JPH03186631A - Dynamic damper - Google Patents
Dynamic damperInfo
- Publication number
- JPH03186631A JPH03186631A JP32408489A JP32408489A JPH03186631A JP H03186631 A JPH03186631 A JP H03186631A JP 32408489 A JP32408489 A JP 32408489A JP 32408489 A JP32408489 A JP 32408489A JP H03186631 A JPH03186631 A JP H03186631A
- Authority
- JP
- Japan
- Prior art keywords
- elastic member
- dynamic damper
- load voltage
- cavity
- viscosity
- 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
- 239000012530 fluid Substances 0.000 claims abstract description 18
- 230000005284 excitation Effects 0.000 claims description 4
- 230000000694 effects Effects 0.000 abstract description 7
- 230000007423 decrease Effects 0.000 abstract description 4
- 238000000518 rheometry Methods 0.000 abstract 3
- 239000007788 liquid Substances 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 10
- 238000013016 damping Methods 0.000 description 7
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000001514 detection method Methods 0.000 description 1
- 239000000615 nonconductor Substances 0.000 description 1
Landscapes
- Vibration Prevention Devices (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、例えばエンジンの回転に応じて生じる振動に
対して、回転数の全域にわたってその振動を抑制するた
めのダイナミックダンパに関するものである。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a dynamic damper for suppressing vibrations generated in accordance with, for example, the rotation of an engine over the entire range of rotational speed.
（従来の技術）
第１１図は従来のダイナミックダンパの一例を示す部分
図で、第１２図はそれを振動モデル化した説明図である
。(Prior Art) FIG. 11 is a partial diagram showing an example of a conventional dynamic damper, and FIG. 12 is an explanatory diagram showing a vibration model of the dynamic damper.
図中１は被制振体、２はゴム等の弾性部材、３はこの弾
性部材２を介して被制振体１に連結された所定の質量を
有する質量体である。In the figure, reference numeral 1 denotes a vibration damped body, 2 an elastic member such as rubber, and 3 a mass body having a predetermined mass that is connected to the vibration damped body 1 via the elastic member 2.
また第１２図において、Ｋは弾性部材２のばね要素のば
ね定数、Ｃは弾性部材２の減衰要素、Ｍは質量体３の質
量である。Further, in FIG. 12, K is the spring constant of the spring element of the elastic member 2, C is the damping element of the elastic member 2, and M is the mass of the mass body 3.
（発明が解決しようとする課Ｍ）
従来のダイナミックダンパは、第１１図および第１２図
に示すように、質量Ｍの質量体３と、ばね定数におよび
減衰要素Ｃを有する弾性部材２とによって横取されてい
る。(Problem M to be Solved by the Invention) As shown in FIGS. 11 and 12, a conventional dynamic damper includes a mass body 3 having a mass M and an elastic member 2 having a spring constant and a damping element C. It has been stolen.
第１３図は、横座標に第１１．１２図に示したダイナミ
ックダンパの周波数をとり、縦座標に質量体３の変位を
とった場合の特性を示すもので、曲線Ａは減衰要素Ｃが
小さいときのものであり、曲線Ｂは減衰要素Ｃが大きい
ときのものである。Figure 13 shows the characteristics when the frequency of the dynamic damper shown in Figure 11.12 is plotted on the abscissa and the displacement of the mass body 3 is plotted on the ordinate.Curve A shows the small damping element C. The curve B is the one when the damping element C is large.
これから従来のダイナミックダンパでは、減衰要素Ｃを
変えても、質量体の変位のピーク時の高さは変化するが
、そのピーク時の共振周波数はほとんど変わらないこと
がわかる。It can be seen from this that in the conventional dynamic damper, even if the damping element C is changed, the height at the peak of the displacement of the mass changes, but the resonance frequency at the peak does not change much.
従来のダイナミックダンパでは、質量体３の質量Ｍ、お
よび弾性部材２のばね定数Ｋを可変にすることが困難で
あるから、ダイナミックダンパのチューニング周波数が
一つに限られる結果、エンジンの回転数に応じて生じる
振動に対しては、回転数の全域にわたってダイナミック
ダンパ効果を得るのが難しいという問題点があった。In conventional dynamic dampers, it is difficult to vary the mass M of the mass body 3 and the spring constant K of the elastic member 2, so the tuning frequency of the dynamic damper is limited to one. There has been a problem in that it is difficult to obtain a dynamic damper effect over the entire range of rotational speeds with respect to the vibrations that occur accordingly.
