JP2003337092A - Method for determining spring constant of dynamic torsion - Google Patents
Method for determining spring constant of dynamic torsionInfo
- Publication number
- JP2003337092A JP2003337092A JP2002145636A JP2002145636A JP2003337092A JP 2003337092 A JP2003337092 A JP 2003337092A JP 2002145636 A JP2002145636 A JP 2002145636A JP 2002145636 A JP2002145636 A JP 2002145636A JP 2003337092 A JP2003337092 A JP 2003337092A
- Authority
- JP
- Japan
- Prior art keywords
- spring constant
- resonance frequency
- torsion
- bode diagram
- dynamic
- 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
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、共振周波数を算出
するために用いる動的捩りのばね定数の割り出し方法に
関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method of determining a spring constant of dynamic torsion used for calculating a resonance frequency.
【0002】[0002]
【従来の技術】エンジンの試験を行なう場合には、図3
のようにダイナモメータ4の回転軸4aにカップリング
3,トルクメータ2を介してエンジン8の出力軸が連結
される。エンジン8においては回転中にトルクが変化
し、クランク軸の捩り振動を誘発する。この捩り振動の
周期がクランク軸の固有の共振振動数としてのエンジン
脈動に一致すると、共振状態となって振動が激しくなり
機器の破損につながる。このため、軸系に固有の共振振
動数を知って、この振動数付近での運転を極力避けるよ
うにしなければならない。しかし、エンジンの試験を目
的とした装置では、共振状態が生じるのを避けることが
できない。2. Description of the Related Art FIG.
As described above, the output shaft of the engine 8 is connected to the rotary shaft 4a of the dynamometer 4 through the coupling 3 and the torque meter 2. In the engine 8, the torque changes during rotation, which induces torsional vibration of the crankshaft. When the cycle of this torsional vibration matches the engine pulsation as the resonance frequency peculiar to the crankshaft, it becomes a resonance state and vibrates violently, resulting in damage to the equipment. For this reason, it is necessary to know the resonance frequency peculiar to the shaft system and avoid operation near this frequency as much as possible. However, in a device for the purpose of testing an engine, a resonance state cannot be avoided.
【0003】共振周波数付近の大きな捩り振動を抑制す
るための対策はいろいろと考案されているが、共振周波
数を予め知っていることが必要であり、カップリング3
の一端にはエンジン8が、他端にはダイナモメータ4が
連結された2質点系では下記の式より求められる。共振
周波数をfとすると、
f=(1/2π)√(K(JE+JD)/JE・JD)・・・(1)
となる。ここで、Kはカップリングの捩りのばね定数、
JEはエンジン慣性、JDはダイナモメータ慣性である。Although various measures have been devised for suppressing large torsional vibrations near the resonance frequency, it is necessary to know the resonance frequency in advance, and the coupling 3
In the two-mass system in which the engine 8 is connected to one end and the dynamometer 4 is connected to the other end, it is calculated by the following formula. If the resonance frequency is f, then f = (1 / 2π) √ (K (J E + J D ) / J E · J D ) ... (1) Where K is the torsional spring constant of the coupling,
J E is the engine inertia and J D is the dynamometer inertia.
【0004】式(1)から共振周波数fを求めるには、
カップリングの捩りのばね定数「K」を先に求めなけれ
ばならない。捩りのばね定数「K」を求めるには、従来
は図2のような装置を用いている。一端が壁面1に固定
されたカップリング3の他端にアーム6を介して荷重W
を加えることによりカップリング3に静的なトルクTを
かけ、トルクTに対するカップリング3の捩り角度θを
測定し、Tとθとの関係からカップリング3を捩る場合
の捩りのばね定数「K」を求めていた。To obtain the resonance frequency f from the equation (1),
The torsional spring constant "K" of the coupling must first be determined. Conventionally, a device as shown in FIG. 2 is used to obtain the torsion spring constant “K”. The load W is applied to the other end of the coupling 3 whose one end is fixed to the wall surface 1 via the arm 6.
