits torque only to the sway is changed between when the distortion acts when torque is transmitted and when the distortion acts when torque is not transmitted. That is, in the invention of claim 1 or 7, when a distortion that does not transmit torque occurs in the coupling, the spring constant is changed to a spring constant lower than the spring constant of the coupling. Further, in the invention of claim 3 or 9, when a distortion in which torque is not transmitted to the coupling occurs, the element is removed. Furthermore, in the invention according to claim 5 or 11, when a distortion that does not transmit torque occurs in the coupling, the spring constant is changed to a zero value. Furthermore, in the invention of claim 2 or 8, when a distortion that does not transmit torque occurs in the coupling, the force of the slider is changed to a value lower than the value of the distortion that transmits the torque. Further, in the invention of claim 4 or 10, the spring and the slider element are removed in the case where a distortion that does not transmit torque occurs in the coupling. Furthermore, in the invention of claim 6 or 12, the slider force is changed to a zero value when a distortion that does not transmit torque occurs in the coupling.
[0123]
Therefore, according to these inventions, it is possible to calculate a state in which the transmission belt drive system including the coupling that transmits the torque only in one direction is very close to the actual phenomenon, and the belt tension fluctuation or the auxiliary machine on the driven side Rotational fluctuations, rotational fluctuations of auxiliary shafts connected to couplings that transmit torque in only one direction, etc. can be accurately calculated, and each belt drive system component due to vibration or a cup that transmits torque only in one direction It can be used appropriately as a guideline for judging ring fatigue life and belt slip.
[Brief description of the drawings]
FIG. 1 is a schematic diagram showing a vibration model of a biaxial transmission belt drive system.
FIG. 2 is a diagram showing in detail a vibration model of a biaxial transmission belt drive system.
FIG. 3 is a diagram showing another vibration model of a biaxial transmission belt drive system.
FIG. 4 is a diagram showing another second vibration model of the two-axis transmission belt drive system.
FIG. 5 is a diagram showing another third vibration model of the two-axis transmission belt drive system.
6 is a diagram showing a transmission belt drive system including a coupling that transmits torque only in one direction of two axes in the first embodiment of the present invention. FIG.
FIG. 7 is a diagram showing another first vibration model of the transmission belt drive system including a coupling that transmits torque only in one direction of two axes.
FIG. 8 is a diagram showing a transmission belt drive system including a coupling that transmits torque in only one direction of three axes.
FIG. 9 is a diagram showing another first vibration model of a transmission belt drive system including a coupling that transmits torque only in one direction of three axes.
FIG. 10 is a diagram showing a transmission belt drive system including a multi-axis auto tensioner and a coupling for transmitting torque only in one direction.
FIG. 11 is a diagram showing another first vibration model of a transmission belt drive system including a multi-axis auto tensioner and a coupling that transmits torque only in one direction.
FIG. 12 is a diagram showing a vibration model by a truss element of a transmission belt drive system including a coupling that transmits torque only in one direction.
FIG. 13 is a flowchart showing the first half of vibration calculation processing in a computer.
FIG. 14 is a flowchart showing the second half of the vibration calculation processing;.
15 is an overall schematic diagram of an experimental apparatus according to Embodiment 1. FIG.
FIG. 16 is a characteristic diagram showing rotational fluctuations of the driving pulley, the driven pulley, and the auxiliary shaft when the auxiliary load is unloaded.
FIG. 17 is a characteristic diagram showing a tension variation in a belt span portion between the driving pulley and the driven pulley when the auxiliary machine load is unloaded.
FIG. 18 shows rotational fluctuations of the driving pulley, driven pulley, auxiliary shaft, and tension of the belt span portion between the driving pulley and the driven pulley when vibration calculation is performed using a conventional design support apparatus. It is a characteristic view which shows a fluctuation | variation.
FIG. 19: Auxiliary load of 20 ampsWhenIt is a characteristic view which shows the rotation fluctuation | variation of the driving | running | working side pulley at the time of having carried out, a driven pulley, and an auxiliary machine shaft.
