JPH07233851A - Control type vibration-proof device - Google Patents
Control type vibration-proof deviceInfo
- Publication number
- JPH07233851A JPH07233851A JP2387194A JP2387194A JPH07233851A JP H07233851 A JPH07233851 A JP H07233851A JP 2387194 A JP2387194 A JP 2387194A JP 2387194 A JP2387194 A JP 2387194A JP H07233851 A JPH07233851 A JP H07233851A
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- piston member
- actuator
- cylinder
- vibration
- 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
Landscapes
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
【0001】[0001]
【産業上の利用分野】本発明は、液室内に振動板を配設
し、この振動板をアクチュエータにより強制加振するこ
とによって液室の内圧上昇を抑制制御するようにした防
振装置に係り、詳しくは、上記振動板とアクチュエータ
との間にアクチュエータによる加振作動力もしくは加振
作動ストロークなどの作動特性を変換する作動特性変換
手段を介装した制御式防振装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration isolator in which a vibration plate is arranged in a liquid chamber, and the vibration plate is forcibly excited by an actuator to suppress and control an increase in internal pressure of the liquid chamber. More specifically, the present invention relates to a control type vibration damping device in which an operating characteristic converting means for converting an operating characteristic such as an oscillating operating force or an oscillating operating stroke by the actuator is interposed between the diaphragm and the actuator.
【0002】[0002]
【従来の技術】従来より、この種の防振装置として、振
動板を加振させるアクチュエータとして圧電素子を用
い、この圧電素子の伸縮量を拡大させる拡大機構を設け
たものが知られている(例えば、実開平5−50200
号公報参照)。このものでは、上記圧電素子の電圧印
加,遮断に伴う伸縮量、つまり、振動板の加振ストロー
クが極めて小さいために、大径筒部と小径筒部とからな
るシリンダの大径筒部に圧電素子に固定したピストンを
内嵌させ、小径筒部に内嵌させた弾性キャップの先端を
振動板に当接させることにより、上記圧電素子の伸縮量
を拡大させて上記振動板を加振させるようにしている。2. Description of the Related Art Conventionally, as this type of vibration isolator, there has been known one in which a piezoelectric element is used as an actuator for vibrating a diaphragm, and an expansion mechanism for expanding the expansion / contraction amount of the piezoelectric element is provided ( For example, the actual Kaihei 5-50200
(See the official gazette). In this structure, the amount of expansion and contraction due to the voltage application and interruption of the piezoelectric element, that is, the vibration stroke of the diaphragm is extremely small. The piston fixed to the element is fitted inside, and the tip of the elastic cap fitted inside the small-diameter cylindrical portion is brought into contact with the vibration plate, thereby expanding the expansion and contraction amount of the piezoelectric element and vibrating the vibration plate. I have to.
【0003】[0003]
【発明が解決しようとする課題】ところで、上記従来の
防振装置において、圧電素子の伸縮量を有効に拡大させ
るには、上記シリンダ内の作動油の容積が変化しないよ
うにする必要がある。このため、上記のシリンダ内に作
動油を注入しピストンおよび弾性キャップを内嵌させる
作業においては、上記作動油の中に気泡が残留しないよ
うに注意して作業を行う必要がある。In the conventional vibration isolator described above, in order to effectively expand the expansion / contraction amount of the piezoelectric element, it is necessary to keep the volume of the hydraulic oil in the cylinder unchanged. Therefore, in the work of injecting the working oil into the cylinder and fitting the piston and the elastic cap therein, it is necessary to perform the work carefully so that no bubbles remain in the working oil.
【0004】しかし、上記の作業においては、防振装置
自体が比較的小さいものであり、その内部に装着するシ
リンダはさらに小さく、この組付け作業には困難を伴う
ため、上記シリンダの内部に気泡が残留するおそれがあ
る。そして、作動油中に気泡が残留すると、圧電素子の
伸長によりピストンが作動油を加圧しても、残留気泡が
圧縮されて作動油全体の体積が変化してしまい、上記圧
電素子の伸長量が有効に増幅されず、大径筒部のピスト
ンの加圧面と小径筒部の弾性キャップの受圧面との面積
比に対応する伸縮量の増幅を得ることができなくなる。
特に、アクチュエータとして圧電素子を用いた場合、そ
の伸縮量が極めて小さいことから、上記残留した気泡が
たとえ微量(例えばマイクロメータ単位の大きさ)であ
ったとしても、その気泡の圧縮による体積変化が振動板
の加振ストロークに与える影響度合は極めて大きくな
り、このため、上記加振ストロークが圧電素子自体の伸
縮量に近いものとなってしまうという加振特性の大幅な
低下を招き、所定の加振特性で振動板を加振することが
できなくなるという問題がある。However, in the above work, the vibration isolator itself is relatively small, and the cylinder to be mounted therein is even smaller, and this assembling work is difficult. May remain. When bubbles remain in the hydraulic oil, even if the piston pressurizes the hydraulic oil due to the expansion of the piezoelectric element, the residual bubbles are compressed and the volume of the entire hydraulic oil changes, and the expansion amount of the piezoelectric element is reduced. It is not amplified effectively, and it becomes impossible to obtain the expansion and contraction amount amplification corresponding to the area ratio between the pressing surface of the piston of the large-diameter tubular portion and the pressure-receiving surface of the elastic cap of the small-diameter tubular portion.
In particular, when a piezoelectric element is used as an actuator, its expansion and contraction amount is extremely small, so that even if the remaining bubbles are very small (for example, in the size of a micrometer), the volume change due to the compression of the bubbles does not occur. The degree of influence of the vibration plate on the vibration stroke becomes extremely large, and therefore, the vibration stroke becomes close to the amount of expansion and contraction of the piezoelectric element itself, which greatly deteriorates the vibration characteristic and causes a predetermined vibration. There is a problem that the vibration plate cannot be excited due to the vibration characteristic.
【0005】本発明は、このような事情に鑑みてなされ
たものであり、その目的とするところは、アクチュエー
タによる振動板の加振作動機構内に、その製造時に万一
気泡が残留したとしても、加振特性の低下を確実に防止
した状態で振動板の加振による効果を得ることにある。The present invention has been made in view of such circumstances, and it is an object of the present invention that even if bubbles are left in the vibration actuation mechanism of the diaphragm by the actuator at the time of its manufacture, This is to obtain the effect of vibrating the diaphragm while surely preventing the deterioration of the vibrating characteristics.
【0006】[0006]
【課題を解決するための手段】上記目的を達成するため
に、請求項1記載の発明は、振動入力方向に互いに離し
て配置された一対の取付部材と、この一対の取付部材を
互いに連結する弾性支承体と、この弾性支承体により画
成されてし非圧縮性の液体が封入された液室と、この液
室の上記弾性支承体の側を仕切るように配置され上記弾
性支承体の側の液室の容積を拡縮する方向に変位可能に
支持された振動板と、上記振動板を加振作動させるアク
チュエータとを備え、このアクチュエータの作動を制御
することにより上記弾性支承体の側の液室の内圧を制御
するようにしたものを前提とする。このものにおいて、
上記振動板とアクチュエータとの間に、アクチュエータ
による振動板の加振作動の特性を変換する作動特性変換
手段を介装し、この作動特性変換手段を、内部に上記液
体と同じ液体が封入されたシリンダ室を有するシリンダ
と、このシリンダに進退可能に配設された駆動側および
従動側の一対のピストン部材と、上記シリンダ室内の気
泡を上記液室側に排出する気泡抜孔とを備えたもので構
成する。そして、上記駆動側ピストン部材の基端部を上
記アクチュエータにより加振作動されるようアクチュエ
ータに連結し、先端部の加圧面を上記シリンダ室の流体
に臨むよう上記シリンダに配置する一方、上記従動側ピ
ストン部材の基端部を上記振動板に取付け、先端部の受
圧面をシリンダ室の流体を介して駆動側ピストン部材か
らの加振作動力を受けるように配置する。また、上記気
泡抜孔を、上記駆動側ピストン部材および従動側ピスト
ン部材の内の上方に位置するピストン部材を貫通して上
記シリンダ室と液室とを互いに連通させるよう形成し、
かつ、その気泡抜孔を介した液柱の共振周波数を、上記
アクチュエータを作動させるものとして予め設定された
入力振動の周波数域よりも十分に低くなるように設定す
る構成とするものである。In order to achieve the above object, the invention according to claim 1 connects a pair of mounting members which are arranged apart from each other in the vibration input direction and the pair of mounting members. An elastic bearing, a liquid chamber defined by the elastic bearing and containing an incompressible liquid, and a side of the elastic bearing arranged so as to partition the side of the elastic bearing of the liquid chamber. A vibrating plate supported so as to be displaceable in a direction in which the volume of the liquid chamber is expanded and contracted, and an actuator for vibrating the vibrating plate, and the liquid on the elastic bearing side is controlled by controlling the operation of the actuator. It is assumed that the internal pressure of the chamber is controlled. In this one,
An operating characteristic converting means for converting the characteristic of the vibration operation of the diaphragm by the actuator is interposed between the diaphragm and the actuator, and the operating characteristic converting means is filled with the same liquid as the liquid. A cylinder having a cylinder chamber, a pair of driving-side and driven-side piston members that are arranged to be able to move forward and backward in the cylinder, and a bubble vent for discharging bubbles in the cylinder chamber to the liquid chamber side. Constitute. The base end of the drive-side piston member is connected to the actuator so that it is vibrated by the actuator, and the pressurizing surface of the tip end is arranged in the cylinder so as to face the fluid in the cylinder chamber while the driven-side side is arranged. The base end portion of the piston member is attached to the vibration plate, and the pressure receiving surface of the tip end portion is arranged so as to receive the vibration actuating force from the drive side piston member via the fluid in the cylinder chamber. Further, the bubble vent hole is formed to penetrate the piston member located above in the drive side piston member and the driven side piston member to communicate the cylinder chamber and the liquid chamber with each other,
Further, the resonance frequency of the liquid column passing through the bubble vent is set to be sufficiently lower than the frequency range of the input vibration that is preset for operating the actuator.
【0007】請求項2記載の発明は、請求項1記載の発
明において、弾性支承体側の液室を上方に位置付け、気
泡を収容するつぼ部を、上記液室の頂部に臨んで下向き
に開口するよう上記弾性支承体に形成する構成とするも
のである。According to a second aspect of the present invention, in the first aspect of the invention, the liquid chamber on the side of the elastic support is positioned above, and the crucible portion for storing bubbles is opened downward facing the top of the liquid chamber. As described above, the elastic support is formed on the elastic support.
【0008】請求項3記載の発明は、請求項2記載の発
明において、液室を、弾性支承体の側の受圧室と、少な
くとも一部が弾性薄膜部材により画成されて拡縮可能な
平衡室とに仕切り、この受圧室と平衡室とを連通するオ
リフィスを備える。そして、つぼ部に対して、上記オリ
フィスを介した液柱の設定共振周波数よりも十分に低い
共振周波数を設定する構成とするものである。According to a third aspect of the present invention, in the second aspect of the invention, the liquid chamber is capable of expanding and contracting with the pressure receiving chamber on the elastic bearing side and at least part of which is defined by an elastic thin film member. And an orifice that connects the pressure receiving chamber and the equilibrium chamber. Then, a resonance frequency that is sufficiently lower than the set resonance frequency of the liquid column via the orifice is set for the pot.
【0009】請求項4記載の発明は、請求項1記載の発
明において、駆動側ピストン部材の加圧面の面積を従動
側ピストン部材の受圧面の面積より小さく設定して、作
動特性変換手段を、従動側ピストン部材の加振作動力特
性を増幅させる構成とするものである。According to a fourth aspect of the present invention, in the first aspect of the invention, the area of the pressing surface of the driving side piston member is set smaller than the area of the pressure receiving surface of the driven side piston member, and the operating characteristic converting means is The configuration is such that the vibration actuation force characteristic of the driven side piston member is amplified.
