JPS61206841A - Exciting force variable type vibration damper - Google Patents
Exciting force variable type vibration damperInfo
- Publication number
- JPS61206841A JPS61206841A JP60043814A JP4381485A JPS61206841A JP S61206841 A JPS61206841 A JP S61206841A JP 60043814 A JP60043814 A JP 60043814A JP 4381485 A JP4381485 A JP 4381485A JP S61206841 A JPS61206841 A JP S61206841A
- Authority
- JP
- Japan
- Prior art keywords
- excitation force
- vibration damper
- vibration
- phase
- excitation
- 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.)
- Granted
Links
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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Power Conversion In General (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の技術分野〕
〔発明の技術分野〕
本発明は、振動発生源の起振力に共振して振動している
構造物に対し、起振力と逆位相の起振力を与え、その振
動を減殺する起振力可変形消振機の改良に関わる。[Detailed Description of the Invention] [Technical Field of the Invention] [Technical Field of the Invention] The present invention is directed to a structure vibrating in resonance with the excitation force of a vibration source, which is Involved in improving vibration dampers with variable excitation force that apply excitation force and reduce vibration.
消振機は、種々の構造物に使われているが、ここでは、
船舶に対する応用を例にとって説明する。Vibration dampers are used in various structures, but here,
An example of application to ships will be explained.
船舶において、ディーゼルエンジン等の往復機関が発生
する起振力に船体が共振し、通常機関の回転の2倍に相
当する周波数で振動が発生することが多い。In ships, the hull of the ship resonates with the excitation force generated by a reciprocating engine such as a diesel engine, and vibrations are often generated at a frequency equivalent to twice the rotation of the normal engine.
そこで、第8図に示すように、2個の不平衡重錘1,2
を互いに逆方向に回転させ、鉛直方向に起振力を発生さ
せて、それを起振源の起振力と。Therefore, as shown in Fig. 8, two unbalanced weights 1 and 2 are
are rotated in opposite directions to generate an excitation force in the vertical direction, which is then combined with the excitation force of the excitation source.
逆位相関係になるように制御して、消振せしめる発明が
実施され、特公昭52−30079号公報で公告されて
いる。しかし、かかる発明において、起振源の起振力と
、消振機の起振力との位相関係は制御できるものの、消
振機の起振力までは制御できなかった。An invention for canceling vibrations by controlling to have an antiphase relationship has been carried out and is published in Japanese Patent Publication No. 52-30079. However, in this invention, although the phase relationship between the excitation force of the excitation source and the excitation force of the vibration damper can be controlled, the vibration excitation force of the vibration damper cannot be controlled.
したがって、起振力の大きさは、一度消振機を停止せし
めて重錘を交換するか、きわめて複雑な機構を用いて回
転重錘の回転半径を変更する方式が採られていたが、ど
ちらも実用性に乏しかった。Therefore, the magnitude of the vibration excitation force has been determined by either stopping the vibration damper and replacing the weight, or changing the radius of rotation of the rotating weight using an extremely complicated mechanism. It also lacked practicality.
また、一般に消振機に要求される起振力は、共振周波数
によって変化し、また、船舶などでは積荷の有無によっ
ても変化するので、ある点に起振力を合わせておくと、
他の共振点では効果が少なかったり、更に、逆に共振を
助長したりする不都合があった。In addition, the excitation force required for a vibration damper generally changes depending on the resonance frequency, and also changes depending on the presence or absence of cargo in ships, etc., so if the excitation force is adjusted to a certain point,
At other resonance points, there is a disadvantage that the effect is small or that resonance is even promoted.
一方、振動を単純に発生させるのみの機能を持つ、起振
機としては、従来より、第9図aおよびbの如く、互い
に逆回転して垂直起振力を発生する不平衡重錘1,2と
更にもう1組の不平衡重錘3.4を用意し1両組相互の
回転位相関係を差動歯車51によって加減して全体の起
振力を加減するものも公知である。しかしこれには複雑
な差動歯車装置1i51が必要であり、かつ、合成起振
力の位相を制御する適当な方法がなかったため、消振機
としては使用できなかった。On the other hand, as shown in FIGS. 9a and 9b, as shown in FIG. It is also known to prepare one set of unbalanced weights 3.4 in addition to the set of unbalanced weights 3.4, and to adjust the rotational phase relationship between the two sets using a differential gear 51 to adjust the overall excitation force. However, this required a complicated differential gear device 1i51, and there was no suitable method for controlling the phase of the combined excitation force, so it could not be used as a vibration damper.