Is applied to the coupling 3 to apply a static torque T, the torsion angle θ of the coupling 3 with respect to the torque T is measured, and the torsion spring constant “K” when the coupling 3 is twisted from the relationship between T and θ Was being asked.
【0005】[0005]
【発明が解決しようとする課題】ところが、静的なトル
クTを加えて捩り角度θを測定することにより捩りのば
ね定数「K」を求めるとダンピングの効果が現れず、求
めた捩りのばね定数「K」を(1)式に代入して共振周
波数fを求めても、回転中の真の共振周波数fとは異な
るものとなってしまう。However, if the spring constant "K" of the torsion is obtained by measuring the torsion angle θ by adding the static torque T, the damping effect does not appear, and the obtained spring constant of the torsion is obtained. Even if "K" is substituted into the equation (1) to obtain the resonance frequency f, it becomes different from the true resonance frequency f during rotation.
【0006】そこで本発明は、斯かる課題を解決した動
的捩りのばね定数の割り出し方法を提供することを目的
とする。Therefore, an object of the present invention is to provide a method for determining the spring constant of dynamic torsion that solves the above problems.
【0007】[0007]
【課題を解決するための手段】斯かる目的を達成するた
めの請求項1に係る動的捩りのばね定数の割り出し方法
の構成は、固定されたトルクメータに一端が連結された
軸の他端を回転させて捩り加振を行なわせ、加振周波数
を変化させて前記トルクメータの出力からボード線図を
求め、当該ボード線図から共振周波数を求め、捩りのば
ね定数と共振周波数との関係式より捩りのばね定数を算
出することを特徴とする。In order to achieve the above object, the method of indexing the spring constant of dynamic torsion according to claim 1 is configured so that the other end of the shaft, one end of which is connected to a fixed torque meter, is connected. Is rotated to perform torsional vibration, the vibration frequency is changed to obtain a Bode diagram from the output of the torque meter, the resonance frequency is obtained from the Bode diagram, and the relationship between the torsion spring constant and the resonance frequency is obtained. It is characterized in that the spring constant of torsion is calculated from the equation.
【0008】斯かる動的捩りのばね定数の割り出し方法
で求めたばね定数を前記関係式に代入すると、共振周波
数を求めることができる。The resonance frequency can be obtained by substituting the spring constant obtained by the method for determining the spring constant of the dynamic torsion into the above relational expression.
【0009】請求項2に係る動的捩りのばね定数の割り
出し方法の構成は、軸を回転させて捩り加振を行なわ
せ、加振周波数を変化させて回転検出器の出力から回転
変動を求め、当該回転変動からボード線図を求め、当該
ボード線図から共振周波数を求め、捩りのばね定数と共
振周波数との関係式より捩りのばね定数を算出すること
を特徴とする。In the structure of the method for determining the spring constant of the dynamic torsion according to the second aspect, the shaft is rotated to perform torsional vibration, and the vibration frequency is changed to obtain the rotation fluctuation from the output of the rotation detector. The Bode diagram is obtained from the rotation fluctuation, the resonance frequency is obtained from the Bode diagram, and the torsion spring constant is calculated from the relational expression between the torsion spring constant and the resonance frequency.
【0010】斯かる動的捩りのばね定数の割り出し方法
で求めたばね定数を前記関係式に代入すると、共振周波
数を求めることができる。By substituting the spring constant obtained by such a method for determining the spring constant of dynamic torsion into the above relational expression, the resonance frequency can be obtained.
【0011】[0011]
【発明の実施の形態】以下、本発明による動的捩りのば
ね定数の割り出し方法の実施の形態を説明する。BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of a method for determining a spring constant of dynamic torsion according to the present invention will be described below.