【0010】また、請求項5記載の発明は、請求項1記
載の発明において、駆動側ピストン部材の加圧面の面積
を従動側ピストン部材の受圧面の面積より大きく設定し
て、作動特性変換手段を、従動側ピストン部材の加振作
動ストローク特性を増幅させる構成とするものである。According to a fifth aspect of the present invention, in the first aspect of the invention, the area of the pressing surface of the driving side piston member is set to be larger than the area of the pressure receiving surface of the driven side piston member, and the operating characteristic converting means is set. Is configured to amplify the vibration operation stroke characteristic of the driven side piston member.
【0011】さらに、請求項6記載の発明は、請求項1
記載の発明において、アクチュエータとして、電圧の印
加,遮断により伸縮する圧電素子を用いて構成するもの
である。Further, the invention according to claim 6 is the same as claim 1.
In the invention described above, the actuator is configured by using a piezoelectric element that expands and contracts by applying and blocking a voltage.
【0012】[0012]
【作用】上記の構成により、請求項1記載の発明では、
取付部材を介して弾性支承体に振動が入力した場合、こ
の弾性支承体の変形を受けて液室内の液圧が変動しよう
とするが、アクチュエータの作動によりその作動力が作
動特性変換手段を介して伝達されて振動板が強制加振さ
れるため、弾性支承体の側の液室内の容積が強制的に拡
縮されてその液室内の液圧変動の吸収が図られる。この
際、作動特性変換手段において、上記駆動側ピストン部
材の加圧面の面積と、従動側ピストン部材の受圧面の面
積とが互いに異なる大きさに設定されているため、アク
チュエータによる駆動側ピストン部材の進退作動特性が
上記両面積の比に応じて変換されて、上記駆動側ピスト
ン部材とは異なる作動力特性もしくは作動ストローク特
性で従動側ピストン部材が進退作動される。With the above construction, in the invention according to claim 1,
When vibration is input to the elastic support through the mounting member, the hydraulic pressure in the liquid chamber tends to fluctuate due to the deformation of the elastic support, but the operating force is changed by the operation of the actuator through the operation characteristic conversion means. Since the vibration plate is forcibly vibrated by being transmitted, the volume in the liquid chamber on the elastic bearing side is forcibly expanded and contracted to absorb fluctuations in the liquid pressure in the liquid chamber. At this time, in the operation characteristic conversion means, the area of the pressure-applying surface of the drive-side piston member and the area of the pressure-receiving surface of the driven-side piston member are set to different sizes from each other. The advancing / retreating operation characteristic is converted according to the ratio of the both areas, and the driven-side piston member is advanced / retreating with an operating force characteristic or an operating stroke characteristic different from that of the driving-side piston member.
【0013】一方、製造時に上記シリンダ室に混入した
空気がその内部の液体中に気泡として残留した場合、気
泡抜孔がシリンダ室の上位の側のピストン部材に形成さ
れているため、その気泡が上記気泡抜孔を通して液室側
に排出される。この結果、上記駆動側ピストン部材の進
退作動によるシリンダ室内の液体がシリンダ室の容積の
まま一定に保たれ、確実に所定の作動特性に維持され
る。しかも、この気泡抜孔を介した液柱共振の共振周波
数が上記アクチュエータを作動させる入力振動の設定周
波数域よりも十分に低いものに設定されているため、上
記アクチュエータを作動させる周波数領域では上記気泡
抜孔が目詰まり状態となってロックする。このため、上
記各ピストン部材の加圧面と受圧面との両面積比に基く
作動特性の変換が確実に所定のものとされる。On the other hand, when the air mixed in the cylinder chamber at the time of manufacture remains as bubbles in the liquid therein, the bubbles are formed because the bubble vent hole is formed in the piston member on the upper side of the cylinder chamber. It is discharged to the liquid chamber side through the bubble vent. As a result, the liquid in the cylinder chamber due to the forward / backward movement of the drive side piston member is kept constant as the volume of the cylinder chamber, and the predetermined operating characteristics are reliably maintained. Moreover, since the resonance frequency of the liquid column resonance through the bubble vent is set to be sufficiently lower than the set frequency range of the input vibration for operating the actuator, the bubble vent is used in the frequency range for operating the actuator. Is locked and locks. For this reason, the conversion of the operating characteristics based on the area ratio of the pressure-applying surface and the pressure-receiving surface of each piston member is surely made to be predetermined.
【0014】請求項2記載の発明では、上記請求項1記
載の発明による作用に加えて、シリンダ室の上位のピス
トン部材に形成された気泡抜孔を通して排出された気泡
が弾性支承体側の液室を上昇し、その頂部に開口するつ
ぼ部に収容される。この結果、液室内の液体中から上記
気泡の存在の排除が可能となる。According to the second aspect of the present invention, in addition to the action of the first aspect of the present invention, the bubbles discharged through the bubble removing hole formed in the upper piston member of the cylinder chamber cause the liquid chamber on the side of the elastic bearing to be discharged. It rises and is housed in a crucible that opens to the top. As a result, it becomes possible to eliminate the presence of the bubbles from the liquid in the liquid chamber.
【0015】請求項3記載の発明では、上記請求項2記
載の発明による作用に加えて、つぼ部に対して、受圧室
と平衡室とを互いに連通するオリフィスの設定共振周波
数よりも十分に低い共振周波数が設定されているため、
このオリフィスの液柱共振により入力振動の減衰を図る
周波数域では上記気泡を収容したつぼ部がロックする。
この結果、その周波数域の振動が入力した際は、上記つ
ぼ部内の気泡が液室内の液体に混入することが防止され
て、この混入に伴うオリフィスの減衰特性の悪化が確実
に防止される。According to the third aspect of the invention, in addition to the effect of the second aspect of the invention, the resonance frequency is sufficiently lower than the set resonance frequency of the orifice for communicating the pressure receiving chamber and the equilibrium chamber with respect to the pot. Since the resonance frequency is set,
In the frequency range where the vibration of the input vibration is attenuated by the resonance of the liquid column of the orifice, the crucible portion containing the bubbles locks.
As a result, when the vibration in the frequency range is input, the bubbles in the pot are prevented from being mixed with the liquid in the liquid chamber, and the deterioration of the damping characteristic of the orifice due to the mixture is surely prevented.
【0016】請求項4記載の発明では、上記請求項1記
載の発明による作用に加えて、駆動側ピストン部材の加
圧面の面積が、従動側ピストン部材の受圧面の面積より
小さく設定されて作動特性変換手段により従動側ピスト
ン部材がアクチュエータの作動力よりも大きい作動力で
進退作動されるように作動特性が変換される。このよう
な場合においても、製造時に気泡が万一残留しても、そ
の気泡が気泡抜孔により排出され上記残留気泡に伴うシ
リンダ室内の容積変化が防止される結果、作動特性の変
換効率の低下が防止される。According to the invention described in claim 4, in addition to the operation according to the invention described in claim 1, the area of the pressing surface of the driving side piston member is set smaller than the area of the pressure receiving surface of the driven side piston member to operate. The characteristic converting means converts the operating characteristic such that the driven side piston member is moved forward and backward with an operating force larger than the operating force of the actuator. Even in such a case, even if air bubbles remain during manufacturing, the air bubbles are discharged through the air bubble vent holes and the volume change in the cylinder chamber due to the above-mentioned remaining air bubbles is prevented, resulting in a decrease in the conversion efficiency of the operating characteristics. To be prevented.
【0017】また、請求項5記載の発明では、上記請求
項1記載の発明による作用に加えて、駆動側ピストン部
材の加圧面の面積が、従動側ピストン部材の受圧面の面
積より大きく設定されて作動特性変換手段により従動側
ピストン部材がアクチュエータの作動ストロークよりも
大きい作動ストロークで進退作動されるように作動特性
が変換される。このような場合においても、製造時に気
泡が万一残留しても、その気泡が気泡抜孔により排出さ
れ上記残留気泡に伴うシリンダ室内の容積変化が防止さ
れる結果、作動特性の変換効率の低下が防止される。According to the invention of claim 5, in addition to the operation of the invention of claim 1, the area of the pressing surface of the driving side piston member is set larger than the area of the pressure receiving surface of the driven side piston member. The operating characteristic converting means converts the operating characteristic such that the driven side piston member is moved forward and backward with an operating stroke larger than the operating stroke of the actuator. Even in such a case, even if air bubbles remain during manufacturing, the air bubbles are discharged through the air bubble vent holes and the volume change in the cylinder chamber due to the above-mentioned remaining air bubbles is prevented, resulting in a decrease in the conversion efficiency of the operating characteristics. To be prevented.
【0018】さらに、請求項6記載の発明では、上記請
求項1記載の発明による作用に加えて、アクチュエータ
が圧電素子により構成されて、電圧の印加、遮断により
圧電素子が伸縮されて駆動側ピストン部材が加振され
る。この際、上記圧電素子による伸縮量が極めて小さい
ため、シリンダ室に気泡が残留した場合、その残留気泡
量が極めて少ないものであっても、作動特性変換手段に
よる作動ストロークの増大変換作用に大きく影響する。
ところが、上記残留気泡が気泡抜孔によって確実に排出
されるため、アクチュエータとして圧電素子を用いた場
合であっても、振動板を確実に増幅した作動ストローク
によって加振させることが可能となる。Further, in the sixth aspect of the invention, in addition to the operation of the first aspect of the invention, the actuator is composed of a piezoelectric element, and the piezoelectric element is expanded / contracted by applying / cutting off a voltage, so that the driving side piston. The member is vibrated. At this time, since the amount of expansion and contraction due to the piezoelectric element is extremely small, when bubbles remain in the cylinder chamber, even if the amount of remaining bubbles is extremely small, it has a great effect on the increase conversion action of the operation stroke by the operation characteristic conversion means. To do.
However, since the residual bubbles are reliably discharged by the bubble vent holes, even when the piezoelectric element is used as the actuator, it is possible to vibrate the diaphragm with a surely amplified operation stroke.
【0019】[0019]
【実施例】以下、本発明の実施例を図面に基いて説明す
る。Embodiments of the present invention will be described below with reference to the drawings.
【0020】<第1実施例>図1は、本発明の第1実施
例に係る制御式防振装置を示す。同図において、1は筒
軸Xを上下方向に向けた第1支持筒体、2は上記第1支
持筒体1の下端開口側を閉止する有底の第2支持筒体で
あり、両者が一体的に連結されて下側の第1取付部材3
が構成されている。この第2支持筒体2の上端部には筒
軸X方向所定寸法にわたって外周方向に拡径された拡径
部2aが形成されている一方、上記第1取付部材1の下
端部が上記拡径部2aの外周囲を覆うよう拡径された
後、上下方向から挟むようにかしめ部1aが形成されて
両者1,2が互いに一体化されている。そして、上記第
2支持筒体2が振動受部である例えば車体のブラケット
に内嵌されて上記拡径部2aおよびかしめ部1aで位置
固定されるようになっている。<First Embodiment> FIG. 1 shows a control type vibration damping device according to a first embodiment of the present invention. In the figure, 1 is a first support cylinder with the cylinder axis X directed in the vertical direction, and 2 is a bottomed second support cylinder that closes the lower end opening side of the first support cylinder 1, both of which are Lower first mounting member 3 connected integrally
Is configured. An enlarged diameter portion 2a is formed on the upper end portion of the second support cylinder body 2 and is enlarged in the outer peripheral direction over a predetermined dimension in the cylinder axis X direction, while the lower end portion of the first mounting member 1 is expanded. After the diameter is enlarged so as to cover the outer periphery of the portion 2a, the caulking portion 1a is formed so as to sandwich the portion 2a from above and below, and the both 1 and 2 are integrated with each other. The second support cylinder 2 is fitted in a vibration receiving portion, for example, a bracket of a vehicle body, and fixed in position by the expanded diameter portion 2a and the caulking portion 1a.