[Fig. 20] Auxiliary machinery load of 20 ampsWhenIt is a characteristic view which shows the tension | tensile_strength fluctuation | variation of the belt span part between a driving | running | working side pulley and a driven side pulley at the time of doing.
FIG. 21: Auxiliary load of 40 ampsWhenIt is a characteristic view which shows the rotation fluctuation | variation of the driving | running | working side pulley at the time of having carried out, a driven pulley, and an auxiliary machine shaft.
[Fig. 22] Auxiliary load of 40 ampsWhenIt is a characteristic view which shows the tension | tensile_strength fluctuation | variation of the belt span part between a driving | running | working side pulley and a driven side pulley at the time of carrying out.
[Explanation of symbols]
  28, 33, 39, 49, 60, 70 Driving side pulley
  29, 34, 40, 41, 50, 51, 61, 62, 71, 72 driven pulley
  30, 35, 42, 52, 65, 75 Auxiliary machine shaft
  63,73 Auto tensioner pulley
  101 judging means
  102 Coupling characteristic changing means
  B belt
  B1, B2 Belt span part

Claims (12)

In a belt design support method for supporting belt design by performing vibration calculation by a vibration calculation model in a belt longitudinal direction including a coupling that transmits torque in only one direction to at least one pulley of a transmission belt drive system.
When the strain applied to the element modeling the coupling part that transmits torque only in one direction as a spring becomes the strain that transmits torque, the spring constant is used as the torque capacity characteristic of the coupling, but no torque is transmitted. A belt design support method characterized by changing a spring constant to a free-running torque characteristic of a coupling when distortion occurs. In a belt design support method for supporting belt design by performing vibration calculation by a vibration calculation model in a belt longitudinal direction including a coupling that transmits torque in only one direction to at least one pulley of a transmission belt drive system.
When the coupling direction that transmits torque in only one direction is modeled as a contact model that takes into account the friction law, the frictional force applied to the element is the direction that transmits torque. On the other hand, the belt design support method is characterized in that the friction force is changed to the idling torque characteristic of the coupling when the friction direction in which torque is not transmitted is reached. In a belt design support method for supporting belt design by performing vibration calculation by a vibration calculation model in a belt longitudinal direction including a coupling that transmits torque in only one direction to at least one pulley of a transmission belt drive system.
When the strain applied to the element modeling the coupling part that transmits torque only in one direction as a spring becomes the strain that transmits torque, the spring constant is used as the torque capacity characteristic of the coupling, but no torque is transmitted. A belt design support method, wherein the element is changed so as to remove the element when distortion occurs. In a belt design support method for supporting belt design by performing vibration calculation by a vibration calculation model in a belt longitudinal direction including a coupling that transmits torque in only one direction to at least one pulley of a transmission belt drive system.
When the frictional direction applied to the element that models the coupling part that transmits torque in only one direction as a contact model that considers the friction law is the direction that transmits torque, the frictional force is the torque capacity characteristic of the coupling. On the other hand, the belt design support method is characterized in that when the friction direction in which torque is not transmitted is reached, the above elements are removed. In a belt design support method for supporting belt design by performing vibration calculation by a vibration calculation model in a belt longitudinal direction including a coupling that transmits torque in only one direction to at least one pulley of a transmission belt drive system.
When the strain applied to the element modeling the coupling part that transmits torque only in one direction as a spring becomes the strain that transmits torque, the spring constant is used as the torque capacity characteristic of the coupling, but no torque is transmitted. A belt design support method, characterized by changing a spring constant to a zero value when strain occurs. In a belt design support method for supporting belt design by performing vibration calculation by a vibration calculation model in a belt longitudinal direction including a coupling that transmits torque in only one direction to at least one pulley of a transmission belt drive system.