本発明の目的は、起振力の大きさを運転中に任意に制御
できると同時に、その起振力の位相を起振源の起振位相
に対して任意の角度に制御できる起振力可変形消振機を
提供せんとするものである。An object of the present invention is to enable the vibration excitation force to be able to arbitrarily control the magnitude of the excitation force during operation, and at the same time to control the phase of the excitation force to an arbitrary angle with respect to the excitation phase of the excitation source. The present invention aims to provide a deformable vibration damper.
本発明による起振力可変形消振機は、起振源より発生す
る起振力に共振して振動する構造物に対し、その起振源
の起振力と同期しかつこれと逆位相の起振力を構造物に
与えて振動を減殺する消振機において、全く独立に制御
し得る消振機を2組設置し、かつ所望の起振力より必要
な偏角θを演算し、一方の消振機は、逆位相よりθだけ
進めた位相に制御し、他方の消振機は逆位相よりθだけ
遅らせた位相に制御することによって任意の合成起振力
を得るように構成したことを特徴とするものである。The variable excitation force type vibration damper according to the present invention is designed to provide a structure that vibrates in resonance with the excitation force generated by an excitation source, in synchronization with the excitation force of the excitation source and in the opposite phase. In a vibration damper that reduces vibration by applying vibrational force to a structure, two sets of vibration dampers that can be controlled completely independently are installed, and the necessary deflection angle θ is calculated from the desired vibrational force. The vibration damper is controlled to a phase that is θ ahead of the opposite phase, and the other vibration damper is controlled to a phase that is delayed by θ from the opposite phase, so that an arbitrary composite excitation force can be obtained. It is characterized by:
以下本発明を第1図および第2図に示す実施例について
説明するに、まず便宜上から本発明の原理構想について
説明する。本発明による起振力可変形消振機の概略構成
を示す。第2図aおよびbにおいて、1,2はその周面
に設けた平歯車5で噛合って互いに逆回転する不平衡重
錘で、回転することによって水平方向の起振力は互いに
相殺し、鉛直方向のみに起振力を発生するように構成さ
れている。この構成は公知の消振機と同様であり、この
不平衡重錘1,2は、重錘1に直結した駆動機6で速度
制御されている。さらに、3,4はその周面に設けた平
歯車7で噛合って1,2と全く同じ構成をした不平衡重
錘で、その重錘3に直結した駆動機8で駆動され、不平
衡重錘1,2の上部に重ねて設置されている。The present invention will be described below with reference to the embodiments shown in FIGS. 1 and 2. First, for convenience, the basic concept of the present invention will be explained. 1 shows a schematic configuration of a variable excitation force vibration damper according to the present invention. In FIGS. 2a and 2b, 1 and 2 are unbalanced weights that mesh with spur gears 5 provided on their circumferential surfaces and rotate in opposite directions, and as they rotate, horizontal excitation forces cancel each other out. It is configured to generate vibrational force only in the vertical direction. This configuration is similar to a known vibration damper, and the unbalanced weights 1 and 2 are speed-controlled by a driving machine 6 directly connected to the weight 1. Furthermore, 3 and 4 are unbalanced weights which have the exact same structure as 1 and 2, meshing with spur gears 7 provided on their circumferential surfaces, and are driven by a driver 8 directly connected to the weight 3, and are unbalanced. It is placed on top of weights 1 and 2.
以後、簡単にするため、1,2で構成される部分を消振
機A、3,4で構成される部分を消振機。Hereinafter, for the sake of simplicity, the part made up of 1 and 2 will be referred to as a vibration damper A, and the part made up of 3 and 4 will be referred to as a vibration damper.
Bと称する。消振機Aと消振機Bは、機械的には全く連
絡なく、自由に回転することができる。It is called B. The vibration dampers A and B have no mechanical communication at all and can rotate freely.
今、不平衡重錘の不平衡重量をm (kg)等価半径を
r(m)、回転角速度をω(rad/s〕とすると、各
重錘が発生する遠心力Fは
F=mrω” (N) Q)である。Now, if the unbalanced weight of the unbalanced weight is m (kg), the equivalent radius is r (m), and the rotational angular velocity is ω (rad/s), then the centrifugal force F generated by each weight is F=mrω" ( N) Q).