【0021】4は上記第1支持筒体1の上端開口側の位
置であって上記筒軸X上に配置された上側の第2取付部
材であり、この第2取付部材4には上記筒軸Xに沿って
取付ボルト4aが上向きに突出されて振動発生源である
例えばエンジンに連結されるようになっている。5はこ
の第2取付部材4と上記第1取付部材3の第1支持持体
1とを互いに連結する環状の弾性支承体であり、この弾
性支承体5が上記第2取付部材4および第1支持筒体1
と一体加硫成形されて第1取付部材3と第2取付部材4
とを互いに連結している。そして、上記第1取付部材3
に取付けられた弾性薄膜部材としてのゴム薄膜製ダイヤ
フラム6と、上記第1支持筒体1と、上記弾性支承体5
とによって液室7が画成されており、この液室7に非圧
縮性の液体8が封入されている。Reference numeral 4 denotes an upper second mounting member which is located on the upper end opening side of the first supporting cylindrical body 1 and is arranged on the cylindrical axis X. The second mounting member 4 includes the cylindrical shaft. The mounting bolt 4a is projected upward along X and is connected to a vibration generating source such as an engine. Reference numeral 5 denotes an annular elastic bearing body that connects the second mounting member 4 and the first support carrier 1 of the first mounting member 3 to each other. The elastic bearing body 5 is the second mounting member 4 and the first mounting member 3. Support cylinder 1
The first mounting member 3 and the second mounting member 4 are integrally vulcanized and molded.
And are connected to each other. Then, the first mounting member 3
A rubber thin film diaphragm 6 as an elastic thin film member attached to the first supporting cylinder 1, the elastic support 5
Defines a liquid chamber 7, and an incompressible liquid 8 is enclosed in the liquid chamber 7.
【0022】また、9は上記液室7内の上下方向中間位
置において筒軸Xに直交する方向に配設された振動板と
しての仕切体であり、この仕切体9によって上記液室7
が上側の弾性支承体5の変形を受けて拡縮される受圧室
7aと、下側のダイヤフラム6により拡縮される平衡室
7bとに仕切られている。加えて、上記仕切体9の周囲
には上記受圧室7aと平衡室7bとを互いに連通する環
状のオリフィス10が形成されている。そして、上記仕
切体9は、その周囲が環状の弾性支持部材11を介して
上記第1取付部材3の内周面に取付けられており、これ
により、上記仕切体9は上下方向に相対変位可能に弾性
支持されている。Further, 9 is a partition body as a vibrating plate which is arranged in a direction orthogonal to the cylinder axis X at an intermediate position in the liquid chamber 7 in the vertical direction.
Is partitioned into a pressure receiving chamber 7a which is expanded and contracted by the deformation of the upper elastic support body 5 and an equilibrium chamber 7b which is expanded and contracted by the lower diaphragm 6. In addition, an annular orifice 10 that connects the pressure receiving chamber 7a and the equilibrium chamber 7b to each other is formed around the partition body 9. The partition body 9 is attached to the inner peripheral surface of the first mounting member 3 through an elastic support member 11 having an annular circumference, whereby the partition body 9 is relatively displaceable in the vertical direction. It is elastically supported by.
【0023】さらに、12は仕切体9を上下方向に強制
加振するためのアクチュエータであり、このアクチュエ
ータ12は第2支持筒体2の底壁に固定された永久磁石
13と、後述の駆動側ピストン部材17の外周囲に設け
られた電磁コイル14と、上記電磁コイル14への交番
電流の通電の制御を行う図示省略の制御器とを備えてい
る。そして、このアクチュエータ12は、作動特性変換
手段15を介して上記仕切体9を上下方向に加振作動す
るようになっている。Further, 12 is an actuator for forcibly vibrating the partition body 9 in the vertical direction. This actuator 12 includes a permanent magnet 13 fixed to the bottom wall of the second support cylinder 2, and a drive side which will be described later. An electromagnetic coil 14 provided on the outer periphery of the piston member 17 and a controller (not shown) for controlling energization of the alternating current to the electromagnetic coil 14 are provided. The actuator 12 is configured to vibrate the partition body 9 in the vertical direction via the operating characteristic conversion means 15.
【0024】上記作動特性変換手段15は、シリンダ1
6と、先端部(上端部)がこのシリンダ16に上下方向
に進退変位可能に下側から上方に内挿された駆動側ピス
トン部材17と、先端部(下端部)が上記シリンダ16
に上下方向に進退変位可能に上側から下方に内挿されて
基端部(上端部)が上記仕切体9に一体的に連結された
従動側ピストン部材18と、後述の気泡抜孔24とを備
えている。上記駆動側ピストン部材17は小径の円形断
面に形成されて上端の加圧面17aが比較的小さい面積
(A1 )とされている一方、上記従動側ピストン部材1
8は上記駆動側ピストン部材17のそれより所定量大径
の円形断面に形成されて下端の受圧面18aが上記面積
(A1 )より所定量大きい面積(A2 )とされている。
そして、上記駆動側ピストン部材17の基端部(下端
部)側の筒部17bに上記電磁コイル14が設けられ
て、この駆動側ピストン部材17が上下方向に進退する
ことにより、その進退作動力が上記シリンダ16のシリ
ンダ室16a内に封入された非圧縮性の作動用液体8を
介して上記従動側ピストン部材18に伝達されるように
なっている。つまり、上記アクチュエータ12による駆
動側ピストン部材17の上下方向作動力をF1 とし、上
記作動用液体8を介して従動側ピストン部材18が受け
る作動力をF2 とすると、このF2 は上記面積A1 ,A
2 に基いて、 F2 =(A2 /A1 )・F1 となり、F1 の(A2 /A1 )倍に作動力特性が増幅変
換されるようになっている。The operating characteristic converting means 15 is the cylinder 1
6, a drive-side piston member 17 having a tip portion (upper end portion) inserted in the cylinder 16 upward and downward so as to be able to move forward and backward, and a tip portion (lower end portion) described above.
A driven-side piston member 18 having a base end portion (upper end portion) integrally connected to the partition body 9 such that the driven piston member 18 is inserted downward from above so as to be able to move forward and backward, and a bubble vent hole 24 described later. ing. The driving-side piston member 17 is formed in a circular cross section with a small diameter so that the pressing surface 17a at the upper end has a relatively small area (A1), while the driven-side piston member 1
8 is formed in a circular cross section having a diameter larger than that of the drive side piston member 17 by a predetermined amount, and the pressure receiving surface 18a at the lower end has an area (A2) larger than the area (A1) by a predetermined amount.
The electromagnetic coil 14 is provided in the tubular portion 17b on the base end (lower end) side of the drive-side piston member 17, and the drive-side piston member 17 moves back and forth to move forward and backward. Is transmitted to the driven side piston member 18 via the incompressible working liquid 8 sealed in the cylinder chamber 16a of the cylinder 16. That is, when the vertical actuating force of the drive side piston member 17 by the actuator 12 is F1 and the actuating force received by the driven side piston member 18 through the actuating liquid 8 is F2, this F2 is the area A1, A
Based on 2, F2 = (A2 / A1) .F1 and the operating force characteristics are amplified and converted to (A2 / A1) times that of F1.
【0025】以下、上記の全体構成をより詳細に説明す
ると、上記第1支持筒体1の下端側のかしめ部1aに至
る内周面にはゴム薄層5aが上記弾性支承体5と一体に
加硫接着されている。そして、上記かしめ部1aのゴム
薄層5aと上記第2支持筒体2の拡径部2a内面との間
に、上記弾性支持部材11の後述の外周側取付リング1
1bのフランジ部と、上記シリンダ16の外周部と、上
記ダイヤフラム6の外周部とが互いに重ね合わされた状
態で挟み込まれており、これにより、上記仕切体9,シ
リンダ16およびダイヤフラム6の第1取付部材3に対
する取付けが行われている。The overall structure will be described in more detail below. A rubber thin layer 5a is integrally formed with the elastic bearing member 5 on the inner peripheral surface of the lower end side of the first supporting cylinder 1 which extends to the caulking portion 1a. It is vulcanized and bonded. Then, between the rubber thin layer 5a of the caulked portion 1a and the inner surface of the expanded diameter portion 2a of the second support cylinder 2, the outer peripheral side attachment ring 1 of the elastic support member 11 described later is formed.
The flange portion 1b, the outer peripheral portion of the cylinder 16 and the outer peripheral portion of the diaphragm 6 are sandwiched in a state of being overlapped with each other, whereby the partition 9, the cylinder 16 and the diaphragm 6 are first mounted. Attachment to the member 3 is performed.
【0026】上記仕切体9は、下方に開口した第1有底
筒部材9aと、上方に開口して上端の周縁が外周方向に
張り出した後、下方に折り返された第2有底筒部材9b
とからなり、この第2有底筒部材9bが上記第1有底筒
部材9aの内面に下側から内嵌状態で重合されて一体化
されている。そして、この第2有底筒部材9bの上端外
周囲と上記第1有底筒部材9aの上端内周囲との間に形
成された環状の通路によって上記オリフィス10が構成
されており、このオリフィス10は周方向一側の開口1
0aで上記受圧室7aに連通する一方、他側の開口10
bで上記平衡室7bに連通している。また、上記第2有
底筒部材9bの中央部は筒軸X上を下方に突出して上記
シリンダ16に内嵌されており、この第2有底筒部材9
bの中央部によって上記従動側ピストン部材18が構成
されている。The partition body 9 has a first bottomed tubular member 9a that opens downward, and a second bottomed tubular member 9b that opens upward and the peripheral edge of the upper end projects outward, and then folds back downward.
The second bottomed tubular member 9b is integrated with the inner surface of the first bottomed tubular member 9a from the lower side in an internally fitted state. The orifice 10 is constituted by an annular passage formed between the outer periphery of the upper end of the second bottomed tubular member 9b and the inner periphery of the upper end of the first bottomed tubular member 9a. Is the opening 1 on one side in the circumferential direction
0a communicates with the pressure receiving chamber 7a, while opening 10 on the other side
b communicates with the equilibrium chamber 7b. Further, the central portion of the second bottomed tubular member 9b is fitted into the cylinder 16 so as to project downward on the tubular axis X, and the second bottomed tubular member 9b.
The driven side piston member 18 is constituted by the central portion of b.
【0027】一方、上記弾性支持部材11は内外周の各
側に配置された一対の取付リング11a,11bと、こ
の一対の取付リング11a,11bと一体に加硫接着さ
れて両取付リング11a,11bを互いに連結する環状
のゴム弾性体11cとから構成されている。そして、内
周側取付リング11aの内周面に上記第1有底筒部材9
aの外周面が圧入される一方、上記外周側取付リング1
1bのフランジ部が上記のごとく第1取付部材3に取付
けられることにより、上記仕切体9が第1取付部材3に
対して上下方向に変位可能に弾性支持されている。On the other hand, the elastic support member 11 has a pair of mounting rings 11a, 11b arranged on each side of the inner and outer circumferences, and both mounting rings 11a, 11b are integrally vulcanized and bonded together. It is composed of an annular rubber elastic body 11c that connects 11b to each other. The first bottomed tubular member 9 is formed on the inner peripheral surface of the inner peripheral side mounting ring 11a.
While the outer peripheral surface of a is press-fitted, the outer peripheral side mounting ring 1
By attaching the flange portion 1b to the first mounting member 3 as described above, the partition body 9 is elastically supported so as to be vertically displaceable with respect to the first mounting member 3.
