JP5175531B2 - Vibration isolator - Google Patents

Vibration isolator Download PDF

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Publication number
JP5175531B2
JP5175531B2 JP2007314611A JP2007314611A JP5175531B2 JP 5175531 B2 JP5175531 B2 JP 5175531B2 JP 2007314611 A JP2007314611 A JP 2007314611A JP 2007314611 A JP2007314611 A JP 2007314611A JP 5175531 B2 JP5175531 B2 JP 5175531B2
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Japan
Prior art keywords
piston
liquid chamber
cylinder
mounting member
liquid
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JP2007314611A
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JP2009138831A (en
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哲 植木
和正 久世
信也 吉田
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Bridgestone Corp
Toyota Motor Corp
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Bridgestone Corp
Toyota Motor Corp
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Priority to JP2007314611A priority Critical patent/JP5175531B2/en
Priority to PCT/JP2008/072080 priority patent/WO2009072574A1/en
Priority to CN200880119288.7A priority patent/CN101889151B/en
Publication of JP2009138831A publication Critical patent/JP2009138831A/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
    • B60K5/12—Arrangement of engine supports
    • B60K5/1208—Resilient supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
    • F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
    • F16F13/107—Passage design between working chambers

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Description

この発明は、エンジンマウント等として用いて好適な防振装置に関するものであり、とくには、主液室および副液室の液室内圧の変動に基いて、それらの液室間での液体の流動経路を自動的に選択して、入力振動を、主には、通路内の液体の液柱共振をもって、防振および減衰させるものであって、ピストンの摺動機構を、装置の大型化なしに簡易に構成できる技術を提案するものである。   The present invention relates to a vibration isolator suitable for use as an engine mount or the like, and in particular, the flow of liquid between the liquid chambers based on fluctuations in the liquid chamber pressures of the main liquid chamber and the sub liquid chamber. The path is automatically selected to dampen and attenuate the input vibration mainly by the liquid column resonance of the liquid in the passage. The piston sliding mechanism can be reduced without increasing the size of the device. A technique that can be easily configured is proposed.

装置の内部に区画される主液室と副液室との内圧の変動に基いて、それらの両液室間での液体の流動経路を自動的に選択して、入力振動を吸収等する従来の防振装置としては、たとえば、特許文献１に開示されたものがある。   Conventionally, based on fluctuations in the internal pressure between the main liquid chamber and the sub liquid chamber partitioned inside the device, the liquid flow path between these two liquid chambers is automatically selected to absorb the input vibration, etc. As an anti-vibration device, there is one disclosed in Patent Document 1, for example.