今、第3図のように、水平方向を工、鉛直方向をソとし
て本発明による消振機の起振力を表現すると
Fz =Fcos(ωt)
■Fy =Fsin(ωt) (3と
なる。Now, as shown in Fig. 3, if we express the excitation force of the vibration damper according to the present invention with E in the horizontal direction and G in the vertical direction, Fz = F cos (ωt)
■Fy =Fsin(ωt) (3).
消振機Aの2個の不平衡重錘1,2が互いにν軸に関し
対称の関係で逆回転しているので、それぞれの起振力を
1,2の添字で表わすと下記の(イ)〜■式となる。Since the two unbalanced weights 1 and 2 of vibration damper A are rotating in opposite directions in a symmetrical relationship with respect to the ν axis, the respective excitation forces can be expressed as subscripts 1 and 2 as shown in (a) below. 〜■ Formula.
Fzl =Fcos((II t) −@)F
yl==Fsin(ωt) ■Fz2
=Fcos(π−ωt)=−Fxl(eFy2 = F
cos(π−(II t) = Fyt ■した
がって、合成した起振力をあらためてFXaeFV&と
おくと■および0式となる。Fzl =Fcos((II t) −@)F
yl==Fsin(ωt) ■Fz2
=Fcos(π-ωt)=-Fxl(eFy2 = F
cos(π-(II t) = Fyt (2) Therefore, if the combined excitation force is again set as FXaeFV&, it becomes (2) and the formula 0.
Fxa = Fxx +’Fx2= O(aFya=F
y1+Fy2= 2Fyl= 2Fsin(ωt)
(9)つまり、水平方向の起振力は相殺され、
鉛直方向の起振力のみが相加わって2倍になっている。Fxa = Fxx +'Fx2= O(aFya=F
y1+Fy2= 2Fyl= 2Fsin(ωt)
(9) In other words, the horizontal excitation force is canceled out,
Only the excitation forces in the vertical direction are added together and doubled.
これが、従来の公知の消振機の原理である。This is the principle of conventional, well-known vibration dampers.
さて、(9)式を更に詳しく書くと
FVa= 2mrω”5in(ωt) (1
0)となり、起振力の大きさは、m、r、ωの関数であ
ることがわかる。このうち、ωは起振源と同期させるた
めに一義的に定まってしまうから、もし起振力を加減し
たければ、mかrを可変にせざるを得ながったが、回転
中にこれを可変にする有効な方法を得ることは困難であ
る。Now, writing equation (9) in more detail, FVa = 2mrω”5in(ωt) (1
0), and it can be seen that the magnitude of the excitation force is a function of m, r, and ω. Of these, ω is uniquely determined in order to synchronize with the excitation source, so if you wanted to adjust the excitation force, you had to make m or r variable, but this It is difficult to find an effective way to make this variable.
本発明においては、上記の消振機Aの上に更に消振機B
を重ねて置き、これをAに対しである位相角を持たせな
がら同じωで運転する。これの起振力は3,4を添字と
して(11)弐〜(14)式で表わされる。In the present invention, a vibration damper B is further provided on top of the vibration damper A.
are placed one on top of the other, and are operated at the same ω while having a certain phase angle with respect to A. The excitation force is expressed by equations (11) to (14) with subscripts 3 and 4.
FzB=Fcos(ωt+20) (
11)Fy3=Fsin(+11 t+ 20)
(12)Fz4=Fcos(π−ωt+2
0)= Fxa (13)Fy4=Fsin(π
−ωt+20)=Fv3 (14)ただし、
2θ=不平衡重錘1と3の位相差
となる。この関係を第4図に示す。FzB=Fcos(ωt+20) (
11) Fy3=Fsin(+11 t+ 20)
(12) Fz4=Fcos(π−ωt+2
0)=Fxa (13)Fy4=Fsin(π
-ωt+20)=Fv3 (14) However, 2θ=phase difference between unbalanced weights 1 and 3. This relationship is shown in FIG.
これらの合成起振力をFより+ Fvbとおくと(15
)および(16)式となる。If we set these combined vibrational forces as +Fvb from F, then (15
) and equation (16).