【0028】上記シリンダ16は、上下方向に互いに重
合されて一体化された一対の板状部材19,20により
形成されており、これら一体化された両板状体19,2
0の外周部が上記の如く第1取付部材3に固定されてい
る。上記の内、下側板状体19の中央部には筒軸Xに沿
って下方に延びる小径筒部19aが一体形成されてお
り、この小径筒部19aが上記ダイヤフラム6を貫通し
て液室8外の第2支持筒体2の内周面により区画された
空間21内に突出されている。そして、この小径筒部1
9aの内周面に上記駆動側ピストン部材17の上端部の
外周面がゴム弾性部材22を介して液密に内嵌されて上
記駆動側ピストン部材17が上下方向に進退変位可能に
支持されている。The cylinder 16 is formed by a pair of plate-like members 19 and 20 which are vertically overlapped with each other and integrated with each other, and these plate-like members 19 and 2 are integrated with each other.
The outer peripheral portion of 0 is fixed to the first mounting member 3 as described above. Of the above, a small-diameter cylinder portion 19a extending downward along the cylinder axis X is integrally formed in the central portion of the lower plate-like body 19, and the small-diameter cylinder portion 19a penetrates the diaphragm 6 and the liquid chamber 8 It projects into the space 21 defined by the inner peripheral surface of the outer second support cylinder 2. And this small diameter cylinder part 1
The outer peripheral surface of the upper end portion of the drive-side piston member 17 is liquid-tightly fitted into the inner peripheral surface of 9a through the rubber elastic member 22 so that the drive-side piston member 17 is supported so as to be able to move forward and backward in the vertical direction. There is.
【0029】一方、上記上側板状体20の中央部には筒
軸Xに沿って上方に延びる大径筒部20aが一体形成さ
れており、この大径筒部20aの内周面に上記従動側ピ
ストン部材18の下端部の外周面が有底筒状のゴム弾性
部材23を介して液密に内嵌されて上記従動側ピストン
部材18が上下方向に進退変位可能に支持されている。
そして、この従動側ピストン部材18の受圧面18a
と、上記大径筒部20aと、上記駆動側ピストン部材1
7の加圧面17aとによって密閉されて上記シリンダ室
16aが画成されている。On the other hand, a large-diameter cylindrical portion 20a extending upward along the cylindrical axis X is integrally formed in the central portion of the upper plate-like body 20, and the driven surface is attached to the inner peripheral surface of the large-diameter cylindrical portion 20a. The outer peripheral surface of the lower end portion of the side piston member 18 is liquid-tightly fitted in via a bottomed tubular rubber elastic member 23 so that the driven side piston member 18 is supported so as to be able to move forward and backward in the vertical direction.
Then, the pressure receiving surface 18a of the driven side piston member 18
And the large-diameter cylindrical portion 20a and the drive-side piston member 1
The cylinder chamber 16a is defined by being closed by the pressure surface 17a of the cylinder 7.
【0030】加えて、上記従動側ピストン部材18の受
圧面18aには所定の微小径の気泡抜孔24が形成され
ており、この気泡抜孔24を通してシリンダ室16a内
に残留した気泡が受圧室7aの側に排出されるようにな
っている。そして、この気泡抜孔24の径などの寸法諸
元は上記ゴム弾性体11cおよびゴム弾性部材22,2
3に基く拡張バネと、気泡抜孔24内の液体の質量とで
定まる共振周波数が、アクチュエータ12の作動により
仕切体9を強制加振させる周波数領域よりも十分に低く
なるように設定されている。つまり、上記仕切体9の強
制加振により受圧室7aの内圧制御を行う周波数領域の
振動が入力した時には、上記気泡抜孔24が目詰まり現
象を生じてロックするようになっている。また、上記弾
性支承体5の頂部には、上記受圧室7aの最上部に臨ん
で下向きに開口するつぼ部25が形成されており、この
つぼ部25によって受圧室7aの頂部に上昇して溜まる
気泡を収容するようになっている。そして、このつぼ部
25の内径および長さなどの寸法諸元は、上記オリフィ
ス10の設定共振周波数よりも十分に低い共振周波数と
なるように設定されており、上記オリフィス10の液柱
共振により振動の減衰を行う低周波域の振動入力時には
上記つぼ部25が目詰まり現象を生じてロックするよう
になっている。In addition, the pressure receiving surface 18a of the driven side piston member 18 is provided with a bubble vent hole 24 having a predetermined small diameter, and the bubbles remaining in the cylinder chamber 16a through the bubble vent hole 24 are stored in the pressure receiving chamber 7a. It is designed to be discharged to the side. Further, the dimensions such as the diameter of the bubble vent hole 24 are determined by the rubber elastic body 11c and the rubber elastic members 22, 2 described above.
The resonance frequency defined by the expansion spring based on 3 and the mass of the liquid in the bubble vent hole 24 is set to be sufficiently lower than the frequency range in which the partition body 9 is forcibly excited by the operation of the actuator 12. That is, when the vibration in the frequency region for controlling the internal pressure of the pressure receiving chamber 7a is input by the forced vibration of the partition body 9, the bubble vent hole 24 is locked due to a clogging phenomenon. Further, a crucible portion 25 is formed at the top of the elastic bearing member 5 so as to face the uppermost portion of the pressure receiving chamber 7a and opens downward. The crucible portion 25 rises and accumulates at the top of the pressure receiving chamber 7a. It is designed to contain air bubbles. The dimensional specifications such as the inner diameter and the length of the pot 25 are set so that the resonance frequency is sufficiently lower than the set resonance frequency of the orifice 10, and the liquid column resonance of the orifice 10 causes vibration. At the time of inputting vibration in the low frequency range for damping, the pot portion 25 causes a clogging phenomenon and locks.
【0031】また、上記アクチュエータ12において、
電磁コイル14には第2支持筒体2を貫通して配設され
た図示省略のラインが接続され、このラインを通して通
電されるようになっている。一方、上記永久磁石13の
上下端の両極にはそれぞれヨーク金具26,27が連結
され、これら両ヨーク金具26,27が上記電磁コイル
14を筒軸Xに直交する方向から所定の隙間を介して挟
むように配置されている。In the actuator 12,
The electromagnetic coil 14 is connected to a line (not shown) arranged so as to pass through the second support cylindrical body 2 and is energized through this line. On the other hand, yoke fittings 26 and 27 are connected to the upper and lower poles of the permanent magnet 13, respectively, and these yoke fittings 26 and 27 interpose the electromagnetic coil 14 in a direction perpendicular to the cylinder axis X via a predetermined gap. It is arranged so as to sandwich it.
【0032】なお、図中28は上記一対の板状体19,
20の外周部を上下に貫通する1以上のかなり大きめの
連通孔であり、この連通孔28によって平衡室7b内の
上記両板状体19,20より上側の部分とダイヤフラム
6側である下側部分との間で液体8の自由な流動が行わ
れるようになっている。In the figure, 28 is the pair of plate-like members 19,
One or more rather large communicating holes vertically penetrating the outer peripheral portion of 20. By means of this communicating hole 28, the portion above the plate-like members 19 and 20 in the equilibrium chamber 7b and the lower side which is the diaphragm 6 side. A free flow of the liquid 8 is made between the portions.
【0033】次に、上記構成の第1実施例による作用、
効果について説明する。Next, the operation of the first embodiment having the above-mentioned structure,
The effect will be described.
【0034】第2取付部材4側から低周波域の振動が上
下方向に弾性支承体5に入力すると、この弾性支承体5
が上下方向に撓められ受圧室7a内の液体8がオリフィ
ス10を通して平衡室7bとの間で流動する。そして、
この液体8の流動により、上記受圧室7aと平衡室7b
との間でのオリフィス10を介した液柱共振が生じ、こ
の液柱共振により上記振動の減衰が図られる。When vibration in the low frequency range is input from the second mounting member 4 side in the vertical direction to the elastic support body 5, this elastic support body 5
Is bent in the vertical direction, and the liquid 8 in the pressure receiving chamber 7a flows through the orifice 10 to the equilibrium chamber 7b. And
Due to the flow of the liquid 8, the pressure receiving chamber 7a and the equilibrium chamber 7b are
A liquid column resonance is generated between the nozzles 1 and 2 via the orifice 10, and the liquid column resonance attenuates the vibration.
【0035】そして、入力振動がより高周波側のものと
なって、上記オリフィス10を通しての液体8の流動が
実質的に生じない、いわゆるロック状態となる場合で
も、上記振動の入力方向に応じて電磁コイル14に通電
してアクチュエータ12を作動することにより、仕切体
9を上下方向に強制加振することができ、受圧室7a内
の液圧変動の吸収を図ることができる。すなわち、振動
入力を受けた第2取付部材4の変位方向と同位相側に上
記仕切体9を加振することにより受圧室7a内の液圧の
急増を抑制することができ、これにより、第1取付部材
3側への伝達率の低減化、動ばね定数の低減化を図るこ
とができる。Even when the input vibration is on the higher frequency side and a so-called locked state in which the flow of the liquid 8 through the orifice 10 does not substantially occur, the electromagnetic wave is generated depending on the input direction of the vibration. By energizing the coil 14 and operating the actuator 12, the partition body 9 can be forcibly excited in the vertical direction, and fluctuations in the hydraulic pressure in the pressure receiving chamber 7a can be absorbed. That is, by vibrating the partition body 9 in the same phase side as the displacement direction of the second mounting member 4 that receives the vibration input, it is possible to suppress a sudden increase in the hydraulic pressure in the pressure receiving chamber 7a. (1) It is possible to reduce the transmissibility to the mounting member 3 side and the dynamic spring constant.
【0036】この強制加振に際し、上記アクチュエータ
12の作動により駆動側ピストン部材17が上下動され
てその加圧面17aがシリンダ室16a内の液体8を加
圧,減圧する。このシリンダ室16aの変化した内圧が
従動側ピストン部材18の受圧面18aに作用して従動
側ピストン部材18が上下動する。この際、上記加圧面
17aの面積(A1 )に対する上記受圧面18aの面積
(A2 )の比率(A2/A1 )で上記駆動側ピストン部
材17の作動力が増幅され、この増幅された作動力で従
動側ピストン部材18が上下方向に加振される。このた
め、アクチュエータ12による作動力の(A2 /A1 )
倍の作動力で仕切体9を加振することができる。このよ
うにアクチュエータ12と仕切体9との間に作動特性変
換手段15を介装させることにより、アクチュエータ1
2が永久磁石13と電磁コイル14との組合わせにより
構成されて比較的弱い加振力しか得られないものであっ
ても、仕切体9を所要の強い加振力で作動させることが
できる一方、仕切体9を同一の加振力で作動させるため
の上記アクチュエータ12の能力や規模、すなわち、永
久磁石13の規模や電磁コイル14への電流値を小さく
することができ、防振装置全体のコンパクト化、作動コ
ストの低減化を図ることができる。なお、この場合、従
動側ピストン部材18の作動ストロークは駆動側のそれ
より小さくなるものの、永久磁石13と電磁コイル14
との組合わせによるアクチュエータ12は、元来、比較
的大きな作動ストロークを有しているため、所要の作動
ストロークを十分に確保することができる。During this forced vibration, the drive side piston member 17 is moved up and down by the operation of the actuator 12, and the pressurizing surface 17a pressurizes and depressurizes the liquid 8 in the cylinder chamber 16a. The changed internal pressure of the cylinder chamber 16a acts on the pressure receiving surface 18a of the driven side piston member 18 to move the driven side piston member 18 up and down. At this time, the operating force of the drive-side piston member 17 is amplified by the ratio (A2 / A1) of the area (A2) of the pressure receiving surface 18a to the area (A1) of the pressing surface 17a. The driven piston member 18 is vertically vibrated. Therefore, the operating force of the actuator 12 (A2 / A1)
The partition body 9 can be vibrated with a double operating force. In this way, by interposing the operating characteristic conversion means 15 between the actuator 12 and the partition body 9, the actuator 1
Even if 2 is a combination of the permanent magnet 13 and the electromagnetic coil 14 and can obtain only a comparatively weak excitation force, the partition 9 can be operated with a required strong excitation force. , The capacity and scale of the actuator 12 for operating the partition body 9 with the same excitation force, that is, the scale of the permanent magnet 13 and the current value to the electromagnetic coil 14 can be reduced, and the vibration damping device as a whole can be reduced. It is possible to make the device compact and reduce the operating cost. In this case, although the working stroke of the driven side piston member 18 is smaller than that on the driving side, the permanent magnet 13 and the electromagnetic coil 14 are
Since the actuator 12 formed by the combination of and has a relatively large operating stroke, it is possible to sufficiently secure the required operating stroke.