【0012】(a)実施の形態1
まず、実施の形態1を説明する。図1のように壁面1に
固定したトルクメータ2にカップリング(軸)3を介し
てダイナモメータ4の回転軸4aが連結されている。ダ
イナモメータ4の回転軸4aを回転させ、一定の振幅で
捩り加振を行なう。その加振周波数を変化させ、トルク
メータ2の出力よりボード線図を求め、当該ボード線図
から共振周波数fHを求める。一方、共振周波数fHと動
的捩りのばね定数Kとは以下の関係が成り立つ。(A) First Embodiment First, the first embodiment will be described. A rotary shaft 4a of a dynamometer 4 is connected to a torque meter 2 fixed to a wall surface 1 via a coupling (shaft) 3 as shown in FIG. The rotating shaft 4a of the dynamometer 4 is rotated to perform torsional vibration with a constant amplitude. The excitation frequency is changed, the Bode diagram is obtained from the output of the torque meter 2, and the resonance frequency f H is obtained from the Bode diagram. On the other hand, the following relationship holds between the resonance frequency f H and the spring constant K of the dynamic torsion.
【0013】
fH=(1/2π)√(K/JD)・・・(2)
(2)式からKを求めると、
K=JD(2πfH)2・・・(3)
となり、前記の共振周波数fHとダイナモメータ慣性JD
とを(3)式に代入することにより動的捩りのばね定数
Kを求めることができる。[0013] f H = (1 / 2π) √ (K / J D) ··· (2) (2) When obtaining the K from the equation, K = J D (2πf H ) 2 ··· (3) becomes , The resonance frequency f H and the dynamometer inertia J D
By substituting and into the equation (3), the spring constant K of the dynamic torsion can be obtained.
【0014】このようにして求めた動的捩りのばね定数
Kを前記の(1)式に代入することで共振周波数fを求
めることができる。ここで求めた共振周波数fは動的な
要素が含まれるため、実態に近い値となる。The resonance frequency f can be obtained by substituting the spring constant K of the dynamic torsion thus obtained into the above equation (1). Since the resonance frequency f obtained here includes a dynamic element, it has a value close to the actual state.
【0015】(b)実施の形態2 次に、実施の形態2について説明する。(B) Second embodiment Next, the second embodiment will be described.
【0016】実施の形態1ではトルクメータの出力を検
出してボード線図を求め、ボード線図から共振周波数f
Hを求め、共振周波数fHを式(3)に代入することで動
的捩りのばね定数Kを求めたが、トルクメータに代えて
図1のダイナモメータの回転検出器5から回転変動を求
め、回転変動からボード線図を求め、ボード線図から実
施の形態1と同様にして動的捩りのばね定数Kを求める
こともできる。In the first embodiment, the Bode diagram is obtained by detecting the output of the torque meter, and the resonance frequency f is calculated from the Bode diagram.
Although the spring constant K of the dynamic torsion was calculated by calculating H and substituting the resonance frequency f H into the equation (3), the rotation fluctuation was calculated from the rotation detector 5 of the dynamometer of FIG. 1 instead of the torque meter. It is also possible to obtain the Bode diagram from the rotation fluctuation and obtain the spring constant K of the dynamic torsion from the Bode diagram in the same manner as in the first embodiment.
【0017】[0017]
【発明の効果】以上の説明からわかるように、請求項
1,2に係る動的捩りのばね定数の割り出し方法によれ
ば、静的捩りのばね定数ではなく、動的捩りのばね定数
を求めることにより、運転状態に近くてより正確な共振
周波数を求めることができる。このため、共振による振
動を原因とする機器の破壊の発生が未然に防止される。As is apparent from the above description, according to the method for determining the spring constant of dynamic torsion according to claims 1 and 2, not the spring constant of static torsion but the spring constant of dynamic torsion is obtained. As a result, a more accurate resonance frequency can be obtained close to the operating state. Therefore, it is possible to prevent the occurrence of breakage of the device due to the vibration due to the resonance.
【図1】本発明による動的捩りのばね定数の割り出し方
法の実施の形態1,2を実施するための構成図。FIG. 1 is a configuration diagram for carrying out Embodiments 1 and 2 of a method for determining a spring constant of dynamic torsion according to the present invention.