Fより=o (ts)F
yb= 2Fya= 2Fsin(ωt+20)
(16)ここで(9)式と(16)式を比較すると、互
いに20だけ位相がずれているだけである。From F=o (ts)F
yb= 2Fya= 2Fsin(ωt+20)
(16) If we compare equations (9) and (16) here, we find that they are only out of phase by 20 from each other.
今、消振機A、B両者位相の中間に仮想の位相を考える
と、FVaとFvbはこの仮想の位相を中心にしてそれ
ぞれθだけ進みおよび遅れの位相を持つ2個の起振力と
みなせる。Now, if we consider a virtual phase between the phases of vibration dampers A and B, FVa and Fvb can be regarded as two excitation forces that lead and lag by θ with respect to this virtual phase. .
したがって■)、 (16)式を書き直せば次の(17
)式および(18)式となる。Therefore, if we rewrite equation (16), we get the following (17
) and (18).
FVa= 2Fsin(ωを一〇> (1
7)Fyb= 2Fsin(ωを十〇>
(18)これを時間軸をtとして図示すれば第5図とな
る。FVa= 2Fsin (ω10> (1
7) Fyb = 2Fsin (ω = 10>
(18) If this is illustrated with the time axis as t, it becomes FIG. 5.
(17)式と(18)式とを合成した起振力をF、とす
ると、単振動合成公式により
Fy=2F(sin(ωt−θ)+5in(ωt+ θ
))=2r′rF 1 cos 2 e 5in(
ωt) (19)となる。Let F be the excitation force obtained by combining equations (17) and (18), then Fy=2F(sin(ωt-θ)+5in(ωt+θ) according to the simple harmonic synthesis formula.
))=2r′rF 1 cos 2 e 5in(
ωt) (19).
これによれば、F、の位相角は第5図に示すように常に
FlllaとFybの中間にあり、かつ起振力は1
cos eゴに比例することがわかる。つまり、とな
る。(19)式に0式を代入すれば次の(20)式とな
る。According to this, the phase angle of F is always between Fulla and Fyb, as shown in Figure 5, and the excitation force is 1
It can be seen that it is proportional to cos e. In other words, it becomes. Substituting equation 0 into equation (19) results in equation (20) below.
Fv=2(τmr (11” 3ゴ5in(ωt)
(20)したがって、この仮想の位相を起振源の起振力
に対し、逆位相になるようにすれば、消振機としての役
目を果たし、また。Fv=2(τmr (11” 3go5in(ωt)
(20) Therefore, if this virtual phase is made to be in opposite phase to the excitation force of the excitation source, it will serve as a vibration damper.
FK = 2 Ebr (112(丁T習消℃璽り一(
21)を制御すれば、所望の起振力FKが得られること
になる。FK = 2 Ebr (112
21), the desired excitation force FK can be obtained.
本発明を実施するための具体的な例を説明する。A specific example for implementing the present invention will be explained.
(21)式をθについて解くと下記の(22)式となる
。When equation (21) is solved for θ, the following equation (22) is obtained.
m、rは通常は定数であるから、所望の起振力FKと、
現在の角速度ωがわかれば(22)よりθが求まる。Since m and r are usually constants, the desired excitation force FK,
If the current angular velocity ω is known, θ can be found from (22).
したがって1本発明による消振機の制御装置としては、
起振源より発生する起振力を打ち消すため、それと逆位
相、即ちπだけずれた合成起振力を発生しなければなら
ないが、消振機Aに対してはπ十〇、消振機Bに対して
はπ−θの位相になるように制御することにより、目的
を達せんとするものである。Therefore, as a control device for a vibration damper according to the present invention,
In order to cancel the excitation force generated from the excitation source, it is necessary to generate a composite excitation force that is in the opposite phase to it, that is, shifted by π. The objective is to be achieved by controlling the phase so that it has a phase of π-θ.
第1図は本発明による起振力可変形消振機に用いる制御
装置の回路を示す。第1図において、11a。FIG. 1 shows a circuit of a control device used in a variable excitation force type vibration damper according to the present invention. In FIG. 1, 11a.
11bは、消振機A、消振機Bを制御する同期式制御部
である。面制御部11a、 llbは同一構成であるの
で、制御部11aを代表して説明する。11b is a synchronous control unit that controls the vibration damper A and the vibration damper B. Since the surface control units 11a and llb have the same configuration, the control unit 11a will be explained as a representative.