この防振装置は、それを、図７に例示する縦断面図に基いて説明すると、振動受け部に連結される第１の取付部材１１１と、振動発生部に連結される第２の取付部材１１２と、第１の取付部材１１１と第２の取付部材１１２との間に配置された弾性体１１３と、弾性体１１３を隔壁の一部として液体が封入され、該弾性体１１３の弾性変形に伴って内容積が変化する主液室１１４と、液体が封入され内容積が拡縮可能とされた副液室１１５と、主液室１１４と副液室１１５とを互いに連通する第１の制限通路１１６と、主液室１１４と副液室１１５とを互いに連通し、第１の制限通路１１６よりも液体の流通抵抗の小さい第２の制限通路１１７と、主液室１１４と副液室１１５との間に設けられ、液体が充填されたシリンダ室１１８と、シリンダ室内を、第２の制限通路１１７の一部を構成すると共に副液室１１５に連通したオリフィス空間１１９と第２の制限通路１１７から隔離された液圧空間とに区画し、オリフィス空間１１９及び液圧空間の拡縮方向に沿って所定の開放位置と閉塞位置との間で移動可能とされたプランジャ部材１２０と、主液室１１４と液圧空間との間に配置され、シリンダ室１１８を主液室１１４及び副液室１１５から区画した仕切部材１２１と、オリフィス空間内に面するように設けられ、第２の制限通路１１７におけるオリフィス空間１１９と他の部分とを連通させ、プランジャ部材１２０が開放位置にあると開放され、プランジャ部材１２０が閉塞位置へ移動すると閉塞されるオリフィス開口１２２と、プランジャ部材１２０を、液圧空間を縮小する開放位置側へ付勢する付勢部材１２３と、主液室１１４とシリンダ室１１８との間に設けられ、主液室内の液圧変化に伴って該主液室１１４と液圧空間との間で一方向へのみ液体を流通させ得る逆止弁１２４と、プランジャ部材１２０に前記拡縮方向に沿って貫通するように設けられた軸受穴１２５と、仕切部材１２１に前記拡縮方向に沿って延在するように設けられ、前記軸受穴内に相対的に摺動可能に挿入されるガイド軸1２６と、を有し、軸受穴１２５の内径とガイド軸１２６の外径との差に応じて算出されるプランジャ部材１２０の前記拡縮方向に対する最大傾き角度をθＭＡＸとした場合に、シリンダ室１１８の内径とプランジャ部材１２０の外径との差ＤＭＩＮを、プランジャ部材１２０に前記最大傾き角θＭＡＸの傾きが生じた状態で、プランジャ部材１２０の外周面における任意の部位が、前記シリンダ室１１８の内周面との間に０ｍｍ以上の間隔を保つように設定したことを特徴とするものである。 This vibration isolator will be described based on the longitudinal sectional view illustrated in FIG. 7. The first mounting member 111 connected to the vibration receiving portion and the second mounting member connected to the vibration generating portion. 112, an elastic body 113 disposed between the first mounting member 111 and the second mounting member 112, and a liquid is sealed with the elastic body 113 as a part of the partition wall, and the elastic body 113 is elastically deformed. Accordingly, the main liquid chamber 114 whose internal volume changes, the sub liquid chamber 115 in which the liquid is enclosed and the internal volume can be expanded and contracted, and the first restriction passage that communicates the main liquid chamber 114 and the sub liquid chamber 115 with each other. 116, the main liquid chamber 114 and the sub liquid chamber 115 communicate with each other, the second restricting passage 117 having a liquid flow resistance smaller than that of the first restricting passage 116, the main liquid chamber 114 and the sub liquid chamber 115, Between the cylinder chamber 118 filled with liquid and the The chamber is divided into an orifice space 119 that forms part of the second restriction passage 117 and communicates with the sub liquid chamber 115 and a hydraulic pressure space that is isolated from the second restriction passage 117, and the orifice space 119 and A plunger member 120 that is movable between a predetermined open position and a closed position along the expansion / contraction direction of the hydraulic space, and is disposed between the main fluid chamber 114 and the hydraulic space, and the cylinder chamber 118 is disposed in the main chamber. The partition member 121 partitioned from the liquid chamber 114 and the sub-liquid chamber 115 is provided so as to face the orifice space. The orifice space 119 and the other part in the second restriction passage 117 are communicated with each other. The orifice member 122 that is opened when in the open position and closed when the plunger member 120 moves to the closed position and the plunger member 120 reduce the hydraulic pressure space. An urging member 123 that urges toward the open position side is provided between the main liquid chamber 114 and the cylinder chamber 118, and between the main liquid chamber 114 and the hydraulic pressure space as the hydraulic pressure changes in the main liquid chamber. The check valve 124 can circulate liquid only in one direction, the bearing hole 125 provided to penetrate the plunger member 120 along the expansion / contraction direction, and the partition member 121 extending along the expansion / contraction direction. And a guide shaft 126 that is slidably inserted into the bearing hole, and is calculated according to the difference between the inner diameter of the bearing hole 125 and the outer diameter of the guide shaft 126. When the maximum inclination angle of the plunger member 120 with respect to the expansion / contraction direction is θ MAX , the difference D MIN between the inner diameter of the cylinder chamber 118 and the outer diameter of the plunger member 120 is determined as the inclination of the maximum inclination angle θ MAX to the plunger member 120. Arise State, any site in the outer peripheral surface of the plunger member 120 is characterized in that which is set to maintain a minimum of 0mm between the inner peripheral surface of the cylinder chamber 118.