【0037】そして、このような作動力特性の増幅変換
が行われる防振装置において、上記シリンダ室16aは
気泡抜孔24を介して受圧室7aと連通されているた
め、例えば防振装置の製造時に気泡がシリンダ室16a
の液体8中に万一残留した場合であっても、その残留し
た気泡が上記気泡抜孔24を通して受圧室7a側に排出
され、この受圧室7a内の液体8中を上昇して頂部に至
り、つぼ部25内に溜められる。これにより、たとえ、
気泡が製造時に残留しても、その残留気泡のシリンダ室
16aおよび/もしくは受圧室7aからの排出および分
離を確実に行うことができる。この結果、上記シリンダ
室16aに残留した気泡により内圧変化が吸収されるこ
とに伴う作動力の特性変換効率の低下を防止することが
できる。しかも、上記気泡抜孔24が上記仕切体9を強
制加振させるような高周波領域ではロックするようにチ
ューニングされているため、作動特性変換手段15によ
る作動力の特性変換作用を確実に得ることができる。加
えて、上記つぼ部25がオリフィス10により減衰され
る低周波領域ではロックするようにチューニングされて
いるため、オリフィス10による低周波領域の振動減衰
機能を害することを確実に防止することができる。In the vibration isolator that performs such amplification and conversion of the operating force characteristic, since the cylinder chamber 16a is communicated with the pressure receiving chamber 7a through the bubble vent hole 24, for example, when the vibration isolator is manufactured. Air bubbles are in the cylinder chamber 16a
Even if it remains in the liquid 8, the remaining bubbles are discharged to the pressure receiving chamber 7a side through the bubble vent hole 24, rise in the liquid 8 in the pressure receiving chamber 7a, and reach the top. It is stored in the pot portion 25. With this, even if
Even if the bubbles remain during manufacturing, it is possible to reliably discharge and separate the residual bubbles from the cylinder chamber 16a and / or the pressure receiving chamber 7a. As a result, it is possible to prevent the efficiency of characteristic conversion of the operating force from being lowered due to the change in the internal pressure being absorbed by the bubbles remaining in the cylinder chamber 16a. Moreover, since the bubble vent hole 24 is tuned so as to be locked in a high frequency region where the partition body 9 is forcibly excited, the characteristic conversion action of the operating force by the operation characteristic conversion means 15 can be reliably obtained. . In addition, since the pot portion 25 is tuned so as to lock in the low frequency region damped by the orifice 10, it is possible to reliably prevent the vibration damping function of the orifice 10 in the low frequency region from being impaired.
【0038】<第2実施例>図2は本発明の第2実施例
に係る制御式防振装置を示し、31は液室7を受圧室7
aと平衡室7bとを仕切るよう筒軸X方向に直交する方
向に配置され弾性支持部材11により筒軸X方向である
上下方向に振動変位可能に弾性支持された振動板として
の仕切体、32はこの仕切体31を上下方向に強制加振
するための圧電素子32aを用いたアクチュエータ、3
3はこのアクチュエータ32と上記仕切体31との間に
介装された作動特性変換手段である。<Second Embodiment> FIG. 2 shows a control type vibration damping device according to a second embodiment of the present invention, in which 31 denotes a liquid chamber 7 and a pressure receiving chamber 7.
A partitioning body as a diaphragm, which is arranged in a direction orthogonal to the cylinder axis X direction so as to partition the a and the equilibrium chamber 7b, and is elastically supported by an elastic support member 11 so as to be capable of vibration displacement in the vertical direction that is the cylinder axis X direction, Is an actuator using a piezoelectric element 32a for forcibly exciting the partition body 31 in the vertical direction,
Reference numeral 3 is an operation characteristic conversion means interposed between the actuator 32 and the partition body 31.
【0039】上記仕切体31は、下方に開口した第1有
底筒部材31aと、同様に下方に開口した第2有底筒部
材31bとからなり、この第2有底筒部材31bが上記
第1有底筒部材31aの内面に下側から内嵌状態で重合
されて一体化されている。そして、この第2有底筒部材
31bの上端外周囲と上記第1有底筒部材31aの上端
内周囲との間に形成された環状の通路によって、受圧室
7aと平衡室7bとを互いに連通するオリフィス10が
構成されている。The partition body 31 is composed of a first bottomed tubular member 31a which is opened downward and a second bottomed tubular member 31b which is similarly opened downward, and the second bottomed tubular member 31b is the first tubular member 31b. 1 The bottomed tubular member 31a is superposed and integrated in an internally fitted state from the lower side. The pressure receiving chamber 7a and the equilibrium chamber 7b are communicated with each other by an annular passage formed between the outer periphery of the upper end of the second bottomed tubular member 31b and the inner periphery of the upper end of the first bottomed tubular member 31a. The orifice 10 is configured.
【0040】上記アクチュエータ32は、棒状に形成さ
れて筒軸Xに対して同軸上に配置された積層圧電素子3
2aと、この圧電素子32aに電圧の印加、遮断の制御
を行う図示省略の制御器とを備えている。上記圧電素子
32aは圧電セラミック層が上下方向に積層されて電圧
を印加した時に生じる圧電縦効果を利用したものであ
り、電圧の印加、遮断により上下方向に伸縮して加振作
動力を発生するようになっている。つまり、電圧の印加
により印加電圧に対応して上下方向に伸び歪みが生じ、
遮断により縮んで復元するようになっている。上記圧電
素子32aは圧電縦効果が生じる方向に細長い棒状に形
成されており、このような圧電素子32aとしては、例
えば、圧電セラミック層となるセラミック薄板を積層接
着したものの他、上記の圧電セラミック層を厚膜積層技
術(グリーンシート法)の応用により接着剤を使わずに
積層しこれを一体焼結したものなどが適用される。そし
て、上記圧電素子32aは下端が第2支持筒体2の底面
上に位置固定され、上端が後述の駆動側ピストン部材3
5の筒部35bに下から内挿されて加圧板35aの下面
に当接されている。The actuator 32 is formed in the shape of a rod and is arranged coaxially with the cylinder axis X.
2a and a controller (not shown) that controls the application and interruption of voltage to the piezoelectric element 32a. The piezoelectric element 32a utilizes a piezoelectric vertical effect that is generated when a piezoelectric ceramic layer is laminated in the vertical direction and a voltage is applied. The piezoelectric element 32a expands and contracts in the vertical direction by applying and blocking the voltage so as to generate a vibration actuation force. It has become. In other words, when voltage is applied, stretching strain is generated in the vertical direction corresponding to the applied voltage,
It is designed to shrink and restore due to interruption. The piezoelectric element 32a is formed in the shape of an elongated rod in the direction in which the piezoelectric vertical effect is generated. As such a piezoelectric element 32a, for example, a ceramic thin plate to be a piezoelectric ceramic layer is laminated and adhered, and the piezoelectric ceramic layer is also used. By applying the thick film laminating technology (green sheet method), a material obtained by laminating without using an adhesive and integrally sintering it is applied. The lower end of the piezoelectric element 32a is positionally fixed on the bottom surface of the second support cylindrical body 2, and the upper end thereof is the drive-side piston member 3 described later.
5 is inserted into the cylindrical portion 35b from below and is in contact with the lower surface of the pressure plate 35a.
【0041】上記作動特性変換手段33は、第1実施例
と同様に、シリンダ34と、加圧面を構成する加圧板3
5aがこのシリンダ34に下側から上方に内挿された駆
動側ピストン部材35と、先端部(下端部)が上記シリ
ンダ34に上側から下方に内挿されて基端部(上端部)
が上記仕切体9に一体的に連結された従動側ピストン部
材36と、後述の気泡抜孔41とを備えている。As in the first embodiment, the operating characteristic converting means 33 includes the cylinder 34 and the pressure plate 3 forming the pressure surface.
5a is a driving-side piston member 35 inserted in the cylinder 34 from the lower side to the upper side, and a tip end (lower end) is inserted in the cylinder 34 from the upper side to the lower side, and a base end (upper end).
Is provided with a driven side piston member 36 integrally connected to the partition body 9 and a bubble vent hole 41 described later.
【0042】上記駆動側ピストン部材35は大径の円板
部材である加圧板35a上面の加圧面が比較的大きい面
積(A1 )とされている一方、上記従動側ピストン部材
36は上記駆動側ピストン部材35のそれより所定量小
径の円形断面に形成されて下端の受圧面36aが上記面
積(A1 )より所定量小さい面積(A2 )とされてい
る。そして、上記駆動側ピストン部材35の加圧板35
aの下面には筒軸Xに沿って下方に突出する筒部35b
が一体に形成されてこの筒部35b内に上述の如く圧電
素子32aが配設されており、この圧電素子32aが上
下方向に伸縮することにより上記駆動側ピストン部材3
5が進退して上記シリンダ34のシリンダ室34a内に
封入された非圧縮性の作動用液体8を介して上記従動側
ピストン部材36に伝達されるようになっている。つま
り、上記アクチュエータ32による駆動側ピストン部材
35の上下方向作動ストロークをS1 とし、上記作動用
液体8を介して従動側ピストン部材36が作動される作
動ストロークをS2 とすると、このS2 は上記面積A1
,A2 に基いて、 S2 =(A1 /A2 )・S1 となり、S1 の(A1 /A2 )倍に作動ストローク特性
が増大変換されるようになっている。The driving side piston member 35 has a relatively large area (A1) for the pressing surface of the pressing plate 35a, which is a large-diameter disk member, while the driven side piston member 36 is the driving side piston. The pressure receiving surface 36a at the lower end is formed in a circular cross section having a diameter smaller than that of the member 35 by a predetermined amount smaller than the area (A1). The pressure plate 35 of the drive side piston member 35 is
On the lower surface of a, a tubular portion 35b protruding downward along the tubular axis X.
Are integrally formed, and the piezoelectric element 32a is disposed in the tubular portion 35b as described above. The piezoelectric element 32a expands and contracts in the vertical direction, so that the drive-side piston member 3 is formed.
5 moves forward and backward and is transmitted to the driven-side piston member 36 via the incompressible working liquid 8 sealed in the cylinder chamber 34a of the cylinder 34. That is, when the vertical operation stroke of the drive side piston member 35 by the actuator 32 is S1 and the operation stroke at which the driven side piston member 36 is operated via the operation liquid 8 is S2, this S2 is the area A1.
, A2, S2 = (A1 / A2) .multidot.S1 and the operating stroke characteristic is increased and converted to (A1 / A2) times S1.
【0043】上記シリンダ34は、上下方向に互いに重
合されて一体化された一対の板状部材37,38により
形成されており、これら一体化された両板状体37,3
8の外周部が第1実施例と同様に第1取付部材3に固定
されている。上記の内、下側板状体37は比較的厚肉に
形成されその中央部に筒軸Xと同軸に上記大径の加圧板
35aより所定量大径の貫通孔が形成される一方、上記
上側板状体38には上下方向に開口して筒軸Xに沿って
上方に延びる小径筒部38aが一体に形成されている。
そして、上記下側板状体37の貫通孔の下端部に上記加
圧板35aが環状のゴム弾性部材39を介して液密状態
で上下方向に進退可能に支持される一方、上記上側板状
体38の小径筒部38a内に従動側ピストン部材36の
下端部が内挿された状態で筒状のゴム弾性部材40介し
て液密状態で上下方向に進退可能に支持されている。こ
れにより、上記駆動側ピストン部材35の加圧板35
a、従動側ピストン部材の受圧面36a、下側板状体3
7の貫通孔、および、上側板状体38の下面によって密
閉されてシリンダ室34aが画成されている。The cylinder 34 is formed by a pair of plate-like members 37 and 38 which are vertically overlapped with each other and integrated with each other. The plate-like members 37 and 3 are integrated with each other.