（課題を解決するための手段）
上述の問題点を解決するため本発明においては、被制振
体に弾性部材を介して所定の質量体を設けたダイナミッ
クダンパにおいて、前記弾性部材内に空洞を設け、その
空洞内に負荷電圧に応じて粘度が変化する電気レオロジ
ー流体を充填し、その流体に電圧を印加できる電極を設
け、この電極に加振周波数に応じて変化する電圧を印加
するようにしてダイナミックダンパを構成する。(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention provides a dynamic damper in which a predetermined mass body is provided on a damped body via an elastic member, in which a cavity is formed in the elastic member. The cavity is filled with an electrorheological fluid whose viscosity changes depending on the load voltage, and an electrode capable of applying a voltage to the fluid is provided, and a voltage that changes depending on the excitation frequency is applied to the electrode. to configure a dynamic damper.
（作 用）
上述のように本発明においては、弾性部材内に空洞を設
け、その空洞内に負荷電圧に応じて粘度が変化する電気
レオロジー流体を充填し、その流体に電圧を印加できる
電極を設け、この電極に加振周波数に応じて変化する電
圧を印加するようにしたから、前記電気レオロジー流体
の粘度が加振周波数に応じて変化することにより、前記
弾性部材の変形のしやすさが変化して、そのばね定数が
変化する結果、共振周波数が連続的に変化するから、加
振周波数の全域にわたってダイナミックダンパ効果を得
ることができる。(Function) As described above, in the present invention, a cavity is provided in the elastic member, an electrorheological fluid whose viscosity changes depending on the applied voltage is filled in the cavity, and an electrode capable of applying a voltage to the fluid is provided. Since the viscosity of the electrorheological fluid changes depending on the excitation frequency, the ease with which the elastic member deforms is reduced. As a result of the change in the spring constant, the resonant frequency changes continuously, so a dynamic damper effect can be obtained over the entire range of excitation frequencies.
（実施例）
以下、第１図〜第１０図について本発明の詳細な説明す
る０図中前記符合と同一の符合は同等のものを示す。す
なわち、図中１は被制振体、２はゴム等の弾性部材、３
はこの弾性部材２を介して被制振体ｌに連結された所定
の質量を有するＸ１体である。(Example) Hereinafter, the present invention will be described in detail with reference to FIGS. 1 to 10. In FIG. That is, in the figure, 1 is a damped body, 2 is an elastic member such as rubber, and 3 is a damped member.
is an X1 body having a predetermined mass and connected to the damped body l via the elastic member 2.
本実施例においては、弾性部材２内に空洞４を設けると
共に、この弾性部材２を第１，２図において上下に二分
割する。In this embodiment, a cavity 4 is provided in the elastic member 2, and the elastic member 2 is divided into upper and lower halves in FIGS. 1 and 2.
また第３図および第４図に示すように、電気絶縁物製の
リングを二分割して、それぞれ半円弧状のインタリング
５．５を形威し、この各インクリング５に電極保持用の
孔５ａを設け、この穴５ａを介して電極６を保持したイ
ンタリング５，５を、前記した弾性部材２の分割面間に
介挿すると共に、空洞４内に負荷電圧に応じて粘度が変
化する電気レオロジー流体７を充填し、前記電極６にエ
ンジン回転数に応じて変化する電圧を印加するようにす
る。Further, as shown in Figs. 3 and 4, the ring made of electrical insulator is divided into two parts, each forming a semicircular arc-shaped interring 5.5, and each ink ring 5 has an electrode holding ring. A hole 5a is provided, and the interrings 5, 5 holding the electrode 6 through the hole 5a are inserted between the split surfaces of the elastic member 2, and the viscosity changes depending on the load voltage inside the cavity 4. The electrode 6 is filled with an electrorheological fluid 7, and a voltage that changes depending on the engine speed is applied to the electrode 6.
すなわち第１図中の８は、電極６，６に接続した電圧発
生装置で、９はその電圧発生装置８と接続したコントロ
ーラ、ＩＯはそのコントローラ９と接続したエンジン回
転数検出装置である。That is, 8 in FIG. 1 is a voltage generating device connected to the electrodes 6, 6, 9 is a controller connected to the voltage generating device 8, and IO is an engine rotation speed detecting device connected to the controller 9.