これにより、この防振装置では、プランジャ部材１２０にガイド軸１２６に対する傾きが生じた場合でも、プランジャ部材１２０の外周面とシリンダ室１１８の内周面との間に摩擦抵抗が生じることを実質的に防止し、プランジャ部材１２０の拡縮方向に沿った移動抵抗の増加を効果的に抑制できるので、プランジャ部材１２０が入力振動の周波数に対応する位置（開放位置又は閉塞位置）へ正常に移動しなくなることを防止できるとする。
特開２００７−１２０６００号公報 Thereby, in this vibration isolator, even when the plunger member 120 is inclined with respect to the guide shaft 126, it is substantially possible that a frictional resistance is generated between the outer peripheral surface of the plunger member 120 and the inner peripheral surface of the cylinder chamber 118. Therefore, the increase in the movement resistance along the expansion / contraction direction of the plunger member 120 can be effectively suppressed, so that the plunger member 120 does not normally move to the position corresponding to the frequency of the input vibration (open position or closed position). This can be prevented.
JP 2007-120600 A

しかるに、プランジャ部材１２０を、上記従来技術でいうように常に円滑に移動させるためには、シリンダ室１１８の内周面と、シリンダとは別体になる仕切部材１２１のガイド軸１２６の外周面とを高い精度で同心加工することが必要になる他、プランジャ部材１２０の外周面および軸受穴１２５をもまた、それらとの関連の下で同心加工することが必要になるため、所定の精度を実現するための加工工数が著しく嵩むという問題があった他、小径のガイド軸１２６および軸受穴１２５の摩耗等に起因する、プランジャ部材１２０の移動精度の低下、ひいては、プランジャ部材１２０の作動不良が不可避になるという問題もあった。   However, in order to always move the plunger member 120 smoothly as described in the prior art, the inner peripheral surface of the cylinder chamber 118 and the outer peripheral surface of the guide shaft 126 of the partition member 121 that is separate from the cylinder are provided. Is required to be concentrically processed with high accuracy, and the outer peripheral surface of the plunger member 120 and the bearing hole 125 are also required to be concentrically processed in relation to them, thereby achieving a predetermined accuracy. In addition to the problem that the man-hours required for the operation are significantly increased, a decrease in the movement accuracy of the plunger member 120 due to the wear of the small-diameter guide shaft 126 and the bearing hole 125 and the malfunction of the plunger member 120 are unavoidable. There was also a problem of becoming.

この発明は、従来技術が抱えるこのような問題点を解決することを課題とするものであり、それの目的とするところは、比較的少ない加工工数の下で、ガイド軸等の摩耗のおそれなしに、ピストンを常に円滑に、かつ正常に変位させることができる、簡単な構造の防振装置を提供するにある。   The object of the present invention is to solve such problems of the prior art, and the object of the present invention is to prevent the wear of the guide shaft and the like under a relatively small number of processing steps. In addition, an object of the present invention is to provide a vibration isolator having a simple structure capable of smoothly and normally displacing a piston.