The outer peripheral portion of 8 is fixed to the first mounting member 3 as in the first embodiment. Among the above, the lower plate-like body 37 is formed to be relatively thick, and a through hole having a predetermined diameter larger than that of the large-diameter pressure plate 35a is formed in the center of the lower plate-like body 37 coaxially with the cylinder axis X. The side plate member 38 is integrally formed with a small-diameter tubular portion 38a that opens in the vertical direction and extends upward along the tubular axis X.
The pressing plate 35a is supported at the lower end of the through hole of the lower plate-like body 37 via a ring-shaped rubber elastic member 39 so as to be vertically movable in the liquid-tight state, while the upper plate-like body 38 is also supported. With the lower end of the driven-side piston member 36 inserted in the small-diameter tubular portion 38a, the driven-side piston member 36 is supported by a tubular rubber elastic member 40 so as to be vertically movable in a vertical direction. Thereby, the pressure plate 35 of the drive side piston member 35 is
a, the pressure receiving surface 36a of the driven side piston member, the lower plate-like body 3
The through hole 7 and the lower surface of the upper plate-like body 38 are closed to define a cylinder chamber 34a.
【0044】一方、上記従動側ピストン部材36には所
定径の気泡抜孔41が貫通して形成されており、この気
泡抜孔41は下端が上記下端面36aでシリンダ室34
aに臨んで開口しシリンダ室34a内に残留した気泡が
この気泡抜孔41を通して仕切体31下側の平衡室7b
に排出されるようになっている。そして、この気泡抜孔
41の径および長さなどの寸法諸元は上記ゴム弾性体1
1cおよびゴム弾性部材39,40に基く拡張バネと、
気泡抜孔41内の液体の質量とで定まる共振周波数が、
アクチュエータ32の作動により仕切体31を強制加振
させる周波数領域よりも十分に低くなるように設定され
ている。つまり、上記仕切体31の強制加振により受圧
室7aの内圧制御を行う周波数領域の振動が入力した時
には、上記気泡抜孔41が目詰まり現象を生じてロック
するようになっている。On the other hand, the driven side piston member 36 is formed with a bubble vent hole 41 of a predetermined diameter penetrating therethrough. The bubble vent hole 41 has a lower end at the lower end surface 36a of the cylinder chamber 34.
Bubbles that open toward the side a and remain in the cylinder chamber 34a pass through the bubble vent holes 41, and the equilibrium chamber 7b below the partition 31.
It is designed to be discharged to. The dimensional specifications such as the diameter and the length of the bubble vent 41 are the same as those of the rubber elastic body 1 described above.
1c and an expansion spring based on the rubber elastic members 39 and 40,
The resonance frequency determined by the mass of the liquid in the bubble vent 41 is
It is set to be sufficiently lower than the frequency range in which the partition body 31 is forcibly excited by the operation of the actuator 32. That is, when the vibration in the frequency range for controlling the internal pressure of the pressure receiving chamber 7a is input by the forced vibration of the partition body 31, the bubble vent hole 41 causes a clogging phenomenon and locks.
【0045】なお、図中42は上記一対の板状体37,
38の外周部を上下に貫通する1以上のかなり大きめの
連通孔であり、この連通孔42によって平衡室7b内の
上記両板状体37,38より上側部分とダイヤフラム6
側である下側部分との間で液体8の自由な流動が行われ
るようになっている。Reference numeral 42 in the drawing denotes the pair of plate-like members 37,
One or more rather large communicating holes vertically penetrating the outer peripheral portion of 38, and the communicating hole 42 allows the diaphragm 6 and the upper portion of both plate-like bodies 37 and 38 in the equilibrium chamber 7b to be communicated.
A free flow of the liquid 8 is made between the lower part which is the side.
【0046】なお、上記制御式防振装置のその他の構成
は第1実施例のものと同様であるために、同一部材には
同一符号を付して、その説明は省略する。Since the other constitution of the control type vibration damping device is the same as that of the first embodiment, the same members are designated by the same reference numerals and the description thereof will be omitted.
【0047】そして、この第2実施例の場合も、第2取
付部材4側から低周波域の振動が上下方向に弾性支承体
5に入力すると、第1実施例と同様に、上記受圧室7a
と平衡室7bとの間でのオリフィス10を介した液柱共
振により上記振動の減衰が図られる一方、上記オリフィ
ス10がロック状態となる高周波側の振動が入力する
と、その入力方向に応じて圧電素子32aへの電圧印
加,遮断が繰り返され、この進退作動力が作動特性変換
手段33を介して仕切体31に伝達されてこの仕切体3
1が強制加振される。すなわち、第1実施例と同様に、
振動入力を受けた第2取付部材4の変位方向と同位相側
に上記仕切体9が加振されて受圧室7a内の液圧の急増
を抑制することができ、これにより、第1取付部材3側
への伝達率の低減化、動ばね定数の低減化を図ることが
できる。Also in this second embodiment, when vibrations in the low frequency range are input from the second mounting member 4 side in the vertical direction to the elastic support body 5, the pressure receiving chamber 7a is the same as in the first embodiment.
The vibrations are damped by the resonance of the liquid column through the orifice 10 between the equilibrium chamber 7b and the equilibrium chamber 7b. On the other hand, when the vibration on the high frequency side in which the orifice 10 is locked is input, the vibration is generated according to the input direction. The application of voltage to the element 32a and the interruption thereof are repeated, and the forward / backward operating force is transmitted to the partition body 31 via the operating characteristic converting means 33 so that the partition body 3 is operated.
1 is forcibly excited. That is, as in the first embodiment,
The partition 9 is vibrated on the same phase side as the displacement direction of the second mounting member 4 which receives the vibration input, and it is possible to suppress the sudden increase of the hydraulic pressure in the pressure receiving chamber 7a. It is possible to reduce the transmissibility to the third side and the dynamic spring constant.
【0048】この強制加振に際し、アクチュエータ32
の作動により駆動側ピストン部材35が上下動されてそ
の加圧板35aがシリンダ室34a内の液体8を加圧,
減圧する。このシリンダ室34aの液体8が従動側ピス
トン部材36の受圧面36aに作用して従動側ピストン
部材36が上下動する。この際、上記受圧面36aの面
積(A2 )に対する上記加圧板35aの面積(A1 )の
比率(A1 /A2 )で上記駆動側ピストン部材35の作
動ストロークが増大され、この増大された作動ストロー
クで従動側ピストン部材36が上下方向に加振される。
このため、アクチュエータ32による作動ストロークの
(A1 /A2 )倍の作動ストロークで仕切体31を加振
することができる。このようにアクチュエータ32と仕
切体31との間に作動特性変換手段33を介装させるこ
とにより、アクチュエータ32が圧電素子32aにより
構成されて比較的小さい作動ストロークでしか加振させ
ることができないものであっても、仕切体31を比較的
大きい作動ストロークで加振作動させることができる一
方、上記作動特性変換手段33を設けない場合と比べ、
仕切体31を同一の作動ストロークで加振させるための
上記アクチュエータ32の能力や規模、すなわち、圧電
素子32aの積層数や印加電圧値などを小さくすること
ができ、防振装置全体のコンパクト化、作動コストの低
減化を図ることができる。なお、この場合、従動側ピス
トン部材36の作動力は駆動側ピストン部材35のそれ
よりも小さくなるものの、アクチュエータ32が圧電素
子32aにより構成されて、元来、比較的大きい作動力
を有しているため、所要の作動力に対して十分なものを
確保することができる。At the time of this forced vibration, the actuator 32
The driving side piston member 35 is moved up and down by the operation of the pressure plate 35a to pressurize the liquid 8 in the cylinder chamber 34a,
Decompress. The liquid 8 in the cylinder chamber 34a acts on the pressure receiving surface 36a of the driven side piston member 36, and the driven side piston member 36 moves up and down. At this time, the working stroke of the drive-side piston member 35 is increased by the ratio (A1 / A2) of the area (A1) of the pressure plate 35a to the area (A2) of the pressure receiving surface 36a. The driven piston member 36 is vertically vibrated.
Therefore, the partition 31 can be vibrated with an operating stroke that is (A1 / A2) times the operating stroke of the actuator 32. By thus interposing the operation characteristic conversion means 33 between the actuator 32 and the partition body 31, the actuator 32 is constituted by the piezoelectric element 32a and can be excited only with a relatively small operation stroke. Even if there is, the partition body 31 can be vibrated with a relatively large operating stroke, while compared with the case where the operating characteristic conversion means 33 is not provided.
It is possible to reduce the capacity and scale of the actuator 32 for vibrating the partition body 31 with the same operation stroke, that is, the number of stacked piezoelectric elements 32a, the applied voltage value, etc. The operating cost can be reduced. In this case, although the operating force of the driven side piston member 36 is smaller than that of the driving side piston member 35, the actuator 32 is composed of the piezoelectric element 32a and originally has a relatively large operating force. Therefore, it is possible to secure a sufficient amount for the required operating force.
【0049】そして、このような作動ストローク特性の
増大変換が行われる防振装置において、上記シリンダ室
34aは気泡抜孔41を介して平衡室7bと連通と連通
されているため、例えば防振装置の製造時に気泡がシリ
ンダ室34aの液体8中に万一残留した場合であって
も、その残留した気泡が上記気泡抜孔41を通して平衡
室7b側に排出されるため、駆動側ピストン部材35に
よる加圧時に上記シリンダ室34aに残留した気泡によ
りシリンダ室34a内の容積が縮小することに伴う作動
ストロークの特性変換度合の低下を防止することができ
る。この場合、アクチュエータ32が圧電素子32aに
よりされて駆動側ピストン部材35の作動ストロークが
極めて小さいため、上記の特性変換度合の低下を防止で
きることは、上記の如きアクチュエータ32を用いる防
振装置にとって、特に重要な効果となる。In the vibration isolator in which the operation stroke characteristic is increased and converted as described above, since the cylinder chamber 34a is in communication with the equilibrium chamber 7b through the bubble vent hole 41, for example, the vibration isolator Even if air bubbles remain in the liquid 8 in the cylinder chamber 34a during manufacturing, the remaining air bubbles are discharged to the equilibrium chamber 7b side through the air bubble vent hole 41, so that the driving side piston member 35 pressurizes the air bubbles. It is possible to prevent a decrease in the degree of characteristic conversion of the working stroke due to the reduction of the volume in the cylinder chamber 34a due to the bubbles remaining in the cylinder chamber 34a. In this case, since the actuator 32 is driven by the piezoelectric element 32a and the operation stroke of the driving side piston member 35 is extremely small, it is possible to prevent the above-mentioned deterioration of the characteristic conversion degree, especially for the vibration isolator using the actuator 32 as described above. It has an important effect.