位相角弁別器12aには、起振源位相パルス13aと消
振機位相パルス14aが入力され、両者の位相差信号1
5aが作られる。位相差信号15aを、位相差設定信号
16aと比較し、信号15aと信号16aが等しくなる
ように消振機の回転速度を制御すれば、例えば信号16
aを起振源と逆位相πになるようにしておくと、消振機
の起振力の位相は常に逆位相になり、消振効果が得られ
る。以上が従来の消振機の制御原理である。The excitation source phase pulse 13a and the damper phase pulse 14a are input to the phase angle discriminator 12a, and the phase difference signal 1 between the two is input.
5a is made. For example, if the phase difference signal 15a is compared with the phase difference setting signal 16a and the rotational speed of the vibration damper is controlled so that the signal 15a and the signal 16a are equal, the signal 16
If a is set to have an opposite phase to the vibration source, the phase of the vibration excitation force of the vibration damper will always be opposite to that of the vibration source, and a vibration damping effect can be obtained. The above is the control principle of the conventional vibration damper.
本発明は、第1図において、起振力設定器21により起
振力を設定してFK/2□mrとする。その分母の2
a/1 m rは機械の寸法で定まる定数である。次に
、角速度ω(消振機A、Bの角速度の平均またはどちら
も定常的には等しいから、どちらかの角速度)を乗算器
または自乗演算器22で自乗してω2を演算する。In the present invention, as shown in FIG. 1, the excitation force is set by the excitation force setting device 21 to be FK/2□mr. 2 of the denominator
a/1 m r is a constant determined by the dimensions of the machine. Next, angular velocity ω (the average of the angular velocities of vibration absorbers A and B, or either angular velocity since they are both stationary) is squared by a multiplier or a square calculator 22 to calculate ω2.
次に除算器23で、起振力設定信号Fg/2[mrを角
速度の自乗ω2で除算し、Fx/2Ehrω2を演算す
る。更にその信号を乗算器または自乗演算器24で自乗
して1を差引き、関数演算器25で逆余弦の1/2を演
算してθを得る。Next, the divider 23 divides the excitation force setting signal Fg/2[mr by the square of the angular velocity ω2 to calculate Fx/2Ehrω2. Further, the signal is squared by a multiplier or square calculator 24, 1 is subtracted, and 1/2 of the inverse cosine is calculated by a function calculator 25 to obtain θ.
これにより(22)式の計算が実行され、θが求まった
ことになる。この得られたθを、一つはそのまま前述の
消振機制御部11aの位相差設定信号16aに加算する
ように構成し、一つは符号反転器26で符号を反転して
一〇を得て、これを消振機制御部16bに加算するよう
に構成する。As a result, the calculation of equation (22) is executed, and θ is determined. One of the obtained θ is added as is to the phase difference setting signal 16a of the damper control section 11a, and the other is inverted in sign by the sign inverter 26 to obtain 10. The configuration is such that this is added to the vibration damper control section 16b.
かようにすれば、消振機Aは、゛逆位相子〇に、消振機
Bは逆位相−〇に制御されるから、その合成起振力は常
に逆位相を向くと同時に、その起振力の大きさはθ=0
の時最大、θ=■の時0になり、その中間で任意の大き
さに制御できる。In this way, the vibration damper A is controlled to have an opposite phase, and the vibration damper B is controlled to have an opposite phase of −○, so that their combined excitation force always faces the opposite phase, and at the same time its origin The magnitude of the vibration force is θ=0
It is maximum when θ=■, and becomes 0 when θ=■, and can be controlled to any size in between.
また、第1図では、起振力設定器21により起振力を一
定か、または手動で制御する方法を例にとったが、実際
には各ωによって、構造物の共振の度合が異なるので、
必要な起振力は一般に第6図のようなωの関数になる。In addition, in Fig. 1, we have taken as an example a method in which the excitation force is kept constant using the excitation force setting device 21 or controlled manually, but in reality, the degree of resonance of the structure differs depending on each ω. ,
The required excitation force is generally a function of ω as shown in FIG.
したがって、第7図のように、ωを任意関数発生器26
を通して起振力設定値を演算させて、第1図の起振力設
定器21の代替をさせることによりあらゆる範囲の速度
に対し、最も有効な消振効果を発揮することができる。Therefore, as shown in FIG.