この発明に係る防振装置は、振動の発生側および受動側のそれぞれに対するそれぞれの取付部材と、一方のコア状取付部材の周りに、他方のスリーブ状取付部材の一端部を、たとえば同軸状態で液密に連結するゴム弾性体と、スリーブ状取付部材の他端を液密に封止して、その取付部材の内側に密閉空間を画成するダイアフラムと、密閉空間の中間部、すなわち、スリーブ状取付部材の軸線方向の中間部に配設されて、液体を充填した密閉空間を、たとえば、ゴム弾性体側の主液室と、ダイアフラム側の副液室とに区画する流路構成部材とを具えるとともに、その流路構成部材を、スリーブ状取付部材の内周面にたとえば間接的に固定されて、主液室と副液室との連通をもたらす制限通路を形成する流路部分と、シリンダ内を、たとえばそれの中心軸線方向にストロークされて、流路部分を副液室にバイパスさせるバイパス路の開閉を司るピストンと、このピストンを、バイパス路を開放する方向に付勢するばね手段と、シリンダに、それの主液室に取付けられて、主液室内の液体のピストン側への流入を許容する逆止弁機構とで構成してなるものであって、シリンダに、ピストンの外周面と面接触するストローク案内面を設けるとともに、ピストンの直径の、ピストン高さに対する比を、とくにはピストンの小径化の下で、１．０以下としてなるものである。   The vibration isolator according to the present invention includes a mounting member for each of the vibration generation side and the passive side, and one end of the other sleeve-shaped mounting member around the one core-shaped mounting member, for example, in a coaxial state. A rubber elastic body that is liquid-tightly connected, a diaphragm that seals the other end of the sleeve-like mounting member in a liquid-tight manner, and defines a sealed space inside the mounting member, and an intermediate portion of the sealed space, that is, a sleeve A flow path constituting member that is disposed in an intermediate portion in the axial direction of the cylindrical mounting member and divides a sealed space filled with a liquid into, for example, a main liquid chamber on the rubber elastic body side and a sub liquid chamber on the diaphragm side. And a flow path portion that is fixed indirectly to the inner peripheral surface of the sleeve-like mounting member, for example, to form a restriction passage that provides communication between the main liquid chamber and the sub liquid chamber; In the cylinder, for example it A piston that is stroked in the direction of the central axis and controls the opening and closing of the bypass path that bypasses the flow path portion to the auxiliary liquid chamber, a spring means that biases the piston in the direction of opening the bypass path, and a cylinder, Stroke guide that is attached to the main liquid chamber and includes a check valve mechanism that allows inflow of liquid in the main liquid chamber to the piston side, and is in surface contact with the outer peripheral surface of the piston. In addition to providing a surface, the ratio of the piston diameter to the piston height is set to 1.0 or less, especially when the piston diameter is reduced.

ここで、「ピストンの直径」とは、ピストンが、角柱形状、角筒形状等の形態を有するものであるときは、そのピストンの外輪郭線に対する外接円直径をいうものとする。   Here, the “diameter of the piston” means a circumscribed circle diameter with respect to the outer contour line of the piston when the piston has a shape such as a prismatic shape or a rectangular tube shape.

ところで、小径化を図ったピストンは、シリンダの中心に対してオフセットさせて配設し、あるいは、ピストンと、ピストン側への液体の流入を許容する逆止弁機構とを相互にオフセットさせて配設する。 By the way, the piston with a reduced diameter is disposed offset from the center of the cylinder , or the piston and the check valve mechanism that allows the liquid to flow into the piston are offset from each other. you set.

そして、これらの場合には、逆止弁機構の、主液室との境界を特定する仕切蓋に、可撓膜体としてのメンブランを設けることが好ましい。   In these cases, it is preferable to provide a membrane as a flexible membrane body on the partition lid that specifies the boundary between the check valve mechanism and the main liquid chamber.

また好ましくは、シリンダおよび逆止弁機構の少なくとも一方に、ストローク端に達したピストンが衝接する緩衝部材を配設する。   Preferably, at least one of the cylinder and the check valve mechanism is provided with a cushioning member with which the piston reaching the stroke end comes into contact.

この発明に係る防振装置は、たとえば、比較的低い振動周波数（たとえば、９〜１５Ｈｚ）で、振幅の大きい、いわゆるシエイク振動、および、比較的高い振動周波数（たとえば、１８〜３０Ｈｚ）で、振幅の小さい、いわゆるアイドル振動のそれぞれに対しては、従来技術の場合と同様に、相互に異なった通路内での液体の液柱共振等に基いて、振動の防振および減衰機能を有効に発揮することができる。   The vibration isolator according to the present invention has, for example, a relatively low vibration frequency (for example, 9 to 15 Hz) and a large amplitude, so-called sway vibration, and a relatively high vibration frequency (for example, 18 to 30 Hz), and an amplitude. For each of the so-called idle vibrations, the vibration damping and damping functions are effectively demonstrated based on the liquid column resonance of the liquid in different passages, as in the case of the prior art. can do.