第５図は、電気レオロジー流体７の粘度と、負荷電圧と
の関係を示す特性図である。すなわち、負荷電圧が大き
くなると、電気レオロジー流体７の粘度が大きくなるこ
とがわかる。そしてこの場合は、弾性部材２内の空洞４
がつぶれにくくなり、ばね定数も大きくなる。したがっ
てこの場合は、質量体３と弾性部材２で構成されるダイ
ナミックダンパの共振周波数が高くなる。FIG. 5 is a characteristic diagram showing the relationship between the viscosity of the electrorheological fluid 7 and the load voltage. That is, it can be seen that as the load voltage increases, the viscosity of the electrorheological fluid 7 increases. In this case, the cavity 4 in the elastic member 2
is less likely to collapse, and the spring constant is also increased. Therefore, in this case, the resonance frequency of the dynamic damper composed of the mass body 3 and the elastic member 2 becomes high.
また負荷電圧が小さくなって電気レオロジー流体７の粘
度が小さくなると、弾性部材２内の空洞４がつぶれやす
くなって、ばね定数も小さくなる。Furthermore, when the load voltage decreases and the viscosity of the electrorheological fluid 7 decreases, the cavity 4 within the elastic member 2 becomes more likely to collapse, and the spring constant also decreases.
したがってこの場合は共振周波数が低くなる。Therefore, in this case, the resonant frequency becomes low.
そして第５図に示したように、電気レオロジー流体は、
負荷電圧に対する粘度の変化が連続的に行われるので、
弾性部材２のばね定数も第６図に示すように、負荷電圧
に対して連続的に変化する。As shown in Figure 5, the electrorheological fluid is
Since the viscosity changes continuously with respect to the load voltage,
The spring constant of the elastic member 2 also changes continuously with respect to the load voltage, as shown in FIG.
したがってダイナミックダンパの共振周波数も、第７図
に示すように、負荷電圧に対して連続的に変化する。Therefore, the resonant frequency of the dynamic damper also changes continuously with respect to the load voltage, as shown in FIG.
すなわち本発明によれば、エンジンの回転数に応じて生
じる振動問題に対して、回転数に同期して変化する負荷
電圧を電極６．６にかけることにより、回転数の全域に
わたってダイナミックダンパ効果を得ることができる。That is, according to the present invention, in order to solve the vibration problem that occurs depending on the engine speed, a dynamic damper effect can be achieved over the entire engine speed range by applying a load voltage that changes in synchronization with the engine speed to the electrode 6.6. Obtainable.
なお、本実施例において使用したインクリング５は、電
極６を確実に保持すると共に、弾性部材２を保護する作
用を有している。Note that the ink ring 5 used in this example has the function of reliably holding the electrode 6 and protecting the elastic member 2.
また第８図は、電極６を図示しない状態の本発明ダイナ
ミックダンパの説明図であり、第９図はそれを振動モデ
ル化した説明図である。図中Ｍは質量体３の質量、Ｋ１
は■部のばね定数、Ｋ２はＩ。Further, FIG. 8 is an explanatory diagram of the dynamic damper of the present invention in a state in which the electrodes 6 are not shown, and FIG. 9 is an explanatory diagram of the dynamic damper as a vibration model. In the figure, M is the mass of mass body 3, K1
is the spring constant of part ■, and K2 is I.
■部のばね定数、Ｃ１は■部の可変の減衰要素、Ｃ２は
Ｉ、ＩＩ部の減衰要素である。C1 is the spring constant of part 2, C1 is a variable damping element of part 2, and C2 is a damping element of parts I and II.
すなわち本発明のダイナミックダンパは、■。That is, the dynamic damper of the present invention has ■.
■部と■部が直列になっている振動系で表現できる。そ
してＣ，＝Ｏのときは、ばね定数はに１とに、の直列ば
ねとなり、ばね定数は最も小さくなり、第１０図に示す
ように、質量体の変位のピーク時における共振周波数も
、曲線りで示すように最も低い。It can be expressed by a vibration system in which part ■ and part ■ are connected in series. When C,=O, the spring constant becomes a series spring with a spring constant of 1, and the spring constant becomes the smallest.As shown in Fig. 10, the resonance frequency at the peak of the displacement of the mass also changes according to the curve is the lowest as shown in .