By calculating the excitation force setting value through the vibration excitation force setting device 21 in FIG. 1, the most effective vibration damping effect can be achieved over a wide range of speeds.
また、単純に、起振力がω2に比例すれば良い場合は、
第1図の演算器22゜除算器23を除いてやるだけで良
いことは、勿論である。Also, if the excitation force simply needs to be proportional to ω2, then
Of course, it is sufficient to simply omit the arithmetic unit 22 and the divider 23 in FIG.
また一般に振動部分の振幅を検出して、その値をフィー
ドバックし、この振幅を最小にするように消振機の起振
力を内的制御する事も容易にできる。Generally, it is also easy to detect the amplitude of the vibrating portion, feed back that value, and internally control the excitation force of the vibration damper so as to minimize this amplitude.
なお、以上の説明は、制御に演算増幅器等を使ったアナ
ログ制御を例にとったが、電子計算機等を使用したデジ
タル制御を行なっても実現できることは当然である。ま
た、消振機は説明の都合上、鉛直方向に起振力を発生す
るものを例にとったが、本発明はこれにより範囲を限定
されるものでなく。Note that although the above explanation has taken analog control using an operational amplifier or the like as an example, it is of course possible to implement digital control using an electronic computer or the like. Furthermore, for convenience of explanation, a vibration absorber that generates vibrational force in the vertical direction has been taken as an example, but the scope of the present invention is not limited thereby.
あらゆる方向に起振力を発揮するものに適用されること
は勿論のことである。It goes without saying that this method can be applied to anything that exerts an excitation force in any direction.
本発明によれば、消振機を運転中に、起振源に対する消
振機の起振力の位相を最適に保ったまま。According to the present invention, while the vibration damper is in operation, the phase of the excitation force of the vibration damper with respect to the vibration source remains optimally maintained.
その合成起振力をOから最大まで任意に可変できるので
、あらゆる点において最適な消振効果が得られるから、
実用上の価値は大きい。Since the combined vibration excitation force can be arbitrarily varied from 0 to the maximum, the optimal vibration damping effect can be obtained in all respects.
It has great practical value.
消振機が2台必要となるので、コストアップになる懸念
があるが、それぞれは必要とする容量の半分で良く、さ
してコストアップにならない。Since two vibration absorbers are required, there is a concern that the cost will increase, but each has only half the required capacity, so the cost does not increase much.
さらに、副次的効果として、かかる慣性モーメントの大
きい負荷は、回ってしまえばあまり動力は必要でないが
、始動の時のために大きい電源容量を必要とする。しか
し、本発明のように2台に分散し、始動に時間差をつけ
れば、電源容量は1台分ですむというコストダウン要素
があり、全体的に考えれば従来品とほぼ同一であると言
える。Furthermore, as a side effect, such a load with a large moment of inertia does not require much power once it is turned, but it requires a large power supply capacity for starting. However, if the power supply is divided into two units and the start times are set at different times as in the present invention, the power supply capacity can be reduced to one unit, which is an element of cost reduction, and overall it can be said that it is almost the same as the conventional product.