しかもここでは、シリンダに、ピストンの外周面と面接触するストローク案内面を設け、この案内面で、ピストンの円滑なる摺動をガイドすることで、従来技術で述べたガイド軸１２６および、プランジャ部材軸受穴１２５が不要となるので、同心加工は、シリンダのストローク案内面と、ピストン外周面との間で行うだけで済むことになって、加工工数を大きく低減させることができる。   In addition, here, the cylinder is provided with a stroke guide surface in surface contact with the outer peripheral surface of the piston, and the guide surface 126 guides the smooth sliding of the piston, whereby the guide shaft 126 and the plunger member described in the prior art are provided. Since the bearing hole 125 is not required, the concentric machining only needs to be performed between the stroke guide surface of the cylinder and the outer peripheral surface of the piston, so that the number of machining steps can be greatly reduced.

その上、この防振装置による、ストローク案内面とピストン外周面との接触面積は、従来技術の、ガイド軸１２６と軸受穴１２５との接触面積に比してはるかに大きくなるので、ピストン等の摩耗のおそれなしに、そのピストンを、常に円滑に、かつ、所期した通りに正確にストロークさせることができる。   In addition, the contact area between the stroke guide surface and the piston outer peripheral surface by the vibration isolator is much larger than the contact area between the guide shaft 126 and the bearing hole 125 of the prior art. The piston can always be smoothly and accurately stroked as expected without fear of wear.

そしてこのことは、ピストンの小径化の下で、ピストンの直径の、ピストン高さに対する比を１．０以下として、ピストンとシリンダ案内面との接触長さを十分長く確保して、その案内面での、ピストンの傾動変位に対する拘束度合を高めることによってより顕著なものとなる。   And this means that under the reduction of the diameter of the piston, the ratio of the piston diameter to the piston height is set to 1.0 or less, the contact length between the piston and the cylinder guide surface is sufficiently long, and the guide surface In this case, it becomes more remarkable by increasing the degree of restraint against the tilt displacement of the piston.

このような防振装置において、小径化したピストンを、シリンダの中心に対してオフセットさせて配設するときは、シリンダ内にフリースペースを確保して、他の通路部材等の、所要に応じた配置を可能とすることができる。   In such an anti-vibration device, when the piston with the reduced diameter is disposed offset from the center of the cylinder, a free space is ensured in the cylinder, and other passage members, etc. Placement can be possible.

またここで、ピストンと、逆止弁機構とを相互にオフセットさせて配設する場合は、シリンダ内にピストンを入れ込み配置するための、穿設等になる小さな寸法のシリンダ開口を、シリンダ頂壁の一部に偏せて形成することで、逆止弁機構を、そのシリンダ頂壁上に構成することが可能となり、これがため、逆止弁機構の弁体を、それの厚み方向に拘束するとともに、半径方向に位置決めする一対の保持部材のうち、シリンダ側に位置することとなるものをシリンダ頂壁によって肩代わりさせることが可能となるので、逆止弁機構の構造を、従来技術に比して簡単なものとすることができる。   Also, here, when the piston and the check valve mechanism are disposed offset from each other, a small-sized cylinder opening for drilling or the like for placing the piston in the cylinder is provided in the cylinder top wall. It is possible to configure the check valve mechanism on the cylinder top wall by biasing it to a part of the cylinder, and this restricts the valve body of the check valve mechanism in the thickness direction thereof. In addition, among the pair of holding members that are positioned in the radial direction, the one that is positioned on the cylinder side can be shouldered by the cylinder top wall. And simple.

そしてまた、ピストンを、シリンダの中心に対してオフセットさせて配設する場合および、ピストンと、逆止弁機構とを相互にオフセットさせて配設する場合のいずれにあっても、逆止弁機構の、主液室との境界を特定する仕切蓋に、アイドル振動（たとえば１８〜３０Ｈｚ）より周波数の高い高周波振動に対して撓み変形、弾性変形等して圧力変動の吸収に寄与する、膜体としてのメンブランを設けたときは、圧力応答精度を十分に高めるとともに、装置のチューニングの幅を大きく広げることができ、また、メンブランを外部に露出させて設ける場合に比して、損傷の発生のおそれを効果的に取り除くことができる。   In addition, the check valve mechanism can be used in any case where the piston is disposed offset with respect to the center of the cylinder and in the case where the piston and the check valve mechanism are disposed offset from each other. A film body that contributes to absorption of pressure fluctuations by bending deformation, elastic deformation, etc. with respect to high-frequency vibration having a frequency higher than that of idle vibration (for example, 18 to 30 Hz) on the partition lid that specifies the boundary with the main liquid chamber If the membrane is provided, the pressure response accuracy can be increased sufficiently and the tuning range of the device can be greatly expanded. In addition, the occurrence of damage can be reduced compared to the case where the membrane is exposed to the outside. The fear can be effectively removed.