【図2】従来の静的捩りのばね定数の割り出し方法を実
施するための構成図。FIG. 2 is a configuration diagram for carrying out a conventional method of indexing a spring constant of static torsion.
【図3】エンジンの試験を行なうための装置の構成図。FIG. 3 is a configuration diagram of a device for performing an engine test.
2…トルクメータ 3…カップリング 4…ダイナモメータ 4a…回転軸 5…回転検出器 2 ... Torque meter 3 ... Coupling 4 ... Dynamometer 4a ... rotary shaft 5 ... Rotation detector
Claims (2)
れた軸の他端を回転させて捩り加振を行なわせ、加振周
波数を変化させて前記トルクメータの出力からボード線
図を求め、当該ボード線図から共振周波数を求め、捩り
のばね定数と共振周波数との関係式より捩りのばね定数
を算出することを特徴とする動的捩りのばね定数の割り
出し方法。1. A Bode diagram is obtained from the output of the torque meter by rotating the other end of a shaft, one end of which is connected to a fixed torque meter, to perform torsional vibration, changing the vibration frequency, A method for determining a spring constant of dynamic torsion, characterized in that the resonance frequency is obtained from the Bode diagram and the spring constant of torsion is calculated from a relational expression between the spring constant of torsion and the resonance frequency.
振周波数を変化させて回転検出器の出力から回転変動を
求め、当該回転変動からボード線図を求め、当該ボード
線図から共振周波数を求め、捩りのばね定数と共振周波
数との関係式より捩りのばね定数を算出することを特徴
とする動的捩りのばね定数の割り出し方法。2. The shaft is rotated to perform torsional vibration, the vibration frequency is changed to obtain the rotation fluctuation from the output of the rotation detector, the Bode diagram is obtained from the rotation fluctuation, and the Bode diagram is calculated from the Bode diagram. A method for determining a spring constant of a dynamic torsion, which comprises obtaining a resonance frequency and calculating a spring constant of the torsion from a relational expression between the spring constant of the torsion and the resonance frequency.
Priority Applications (1)
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JP2002145636A JP2003337092A (en) | 2002-05-21 | 2002-05-21 | Method for determining spring constant of dynamic torsion |
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JP2003337092A true JP2003337092A (en) | 2003-11-28 |
Family
ID=29704865
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012068200A (en) * | 2010-09-27 | 2012-04-05 | Meidensha Corp | Shaft torque control device of dynamometer |
CN102589675A (en) * | 2012-03-14 | 2012-07-18 | 南京埃斯顿自动控制技术有限公司 | Method for measuring mechanical resonance frequency by using servo driver |
CN108180981A (en) * | 2017-12-29 | 2018-06-19 | 国网浙江省电力有限公司电力科学研究院 | A kind of high-rating generator housing resonant frequency test method and device |
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JPS5587026A (en) * | 1978-12-26 | 1980-07-01 | Saginomiya Seisakusho Inc | Electro-hydraulic torsion tester |
JPS5950334A (en) * | 1982-09-16 | 1984-03-23 | Hitachi Ltd | Torsional vibration damping control device of shaft |
JPS6469923A (en) * | 1987-09-11 | 1989-03-15 | Saginomiya Seisakusho Inc | Method for measuring resonance point of resonating member |
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012068200A (en) * | 2010-09-27 | 2012-04-05 | Meidensha Corp | Shaft torque control device of dynamometer |
CN102589675A (en) * | 2012-03-14 | 2012-07-18 | 南京埃斯顿自动控制技术有限公司 | Method for measuring mechanical resonance frequency by using servo driver |
WO2013135138A1 (en) * | 2012-03-14 | 2013-09-19 | 南京埃斯顿自动控制技术有限公司 | Method for measuring mechanical resonance frequency by using servo driver |
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CN108180981A (en) * | 2017-12-29 | 2018-06-19 | 国网浙江省电力有限公司电力科学研究院 | A kind of high-rating generator housing resonant frequency test method and device |
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