またＣ＋＝■のときは、ばね定数はに２で決まり、質量
体の変位のピーク時における共振周波数は、第１０図の
曲線Ｈで示すように最も高い。When C+=■, the spring constant is determined by 2, and the resonance frequency at the peak of the displacement of the mass is the highest, as shown by curve H in FIG.
そしてＣＩがＯ〜のまでの中間の値の場合は、第１０図
の曲線Ｅ、Ｆ、Ｇのようになる。しかしてこれらの各曲
線Ｄ−Ｈのそれぞれのピークをｄ、ｅ。When CI is an intermediate value between 0 and 0, the curves E, F, and G in FIG. 10 are obtained. Therefore, the respective peaks of each of these curves DH are d and e.
ｒ、ｇ、ｈで示せば、これら各ピークを結ぶ曲線ｄ−ｅ
−ｆ−ｇ−ｈが、本発明のダイナミックダンパによる共
振周波数の連続的変化を示すものである。If indicated by r, g, h, the curve connecting these peaks is d-e
-fgh indicates a continuous change in resonance frequency due to the dynamic damper of the present invention.
（発明の効果）
上述のように本発明においては、弾性部材２内に空洞４
を設け、その空洞４内に負荷電圧に応じて粘度が変化す
る電気レオロジー流体７を充填し、その流体７に電圧を
印加できる電極６を設け、この電極６にエンジン回転数
に応じて変化する電圧を印加するようにしたから、前記
電気レオロジー流体７の粘度がエンジンの回転数に応じ
て変化することにより、前記弾性部材２の変形のしやす
さが変化して、そのばね定数が変化する結果、共振周波
数が連続的に変化するから、本発明によれば、回転数の
全域にわたってダイナミックダンパ効果を得ることがで
きるという効果が得られる。(Effects of the Invention) As described above, in the present invention, the cavity 4 is provided in the elastic member 2.
The cavity 4 is filled with an electrorheological fluid 7 whose viscosity changes depending on the load voltage, and an electrode 6 that can apply a voltage to the fluid 7 is provided, and the electrode 6 has a viscosity that changes depending on the engine speed. Since a voltage is applied, the viscosity of the electrorheological fluid 7 changes in accordance with the engine speed, which changes the ease with which the elastic member 2 deforms, and its spring constant changes. As a result, since the resonant frequency changes continuously, according to the present invention, it is possible to obtain a dynamic damper effect over the entire rotation speed range.
第１図は本発明のダイナミックダンパの一部を断面で示
す部分断面図、
第２図はその外観を示す斜視図、
第３図はそのインタリングの斜視図、
第４図は第３図のＩＶ−ｒＶ断面図、
第５図〜第７図は各種特性図、
第８図および第９図は本発明ダンパの説明図、第１０図
は本発明ダンパの特性図、
第１１図および第１２図は従来のダンパの説明図、第１
３図は従来のダンパの特性図である。
１・・・被制振体 ２・・・弾性部材３・・・
質量体 ４・・・空洞５・・・インクリング
６・・・電極７・・・電気レオロジー流体
８・・・電圧発生装置 ９・・・コントローラ１０
・・・エンジン回転数検出装置
第１図
第２図
第３図
５（イ／ゲリ７ゲ）
第４図
第５図
第６図
ｖ４荷電圧
第７図
負荷電圧
第８図
第９図Fig. 1 is a partial sectional view showing a part of the dynamic damper of the present invention, Fig. 2 is a perspective view showing its appearance, Fig. 3 is a perspective view of its interring, and Fig. 4 is the same as Fig. 3. IV-rV sectional view, Figures 5 to 7 are various characteristic diagrams, Figures 8 and 9 are explanatory diagrams of the damper of the present invention, Figure 10 is characteristic diagrams of the damper of the present invention, Figures 11 and 12 The figure is an explanatory diagram of a conventional damper.
FIG. 3 is a characteristic diagram of a conventional damper. 1... Vibration controlled body 2... Elastic member 3...