図１はこの発明の基本形態を示す、中心軸線を含む縦断面図である。
図中１，２はそれぞれ、振動の発生側および受動側のそれぞれに固定される取付部材を示し、ここではたとえば、一方の取付部材１を、自動車のエンジン側に、ボルト等を介して連結されるコア状取付部材とし、他方の取付部材２を、自動車の車体側に、カップ状のホルダ等を介して連結されるスリーブ状取付部材とし、コア状取付部材１の周りに、スリーブ状取付部材２の上端部分を、ゴム弾性体３によって液密に連結して、このゴム弾性体３の外周面を、スリーブ状取付部材２からコア状取付部材１に向けて次第に先細りとする。 FIG. 1 is a longitudinal sectional view including a central axis showing a basic form of the present invention.
In the figure, reference numerals 1 and 2 denote attachment members fixed to the vibration generation side and the passive side, respectively. Here, for example, one attachment member 1 is connected to the engine side of the automobile via a bolt or the like. The other mounting member 2 is a sleeve-shaped mounting member connected to the vehicle body side via a cup-shaped holder or the like, and the sleeve-shaped mounting member 1 is provided around the core-shaped mounting member 1. The upper end portion of the rubber elastic body 3 is liquid-tightly connected by the rubber elastic body 3, and the outer peripheral surface of the rubber elastic body 3 is gradually tapered from the sleeve-shaped mounting member 2 toward the core-shaped mounting member 1.

またスリーブ状取付部材２の他端には、たとえば、支持リング４の内周面に加硫接着させてなるダイアフラム５を、ライニングゴム層を介して液密にかしめ固定することにより、スリーブ取付部材２の内側を密閉空間とする。   Further, for example, a diaphragm 5 formed by vulcanization and adhesion to the inner peripheral surface of the support ring 4 is fixed to the other end of the sleeve-like mounting member 2 by liquid-tight caulking through a lining rubber layer. The inside of 2 is a sealed space.

そしてこの密閉空間の中間部、いいかえれば、スリーブ状取付部材２の軸線方向の中間部には、液体を充填したその密閉空間を、図では、コア取付部材1側の主液室６と、それとは反対側の副液室７とに区画する流路構成部材８を、これもたとえば、ライニングゴム層を介した液密なかしめ固定によって配設し、この流路構成部材８の、軸線方向の変位を、支持リング４、および、その流路構成部材８よりコア状取付部材１側で、スリーブ状取付部材２に設けた括れ部２ａ、直接的には、その括れ部２ａより図の下方側に位置するライニングゴム層の小径段部３ａをもって拘束する。   The intermediate portion of this sealed space, in other words, the intermediate portion in the axial direction of the sleeve-like mounting member 2, the sealed space filled with the liquid, in the figure, the main liquid chamber 6 on the core mounting member 1 side, Is provided with a flow path component member 8 that is divided into the sub liquid chamber 7 on the opposite side, for example, by liquid-tight caulking and fixing via a lining rubber layer. Displacement of the support ring 4 and the flow path component 8 on the core-shaped mounting member 1 side, the constricted portion 2a provided on the sleeve-shaped mounting member 2, directly below the constricted portion 2a in the figure. It is restrained by the small diameter step 3a of the lining rubber layer located at the position.