【0050】しかも、上記の場合、平衡室7b内に排出
された気泡がオリフィス10を通して受圧室7a側に排
出され、受圧室7a内を上昇してつぼ部25内に溜めら
れるため、平衡室7bおよび受圧室7aから混入気泡を
確実に排出させることができる。加えて、上記気泡抜孔
41の高周波領域でのロック、および、つぼ部25の低
周波領域でのロックによって、上記高周波領域での作動
特性変換手段33による作動ストロークの特性変換作用
を確実に得ることができる一方、オリフィス10による
低周波領域の入力振動の減衰を確実に得ることができる
点は、第1実施例と同様である。Moreover, in the above case, the air bubbles discharged into the equilibrium chamber 7b are discharged to the pressure receiving chamber 7a side through the orifice 10, rise in the pressure receiving chamber 7a and are stored in the crucible portion 25. Also, the mixed bubbles can be reliably discharged from the pressure receiving chamber 7a. In addition, by locking the bubble vent hole 41 in the high frequency range and locking the pot 25 in the low frequency range, it is possible to reliably obtain the characteristic conversion action of the operation stroke by the operation characteristic conversion means 33 in the high frequency range. On the other hand, the point that the input vibration in the low frequency region can be reliably attenuated by the orifice 10 is the same as in the first embodiment.
【0051】<他の態様例>なお、本発明は上記第1お
よび第2実施例に限定されるものではなく、その他種々
の変形例を包含するものである。すなわち、上記実施例
では、振動板として、受圧室7aと平衡室7bとを仕切
る仕切体9,31を用いているが、これに限らず、例え
ば仕切体を固定にし、この仕切体とは別に振動板を設け
るようにしてもよい。<Other Embodiments> The present invention is not limited to the first and second embodiments described above, but includes various other modifications. That is, in the above-mentioned embodiment, as the diaphragm, the partition bodies 9 and 31 for partitioning the pressure receiving chamber 7a and the equilibrium chamber 7b are used, but the invention is not limited to this. For example, the partition body may be fixed and separated from this partition body. A diaphragm may be provided.
【0052】上記実施例では、各ピストン部材17,1
8、35,36をゴム弾性部材22,23、39,40
により弾性支持させているが、これに限らず、液密に維
持した状態で摺動により進退可能に支持させてもよい。In the above embodiment, each piston member 17, 1
8, 35, 36 are rubber elastic members 22, 23, 39, 40
However, the invention is not limited to this and may be supported so as to be able to advance and retreat by sliding in a liquid-tight state.
【0053】上記実施例では、駆動側と従動側との両ピ
ストン部材17,35、18,36を共に進退方向が上
下方向になるように配置しているが、これに限らず、上
記従動側ピストン部材18,36をのみ振動板の加振方
向である上下方向に配置する必要があるだけで、駆動側
ピストン部材17,35は、シリンダ室16a,34a
内の液体を加圧,減圧できれば、いずれの方向に進退す
るように配置してもよい。In the above embodiment, both the driving side and driven side piston members 17, 35, 18 and 36 are arranged so that the advancing and retreating directions are the up and down directions. Only the piston members 18 and 36 need to be arranged in the vertical direction, which is the vibration direction of the diaphragm, and the drive side piston members 17 and 35 are arranged in the cylinder chambers 16a and 34a.
As long as the liquid inside can be pressurized or depressurized, it may be arranged so as to move forward or backward in any direction.
【0054】また、上記実施例では、オリフィス10を
仕切体9,31自体に形成しているが、これに限らず、
例えば、仕切体とは全く独立してオリフィスを形成して
もよい。Further, in the above-mentioned embodiment, the orifice 10 is formed in the partition bodies 9 and 31 itself, but the invention is not limited to this.
For example, the orifice may be formed completely independently of the partition body.
【0055】さらに、上記実施例では、上側の第2取付
部材4をエンジン側に、第1取付部材3を車体側に連結
しているが、これに限らず、例えばエンジンを吊り下げ
支承するタイプでは、第1取付部材を車体側に、第2取
付部材をエンジン側に連結すればよい。この場合、図3
に示すように、シリンダ室34aの上位となる駆動側ピ
ストン部材の加圧板35aに気泡抜孔43を設け、シリ
ンダ室34a内の液体8中に混入した気泡を上記気泡抜
孔43から平衡室7bのダイヤフラム6側の部分に排出
し、この頂部44に気泡を溜めるようにすればよい。こ
の場合においても、上記気泡抜孔43は第1,第2実施
例と同様にチューニングすればよい。また、気泡が上記
ダイヤフラム6の頂部44に溜められるため、弾性支承
体5の側から入力する低周波振動の減衰特性を害するこ
ともなく、また、つぼ部25を設ける必要もない。Further, in the above embodiment, the upper second mounting member 4 is connected to the engine side and the first mounting member 3 is connected to the vehicle body side. However, the present invention is not limited to this, and the engine is suspended and supported, for example. Then, it suffices to connect the first mounting member to the vehicle body side and the second mounting member to the engine side. In this case,
As shown in FIG. 5, a bubble vent hole 43 is provided in the pressure plate 35a of the drive side piston member above the cylinder chamber 34a, so that the bubbles mixed in the liquid 8 in the cylinder chamber 34a can pass through the bubble vent hole 43 to the diaphragm of the equilibration chamber 7b. The gas may be discharged to the portion on the 6 side and the bubbles may be accumulated in the top portion 44. Even in this case, the bubble vent hole 43 may be tuned in the same manner as in the first and second embodiments. Further, since the bubbles are stored in the top portion 44 of the diaphragm 6, the damping characteristic of low frequency vibration input from the elastic support 5 side is not impaired, and it is not necessary to provide the crucible portion 25.
【0056】[0056]
【発明の効果】以上説明したように、請求項1記載の発
明における制御式防振装置によれば、振動板と、これを
強制加振するためのアクチュエータとの間に、シリンダ
と、アクチュエータに連結されてシリンダに対して進退
する駆動側ピストン部材と、振動板に連結されてシリン
ダ室内に封入された非圧縮性液体を介して従動される従
動側ピストン部材と、気泡抜孔とで構成した作動特性変
換手段を介装し、その駆動側ピストン部材の加圧面の面
積と従動側ピストン部材の受圧面の面積とを互いに異な
る大きさに設定しているため、上記従動側ピストン部材
の作動力もしくは作動ストロークなどの進退作動特性
を、アクチュエータによる駆動側ピストン部材の進退作
動力もしくは作動ストロークに対して上記加圧面の面積
と受圧面の面積との比に応じて変化させたものにするこ
とができる。As described above, according to the control type vibration damping device of the first aspect of the invention, the cylinder and the actuator are provided between the diaphragm and the actuator for forcibly exciting the diaphragm. Operation consisting of a drive-side piston member that is connected and moves back and forth with respect to the cylinder, a driven-side piston member that is connected to the vibration plate and driven by the incompressible liquid enclosed in the cylinder chamber, and a bubble vent hole Since the characteristic converting means is interposed and the area of the pressing surface of the driving side piston member and the area of the pressure receiving surface of the driven side piston member are set to different sizes from each other, the operating force of the driven side piston member or The advancing / retreating characteristic such as the operating stroke can be calculated by comparing the area of the pressure surface and the area of the pressure receiving surface with respect to the advancing / retreating operation force of the driving side piston member by the actuator or the operating stroke. It can be that varied depending on the.
【0057】そして、このような作動特性を変換し得る
防振装置において、製造時にシリンダ室に混入した空気
がその内部の液体中に気泡として残留した場合であって
も、上記シリンダ室の上位の側のピストン部材に気泡抜
孔を形成しているため、その気泡を上記気泡抜孔を通し
て液室側に確実に排出することができ、この結果、上記
駆動側ピストン部材の進退作動時にシリンダ室内の液体
をシリンダ室の容積のまま確実に一定に保つことがで
き、所定の効率の作動特性の変換を確実に得ることがで
きる。しかも、この気泡抜孔を介した液柱共振の共振周
波数として上記アクチュエータを作動させる入力振動の
設定周波数域よりも十分に低いものに設定しているた
め、上記アクチュエータを作動させる周波数領域では上
記気泡抜孔を目詰まり状態としてロックさせることがで
き、このため、上記各ピストン部材の加圧面と受圧面と
の両面積比に基く作動特性の変換を確実に所定のもに維
持することができる。In the vibration isolator capable of converting such operating characteristics, even when the air mixed in the cylinder chamber at the time of manufacture remains as bubbles in the liquid inside, the upper part of the cylinder chamber Since the air bubble vent hole is formed in the piston member on the side, the air bubble can be surely discharged to the liquid chamber side through the air bubble vent hole. The volume of the cylinder chamber can be surely kept constant and the conversion of the operating characteristic with a predetermined efficiency can be surely obtained. Moreover, since the resonance frequency of the liquid column resonance through the bubble vent is set to be sufficiently lower than the set frequency range of the input vibration for operating the actuator, the bubble vent is used in the frequency range for operating the actuator. Can be locked as a clogged state, so that the conversion of the operating characteristics based on the area ratio between the pressure surface and the pressure receiving surface of each piston member can be reliably maintained at a predetermined value.
【0058】請求項2記載の発明によれば、上記請求項
1記載の発明による効果に加えて、液室の上方に位置付
けた弾性支承体の頂部に気泡を収容するつぼ部を設けて
いるため、シリンダ室の上位のピストン部材に形成され
た気泡抜孔を通して上記弾性支承体側の液室に排出され
た気泡を上記つぼ部に収容することができ、この結果、
液室内の液体中から上記気泡を排除することができる。According to the second aspect of the invention, in addition to the effect of the first aspect of the invention, a crucible portion for accommodating air bubbles is provided at the top of the elastic support positioned above the liquid chamber. , The bubbles discharged into the liquid chamber on the side of the elastic bearing through the bubble vent hole formed in the upper piston member of the cylinder chamber can be accommodated in the pot portion, and as a result,
The bubbles can be eliminated from the liquid in the liquid chamber.
【0059】請求項3記載の発明によれば、上記請求項
2記載の発明による効果に加えて、液室をオリフィスで
互いに連通させた受圧室と平衡室とに仕切るとともに、
つぼ部に対して、受圧室と平衡室とを互いに連通するオ
リフィスの設定共振周波数よりも十分に低い共振周波数
を設定しているため、このオリフィスの液柱共振により
入力振動の減衰を図る周波数域では上記気泡を収容した
つぼ部をロックさせることができ、この結果、その周波
数域の振動が入力した際に上記つぼ部内の気泡が液室内
の液体に混入してオリフィスの減衰特性を悪化させるこ
とを確実に防止することができる。According to the invention of claim 3, in addition to the effect of the invention of claim 2, the liquid chamber is partitioned into a pressure receiving chamber and an equilibrium chamber which are communicated with each other by an orifice, and
The resonance frequency is set to the pot, which is sufficiently lower than the set resonance frequency of the orifice that connects the pressure receiving chamber and the equilibrium chamber to each other. Can lock the pot containing the bubble, and as a result, when the vibration in the frequency range is input, the bubble in the pot mixes with the liquid in the liquid chamber and deteriorates the damping characteristic of the orifice. Can be reliably prevented.
【0060】請求項4記載の発明によれば、上記請求項
1記載の発明による効果に加えて、駆動側ピストン部材
の加圧面の面積を、従動側ピストン部材の受圧面の面積
より小さく設定して作動特性変換手段により従動側ピス
トン部材がアクチュエータの作動力よりも大きい作動力
で進退作動されるように作動特性の変換をしている場合
において、製造時に気泡が万一残留しても、その気泡を
気泡抜孔により排出させて上記残留気泡に伴うシリンダ
室内の容積変化の発生を防止することができる結果、作
動特性の変換効率の低下を確実に防止することができ
る。According to the invention of claim 4, in addition to the effect of the invention of claim 1, the area of the pressing surface of the driving side piston member is set smaller than the area of the pressure receiving surface of the driven side piston member. If the operating characteristic is converted by the operating characteristic converting means such that the driven side piston member is moved forward and backward with an operating force larger than the operating force of the actuator, even if bubbles remain during manufacturing, As a result of the bubbles being discharged through the bubble vents and the volume change in the cylinder chamber caused by the residual bubbles being prevented from occurring, it is possible to reliably prevent the conversion efficiency of the operating characteristics from decreasing.