Mass body 4...Cavity 5...Ink ring 6...Electrode 7...Electrorheological fluid 8...Voltage generator 9...Controller 10
...Engine speed detection device Fig. 1 Fig. 2 Fig. 3 Fig. 5 (I/Geri 7ge) Fig. 4 Fig. 5 Fig. 6 v4 Load voltage Fig. 7 Load voltage Fig. 8 Fig. 9
Claims (1)
ダイナミックダンパにおいて、前記弾性部材内に空洞を
設け、その空洞内に負荷電圧に応じて粘度が変化する電
気レオロジー流体を充填し、その流体に電圧を印加でき
る電極を設け、この電極に加振周波数に応じて変化する
電圧を印加するようにしたことを特徴とするダイナミッ
クダンパ。1. In a dynamic damper in which a predetermined mass body is provided on the damped body via an elastic member, a cavity is provided in the elastic member, and the cavity is filled with an electrorheological fluid whose viscosity changes depending on the load voltage. A dynamic damper characterized in that an electrode capable of applying a voltage to the fluid is provided, and a voltage that changes depending on the excitation frequency is applied to the electrode.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32408489A JPH03186631A (en) | 1989-12-15 | 1989-12-15 | Dynamic damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32408489A JPH03186631A (en) | 1989-12-15 | 1989-12-15 | Dynamic damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH03186631A true JPH03186631A (en) | 1991-08-14 |
Family
ID=18161973
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP32408489A Pending JPH03186631A (en) | 1989-12-15 | 1989-12-15 | Dynamic damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH03186631A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0886079A3 (en) * | 1997-06-18 | 2003-01-08 | Deutsches Zentrum für Luft- und Raumfahrt e.V | Method and apparatus for vibration damping using a dynamic mass |
| KR20030020612A (en) * | 2001-09-04 | 2003-03-10 | 현대자동차주식회사 | lower arm bush of vehicle |
| US8152145B2 (en) * | 2009-04-29 | 2012-04-10 | Honeywell International Inc. | Isoelastic magneto-rheological elastomer isolator |
| JP2014109300A (en) * | 2012-11-30 | 2014-06-12 | Railway Technical Research Institute | Vibration control device and railway car |
-
1989
- 1989-12-15 JP JP32408489A patent/JPH03186631A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0886079A3 (en) * | 1997-06-18 | 2003-01-08 | Deutsches Zentrum für Luft- und Raumfahrt e.V | Method and apparatus for vibration damping using a dynamic mass |
| KR20030020612A (en) * | 2001-09-04 | 2003-03-10 | 현대자동차주식회사 | lower arm bush of vehicle |
| US8152145B2 (en) * | 2009-04-29 | 2012-04-10 | Honeywell International Inc. | Isoelastic magneto-rheological elastomer isolator |
| JP2014109300A (en) * | 2012-11-30 | 2014-06-12 | Railway Technical Research Institute | Vibration control device and railway car |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4893800A (en) | Electronically controlled vibration damper for mounting automotive internal combustion engines and the like | |
| US4913409A (en) | Electronically controllable vibration damper for use with automotive engine or the like | |
| Flower | Understanding hydraulic mounts for improved vehicle noise, vibration and ride qualities | |
| US6439556B1 (en) | Active decoupler hydraulic mount | |
| US5044813A (en) | Bush type hydraulically damped engine or transmission mount | |
| EP0412674A1 (en) | Mount with adjustable length inertia track | |
| JPS60104828A (en) | Two chamber type engine supporter having hydraulic damping performance | |
| US4873887A (en) | Torsion-vibration damper | |
| US4641808A (en) | Dynamic vibration attenuator utilizing inertial fluid | |
| JPH0718470B2 (en) | Controlled vibration control device | |
| JP2860701B2 (en) | Liquid filled vibration isolator | |
| JPH03186631A (en) | Dynamic damper | |
| US5145024A (en) | Engine suspension system | |
| EP0174184A2 (en) | Vibration isolating apparatus | |
| US5028039A (en) | Vibration damping device | |
| JPS591828A (en) | Liquid-enclosing vibration-proof device | |
| JP3039105B2 (en) | Cylindrical anti-vibration mount, power plant supporting device using the cylindrical anti-vibration mount, and method of controlling cylindrical anti-vibration mount in power plant supporting device | |
| JP2002055117A (en) | Capacitance type acceleration sensor | |
| JPH07243482A (en) | Damper | |
| Tagata | Parametric oscillations of a non-linear string | |
| EP0926385A1 (en) | A vibration absorbing system | |
| JPH0925988A (en) | Vibration control device | |
| GB2314399A (en) | A device for damping the transmission of vibration | |
| JPH01188737A (en) | Vibration damper | |
| JPH0821478A (en) | Vibration dapming device |