ところで、ここにおける流路構成部材８は、外周面に、主液室６と副液室７との連通をもたらすべく、たとえば、二周弱の螺旋巻回構造になる、流路部分としての溝部９を設けたシリンダ１０を具え、このシリンダ１０は、流路構成部材８の、上述したような取付け姿勢の下で、溝部９とライニングゴム層とによって、両液室６，７の連通をもたらす二種類の制限通路１１，１２を成形する。
なお、流路部分は、シリンダ１０とは別体にて構成することも可能である。 By the way, the flow path component member 8 here has, for example, a groove portion as a flow path portion that has a spiral winding structure of a little less than two rounds in order to provide communication between the main liquid chamber 6 and the sub liquid chamber 7 on the outer peripheral surface. 9 is provided, and this cylinder 10 brings the fluid chambers 6 and 7 into communication with each other by the groove 9 and the lining rubber layer under the mounting posture of the flow path component member 8 as described above. Two types of restriction passages 11 and 12 are formed.
The flow path portion can be configured separately from the cylinder 10.

ここで、一方の制限通路１１は、図の上端側を主液室６に開口させた、図２に例示するような一本の螺旋溝部９の、断面積の大きい部分、図では、深さが一定で、広い溝幅W１を有する部分に延在して、たとえば、その広幅溝部分の溝底に設けた、好ましくは、その広幅溝部分の横断面積よりも大きな開口面積を有する、バイパス路としての、一のシリンダ貫通穴１３を経て、シリンダ内部から副液室７に到る流路からなり、他方の制限通路１２は、溝部９の、主液室６への開口部から、広い溝幅W１を有する部分を含むとともに、その広幅溝部分より下流側に存在する、狭い溝幅W２を有する部分を経て図の下端で副液室７に開口する、狭幅溝部分を通る流路からなる。 Here, one restricting passage 11 is a portion having a large cross-sectional area of one spiral groove portion 9 as illustrated in FIG. in but constant, extends to the portion having a wide groove width W 1, for example, provided in the groove bottom of the wide groove portion, preferably, it has an opening area larger than the cross-sectional area of the wide groove portion, a bypass As a passage, it consists of a flow path from the inside of the cylinder to the sub liquid chamber 7 through one cylinder through hole 13, and the other restricting passage 12 is wide from the opening of the groove 9 to the main liquid chamber 6. together includes a portion having a groove width W 1, the more wide groove portion located downstream side, open to the auxiliary liquid chamber 7 at the lower end of FIG via a portion having a narrow groove width W 2, through the narrow groove portion It consists of a flow path.

また、この流路構成部材８は、シリンダ１０内を、そこに設けたストローク案内面１０ａによって、シリンダ１０の中心軸線方向にガイドされて、図では上下方向にストロークして、前記貫通穴１３の開閉を司るピストン１４および、このピストン１４を、貫通穴１３を開放する向き、ここでは、主液室６側となる図の上方へ付勢するばね手段１５、たとえばコイルスプリングを具え、さらに、シリンダ１０に、それの主液室６側に取付けられて、主液室６内の液体の、図では底壁付きのカップ状をなすピストン１４側への流入のみを許容し、ピストン１４側から主液室６側への液体の流動を阻止する逆止弁機構１６とを具える。   Further, the flow path component member 8 is guided in the cylinder 10 by a stroke guide surface 10a provided in the cylinder 10 in the direction of the central axis of the cylinder 10 and strokes in the vertical direction in the drawing, A piston 14 that controls opening and closing, and a spring means 15 that biases the piston 14 in the direction in which the through hole 13 is opened, that is, the upper side of the figure on the main liquid chamber 6 side, such as a coil spring, are further provided. 10 is attached to the main liquid chamber 6 side of the main liquid chamber 6 to allow only the inflow of the liquid in the main liquid chamber 6 to the piston 14 side having a cup shape with a bottom wall in the figure. And a check valve mechanism 16 for preventing the liquid from flowing to the liquid chamber 6 side.

ここにおけるこの逆止弁機構１６は、図３に、シリンダ１０およびピストン１４等とともに分解斜視図で例示するように、一対の保持部材１７，１８および、それらの保持部材１７，１８によって、厚み方向および半径方向に拘束される、たとえばゴム製の、周辺部分が高い可撓性を有する弁体１９からなる。   The check valve mechanism 16 herein includes a pair of holding members 17 and 18 and the holding members 17 and 18 in the thickness direction as illustrated in FIG. 3 in an exploded perspective view together with the cylinder 10 and the piston 14 and the like. The valve body 19 is made of, for example, rubber, which is constrained in the radial direction, and has a highly flexible peripheral portion.