When the coupling direction that transmits torque in only one direction is modeled as a contact model that takes into account the friction law, the frictional force applied to the element is the direction that transmits torque. On the other hand, when the friction direction in which torque is not transmitted is reached, the frictional force is changed to a zero value. Belt design support that supports belt design by performing vibration calculation with a belt longitudinal vibration calculation model that includes a coupling that transmits torque in only one direction to at least one pulley of the transmission belt drive system In the device
When calculating the vibration of a transmission belt drive system that includes a coupling that transmits torque in only one direction using the above vibration calculation model, the coupling part that transmits torque in only one direction is added to the modeled element as a spring. Determining means for determining distortion;
When the determination means determines that the strain applied to the element is a strain that transmits torque, the spring constant is used as the torque capacity characteristic of the coupling, while when the strain does not transmit torque, the spring constant is coupled. A belt design support device comprising spring constant changing means for changing to the idling torque characteristics of the belt. Belt design support that supports belt design by performing vibration calculation with a belt longitudinal vibration calculation model that includes a coupling that transmits torque in only one direction to at least one pulley of the transmission belt drive system In the device
A contact model that takes the friction law into account for the coupling part that transmits torque only in one direction when performing vibration calculation of a transmission belt drive system that includes a coupling that transmits torque only in one direction by the above vibration calculation model Determining means for determining the direction of friction applied to the element modeled as:
When it is determined by the determination means that the direction of friction applied to the element is the direction in which torque is transmitted, the frictional force is used as the torque capacity characteristic of the coupling. A belt design support device comprising: friction force changing means for changing to an idling torque characteristic of a coupling. Belt design support that supports belt design by performing vibration calculation with a belt longitudinal vibration calculation model that includes a coupling that transmits torque in only one direction to at least one pulley of the transmission belt drive system In the device
When calculating the vibration of a transmission belt drive system that includes a coupling that transmits torque only in one direction using the above vibration calculation model, the coupling part that transmits torque only in one direction is modeled as a torsion spring. A determination means for determining applied strain;
When the determination means determines that the strain applied to the element is a distortion that transmits torque, the spring constant is used as the torque capacity characteristic of the coupling. And a spring constant changing means for changing so as to remove the belt. Belt design support that supports belt design by performing vibration calculation with a belt longitudinal vibration calculation model that includes a coupling that transmits torque in only one direction to at least one pulley of the transmission belt drive system In the device
A contact model that takes the friction law into account for the coupling part that transmits torque only in one direction when performing vibration calculation of a transmission belt drive system that includes a coupling that transmits torque only in one direction by the above vibration calculation model Determining means for determining the direction of friction applied to the element modeled as:
When it is determined by the determination means that the friction direction applied to the element is a direction in which torque is transmitted, the frictional force is set as the torque capacity characteristic of the coupling. A belt design support device, comprising: a frictional force changing means for changing so as to be removed. Belt design support that supports belt design by performing vibration calculation with a belt longitudinal vibration calculation model that includes a coupling that transmits torque in only one direction to at least one pulley of the transmission belt drive system In the device
When calculating the vibration of a transmission belt drive system that includes a coupling that transmits torque in only one direction using the above vibration calculation model, the coupling part that transmits torque in only one direction is added to the modeled element as a spring. Determining means for determining distortion;
When the determination means determines that the strain applied to the element is a distortion that transmits torque, the spring constant is set as the torque capacity characteristic of the coupling. On the other hand, when the distortion does not transmit torque, the spring constant is set to zero. A belt design support device comprising spring constant changing means for changing to a value. Belt design support that supports belt design by performing vibration calculation with a belt longitudinal vibration calculation model that includes a coupling that transmits torque in only one direction to at least one pulley of the transmission belt drive system In the device
A contact model that takes the friction law into account for the coupling part that transmits torque only in one direction when performing vibration calculation of a transmission belt drive system that includes a coupling that transmits torque only in one direction by the above vibration calculation model Determining means for determining the direction of friction applied to the element modeled as:
When it is determined by the determination means that the direction of friction applied to the element is the direction in which torque is transmitted, the frictional force is used as the torque capacity characteristic of the coupling. A belt design support device comprising: friction force changing means for changing to a zero value.

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