【0061】また、請求項5記載の発明によれば、上記
請求項1記載の発明による効果に加えて、駆動側ピスト
ン部材の加圧面の面積を、従動側ピストン部材の受圧面
の面積より大きく設定して作動特性変換手段により従動
側ピストン部材がアクチュエータの作動ストロークより
も大きい作動ストロークで進退作動されるように作動特
性を変換している場合において、製造時に気泡が万一残
留しても、その気泡を気泡抜孔により排出させて上記残
留気泡に伴うシリンダ室内の容積変化の発生を防止する
ことができる結果、作動特性の変換効率の低下を確実に
防止することができる。According to the invention of claim 5, in addition to the effect of the invention of claim 1, the area of the pressing surface of the driving side piston member is larger than the area of the pressure receiving surface of the driven side piston member. In the case where the operating characteristic is converted by the operating characteristic converting means so that the driven side piston member is moved forward and backward with an operating stroke larger than the operating stroke of the actuator, even if bubbles remain during manufacturing, The bubbles can be discharged through the bubble vents to prevent the volume change in the cylinder chamber due to the residual bubbles, and as a result, it is possible to reliably prevent the conversion efficiency of the operating characteristics from being lowered.
【0062】さらに、請求項6記載の発明によれば、上
記請求項1記載の発明による効果に加えて、アクチュエ
ータを圧電素子により構成し、電圧の印加、遮断による
圧電素子の伸縮により駆動側ピストン部材を加振するよ
うにした場合において、上記圧電素子による伸縮量が極
めて小さくて、シリンダ室に残留した気泡量に対する作
動特性変換手段による作動ストロークの増大変換効率の
低下度合が極めて大きいものであっても、上記残留気泡
を気泡抜孔によって確実に排出することができる結果、
振動板を確実に所定の増大変換効率の作動ストロークに
よって加振させることができる。従って、アクチュエー
タとして圧電素子を用い、これに作動ストロークを増大
させる作動特性変換手段を組み合わせた場合において
も、上記気泡抜孔を設けることにより上記の作動ストロ
ーク増大効果を確実に得ることができる。Further, according to the invention of claim 6, in addition to the effect of the invention of claim 1, the actuator is composed of a piezoelectric element, and the driving side piston is expanded and contracted by applying and blocking a voltage. When the member is vibrated, the amount of expansion and contraction by the piezoelectric element is extremely small, and the increase in the operation stroke by the operation characteristic conversion means with respect to the amount of bubbles remaining in the cylinder chamber is extremely large. Even as a result, it is possible to reliably discharge the residual bubbles by the bubble vents,
It is possible to reliably vibrate the diaphragm with an operation stroke having a predetermined increased conversion efficiency. Therefore, even when the piezoelectric element is used as the actuator and the operation characteristic conversion means for increasing the operation stroke is combined with the actuator, the effect of increasing the operation stroke can be reliably obtained by providing the bubble vent hole.
【図1】本発明の第1実施例を示す縦断面図である。FIG. 1 is a vertical cross-sectional view showing a first embodiment of the present invention.
【図2】本発明の第2実施例を示す縦断面図である。FIG. 2 is a vertical sectional view showing a second embodiment of the present invention.
【図3】他の態様例を示す縦断面図である。FIG. 3 is a vertical cross-sectional view showing another embodiment example.
3 第1取付部材 4 第2取付部材 5 弾性支承体 6 ダイヤフラム(弾性薄膜部材) 7 液室 7a 受圧室 7b 平衡室 8 液体 9 仕切体(振動板) 10 オリフィス 12,32 アクチュエータ 15,33 作動特性変換手段 17,35 駆動側ピストン部材 18,36 従動側ピストン部材 17a 加圧面 24,41,43 気泡抜孔 25 つぼ部 32a 圧電素子 35a 加圧板(加圧面) 18a,36a 受圧面 3 1st mounting member 4 2nd mounting member 5 Elastic support body 6 Diaphragm (elastic thin film member) 7 Liquid chamber 7a Pressure receiving chamber 7b Equilibrium chamber 8 Liquid 9 Partition body (vibrating plate) 10 Orifice 12,32 Actuator 15,33 Operating characteristics Conversion means 17,35 Drive side piston member 18,36 Driven side piston member 17a Pressurizing surface 24,41,43 Bubble removal hole 25 Vessel part 32a Piezoelectric element 35a Pressurizing plate (pressurizing surface) 18a, 36a Pressure receiving surface
Claims (6)
一対の取付部材と、この一対の取付部材を互いに連結す
る弾性支承体と、この弾性支承体により画成されてし非
圧縮性の液体が封入された液室と、この液室の上記弾性
支承体の側を仕切るように配置され上記弾性支承体の側
の液室の容積を拡縮する方向に変位可能に支持された振
動板と、上記振動板を加振作動させるアクチュエータと
を備え、このアクチュエータの作動を制御することによ
り上記弾性支承体の側の液室の内圧を制御するようにし
た制御式防振装置において、 上記振動板とアクチュエータとの間には、アクチュエー
タによる振動板の加振作動の特性を変換する作動特性変
換手段が介装され、この作動特性変換手段は、内部に上
記液体と同じ液体が封入されたシリンダ室を有するシリ
ンダと、このシリンダに進退可能に配設された駆動側お
よび従動側の一対のピストン部材と、上記シリンダ室内
の気泡を上記液室側に排出する気泡抜孔とを備えてお
り、 上記駆動側ピストン部材は基端部が上記アクチュエータ
により加振作動されるようアクチュエータに連結され、
先端部の加圧面が上記シリンダ室の流体に臨むよう上記
シリンダに配置される一方、上記従動側ピストン部材は
基端部が上記振動板に取付けられ、先端部の受圧面がシ
リンダ室の流体を介して駆動側ピストン部材からの加振
作動力を受けるように配置されており、 上記気泡抜孔は、上記駆動側ピストン部材および従動側
ピストン部材の内の上方に位置するピストン部材を貫通
して上記シリンダ室と液室とを互いに連通させるよう形
成され、かつ、その気泡抜孔を介した液柱の共振周波数
が、上記アクチュエータを作動させるものとして予め設
定された入力振動の周波数域よりも十分に低くなるよう
に設定されていることを特徴とする制御式防振装置。1. A pair of mounting members, which are arranged apart from each other in the vibration input direction, an elastic support member that connects the pair of mounting members to each other, and an incompressible liquid defined by the elastic support members. A liquid chamber in which is enclosed, and a diaphragm which is arranged so as to partition the side of the elastic bearing of the liquid chamber and is supported so as to be displaceable in the direction of expanding and contracting the volume of the liquid chamber on the side of the elastic bearing, A control type vibration damping device, comprising: an actuator for vibrating the diaphragm, and controlling the operation of the actuator to control the internal pressure of the liquid chamber on the elastic bearing side. Between the actuator and the actuator, an operating characteristic converting means for converting the characteristic of the vibration operation of the diaphragm by the actuator is interposed, and the operating characteristic converting means is a cylinder chamber in which the same liquid as the above liquid is sealed. And a pair of piston members on the driving side and the driven side, which are arranged to move forward and backward in the cylinder, and a bubble vent hole for discharging bubbles in the cylinder chamber to the liquid chamber side. The piston member is connected to the actuator so that the base end portion is vibrated by the actuator,
The pressurizing surface of the tip portion is arranged in the cylinder so as to face the fluid in the cylinder chamber, while the base end portion of the driven side piston member is attached to the diaphragm, and the pressure receiving surface of the tip portion exposes the fluid in the cylinder chamber. Is arranged so as to receive an oscillating actuating force from the drive side piston member via the above-mentioned bubble extraction hole, and penetrates the piston member located above the drive side piston member and the driven side piston member, and the cylinder The chamber and the liquid chamber are formed to communicate with each other, and the resonance frequency of the liquid column through the bubble vent hole is sufficiently lower than the frequency range of the input vibration preset for operating the actuator. The vibration control device is a control type that is set as follows.
するつぼ部が上記液室の頂部に臨んで下向きに開口する
よう上記弾性支承体に形成されている制御式防振装置。2. The liquid chamber on the side of the elastic support is positioned above, and a crucible for containing bubbles is formed in the elastic support so as to open downward facing the top of the liquid chamber. Controlled anti-vibration device.
弾性薄膜部材により画成されて拡縮可能な平衡室とに仕
切られて、この受圧室と平衡室とを連通するオリフィス
を備えており、 つぼ部に対して、上記オリフィスを介した液柱の設定共
振周波数よりも十分に低い共振周波数が設定されている
制御式防振装置。3. The pressure receiving chamber according to claim 2, wherein the liquid chamber is partitioned into a pressure receiving chamber on the side of the elastic support and an equilibrium chamber which is at least partially defined by an elastic thin film member and is expandable and contractible. And a balance chamber, the control type vibration damping device having a resonance frequency sufficiently lower than the resonance frequency of the liquid column through the orifice.
部材の受圧面の面積より小さく設定されて、作動特性変
換手段が従動側ピストン部材の加振作動力特性を増幅す
るものである制御式防振装置。4. The area of the pressurizing surface of the driving side piston member is set to be smaller than the area of the pressure receiving surface of the driven side piston member, and the operating characteristic converting means sets the vibration actuating force characteristic of the driven side piston member. A control type anti-vibration device that amplifies.
部材の受圧面の面積より大きく設定されて、作動特性変
換手段が従動側ピストン部材の加振作動ストローク特性
を増幅するものである制御式防振装置。5. The driving characteristic of the driven piston member according to claim 1, wherein the pressing surface area of the driving side piston member is set larger than the pressure receiving surface area of the driven piston member. Controlled anti-vibration device that amplifies the characteristics.
電素子によって構成されている制御式防振装置。6. The control type vibration damping device according to claim 1, wherein the actuator is composed of a piezoelectric element that expands and contracts by applying and blocking a voltage.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2387194A JP3499279B2 (en) | 1994-02-22 | 1994-02-22 | Control type anti-vibration device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2387194A JP3499279B2 (en) | 1994-02-22 | 1994-02-22 | Control type anti-vibration device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH07233851A true JPH07233851A (en) | 1995-09-05 |
JP3499279B2 JP3499279B2 (en) | 2004-02-23 |
Family
ID=12122515
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2387194A Expired - Fee Related JP3499279B2 (en) | 1994-02-22 | 1994-02-22 | Control type anti-vibration device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3499279B2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000356242A (en) * | 1999-05-17 | 2000-12-26 | Hutchinson Sa | Active hydraulic vibration control support device and active vibration control system including this support device |
CN104100673A (en) * | 2014-07-22 | 2014-10-15 | 建新赵氏集团有限公司 | Semi-active control hydraulic suspension for automobile powertrain |
CN115515705A (en) * | 2020-06-03 | 2022-12-23 | 株式会社村田制作所 | Bubble generation device and bubble generation system |
-
1994
- 1994-02-22 JP JP2387194A patent/JP3499279B2/en not_active Expired - Fee Related
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000356242A (en) * | 1999-05-17 | 2000-12-26 | Hutchinson Sa | Active hydraulic vibration control support device and active vibration control system including this support device |
JP4685213B2 (en) * | 1999-05-17 | 2011-05-18 | ユチンソン | Active hydraulic vibration preventing support device and active vibration preventing system including the support device |
CN104100673A (en) * | 2014-07-22 | 2014-10-15 | 建新赵氏集团有限公司 | Semi-active control hydraulic suspension for automobile powertrain |
CN104100673B (en) * | 2014-07-22 | 2016-03-02 | 建新赵氏集团有限公司 | Automobile power assembly semi-active control hydraulic mount |
CN115515705A (en) * | 2020-06-03 | 2022-12-23 | 株式会社村田制作所 | Bubble generation device and bubble generation system |
Also Published As
Publication number | Publication date |
---|---|
JP3499279B2 (en) | 2004-02-23 |
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