第1図は本発明による起振力可変形消振機の制御装置の
一実施例を示す回路図、第2図aおよびbは本発明によ
る起振力可変形消振機の概略構成を示す正面図および側
面図、第3図は消振機の起振力の発生原理を説明するた
めのベクトル図、第4図は2台の消振機の起振力の位相
関係を示すベクトル図、第5図は2台の消振機の起振力
および合成起振力の関係を示す波形図、第6図は起振力
を示す斜視図、第9図aおよびbは同じ〈従来の消振機
を示す正面図および側面図である。
A、B・・・消振機 1,2,3.4・・・不
平衡重錘5.7・・・平歯車 6,8・・・駆
動機11a、llb・・・制御部 12a・・・位
相角弁別器13a・・・起振源位相パルス
14a・・・消振様位相パルス 15a・・・位相信
号16a・・・位相差設定信号 21・・・起振力設定
器22.24.25・・・演算器 23・・・除算器
26・・・符号反転器
(8733) 代理人 弁理士 猪 股 祥 晃(ほ
か1名)第1図
第 3 図
第 4 図
第 5 図
第 6 図
W
第7図
昂
第 8 図
第 9 図
(cL) (!:))FIG. 1 is a circuit diagram showing an embodiment of a control device for a variable excitation force type vibration damper according to the present invention, and FIGS. 2a and 2 b show a schematic configuration of a vibration suppressor with variable excitation force according to the present invention. A front view and a side view, Fig. 3 is a vector diagram for explaining the principle of generation of excitation force of the vibration damper, Fig. 4 is a vector diagram showing the phase relationship of the excitation force of two vibration dampers, Fig. 5 is a waveform diagram showing the relationship between the excitation force and the combined excitation force of the two vibration dampers, Fig. 6 is a perspective view showing the vibration force, and Fig. 9 a and b are the same. It is a front view and a side view which show a shaker. A, B... Vibration damper 1, 2, 3.4... Unbalanced weight 5.7... Spur gear 6, 8... Drive machine 11a, llb... Control section 12a... - Phase angle discriminator 13a... Excitation source phase pulse 14a... Vibration cancellation-like phase pulse 15a... Phase signal 16a... Phase difference setting signal 21... Excitation force setting device 22.24. 25... Arithmetic unit 23... Divider 26... Sign inverter (8733) Agent Patent attorney Yoshiaki Inomata (and one other person) Figure 1 Figure 3 Figure 4 Figure 5 Figure 6 W Figure 7 Figure 8 Figure 9 (cL) (!:))
Claims (2)
造物に対し、その起振源の起振力と同期しかつこれと逆
位相の起振力を構造物に与えて振動を減殺する消振機に
おいて、全く独立に制御し得る消振機を2組設置し、か
つ所望の起振力より必要な偏角θを演算し、一方の消振
機は逆位相よりθだけ進めた位相に制御し、他方の消振
機は逆位相よりθだけ遅らせた位相に制御することによ
って任意の合成起振力を得るように構成したことを特徴
とする起振力可変形消振機。(1) A structure that vibrates in resonance with the excitation force generated by an excitation source is vibrated by applying an excitation force that is synchronized with and in opposite phase to the excitation force of the excitation source to the structure. Two sets of dampers are installed that can be controlled completely independently, and the necessary deflection angle θ is calculated based on the desired excitation force. A variable excitation force type vibration damper characterized in that the vibration damper is configured to obtain an arbitrary composite vibration force by controlling the vibration damper to an advanced phase and controlling the other vibration damper to a phase delayed by θ from the opposite phase. Machine.
F_K)/(2√2mrω^2))^2−1}(但しF
_Kは所望の起振力、ωは角速度、m、rは定数)から
演算して得られたことを特徴とする特許請求の範囲第1
項記載の起振力可変形消振機。(2) The argument angle θ is calculated using the following formula θ=1/2cos^*^1;((
F_K)/(2√2mrω^2))^2-1} (However, F
_K is a desired excitation force, ω is an angular velocity, and m and r are constants).
Variable excitation force vibration damper as described in Section 1.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP60043814A JPS61206841A (en) | 1985-03-07 | 1985-03-07 | Exciting force variable type vibration damper |
KR1019850005408A KR910000778B1 (en) | 1985-03-07 | 1985-07-27 | Exciting force variable type vibration damper |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP60043814A JPS61206841A (en) | 1985-03-07 | 1985-03-07 | Exciting force variable type vibration damper |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS61206841A true JPS61206841A (en) | 1986-09-13 |
JPH0364736B2 JPH0364736B2 (en) | 1991-10-08 |
Family
ID=12674207
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP60043814A Granted JPS61206841A (en) | 1985-03-07 | 1985-03-07 | Exciting force variable type vibration damper |
Country Status (2)
Country | Link |
---|---|
JP (1) | JPS61206841A (en) |
KR (1) | KR910000778B1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2010512495A (en) * | 2006-12-15 | 2010-04-22 | ソレタンシュ フレシネ | Vibration control device for structures |
-
1985
- 1985-03-07 JP JP60043814A patent/JPS61206841A/en active Granted
- 1985-07-27 KR KR1019850005408A patent/KR910000778B1/en not_active IP Right Cessation
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2010512495A (en) * | 2006-12-15 | 2010-04-22 | ソレタンシュ フレシネ | Vibration control device for structures |
Also Published As
Publication number | Publication date |
---|---|
KR860007580A (en) | 1986-10-15 |
JPH0364736B2 (en) | 1991-10-08 |
KR910000778B1 (en) | 1991-02-06 |
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