ここで、下方側の保持部材１７としての、たとえば金属製のホルダは、シリンダ１０内に嵌めこまれ、ピストン１４の頂面、図ではリング状をなす頂面に掛合して、そのピストン１４の上方への抜出し変位を拘束するとともに、弁体１９の、中央部分のボス状肉厚部を、中央貫通穴内に嵌め込まれて、弁体１９の半径方向位置を特定するべくも機能する。また、上方側の保持部材１８としての仕切蓋は、たとえば、シリンダ１０の上端部外周面に嵌め合わせ固定される金属フレームに、ゴムを加硫接着等させてなり、弁体１９の中央部分の、これもボス状の肉厚部を、中央貫通穴内に嵌め込まれて、弁体１９の半径方向位置を特定するとともに、下面をもって弁体１９の平坦上面に面接触して、弁体周辺部分の、図の上方側への反り変形を防止し、封入液体の、ピストン１４側から主液室６側への流動を阻止すべく機能する。   Here, a holder made of metal, for example, as the holding member 17 on the lower side is fitted into the cylinder 10 and is engaged with the top surface of the piston 14, which is a ring-shaped top surface in the drawing, and the piston 14. While restraining the upward displacement, the boss-like thick portion of the central portion of the valve body 19 is fitted into the central through hole, and functions to specify the radial position of the valve body 19. Moreover, the partition lid as the upper holding member 18 is formed by, for example, vulcanizing and bonding rubber to a metal frame fitted and fixed to the outer peripheral surface of the upper end of the cylinder 10. The boss-like thick portion is also fitted in the central through hole to specify the radial position of the valve body 19 and to make a surface contact with the flat upper surface of the valve body 19 with the lower surface. This functions to prevent warping deformation upward in the figure and to prevent the flow of the sealed liquid from the piston 14 side to the main liquid chamber 6 side.

この一方で、弁体１９は、その下面側では、中央部分から周縁に向けて次第に薄肉とされており、また、この弁体１９の周辺部分は、下方側の保持部材であるホルダ１７の上方側へ離隔させて配置されていることから、その弁体１９の周辺部分は、それの下方側への反り変形は許容されることになる。   On the other hand, the valve body 19 is gradually thinned from the central portion toward the periphery on the lower surface side, and the peripheral portion of the valve body 19 is located above the holder 17 which is a holding member on the lower side. Since the valve body 19 is disposed so as to be separated from the side, warpage deformation of the peripheral portion of the valve body 19 is allowed.

かくして、この逆止弁機構１６では、エンジンから防振装置に伝達される振動が、たとえば、シエイク振動のように低周波大振幅振動である場合、主液室６内の液体の加圧状態の下では、その液体は、上方側の保持部材としての仕切蓋１８に設けた開口１８ａを経て弁体１９を下方側へ押圧して、その弁体１９の周辺部分を下方側へ反らし変形させながら弁体１９の下面側へ流入することになる。そして、弁体１９の下面側へ流入したこの液体は、下方側の保持部材としてのホルダ１７に穿設した開口１７ａを経て、シリンダ１０の、ピストン収納部の周りの頂壁１０ｂ上へ流入し、その頂壁１０ｂ上からピストン１４のリング状頂面に設けた切欠き１４ａを経て、カップ状をなすピストン１４の内側へ流入し、これらのことは、主液室６内の液体が、液室容積が減少する向きのゴム弾性体３の変形に基いて加圧される度に繰返されることになる。   Thus, in the check valve mechanism 16, when the vibration transmitted from the engine to the vibration isolator is a low-frequency large-amplitude vibration such as a shake vibration, the liquid in the main liquid chamber 6 is in a pressurized state. Below, the liquid presses the valve body 19 downward through an opening 18a provided in the partition lid 18 as an upper holding member, and warps and deforms the peripheral portion of the valve body 19 downward. It flows into the lower surface side of the valve body 19. Then, the liquid that has flowed into the lower surface side of the valve body 19 flows onto the top wall 10b around the piston housing portion of the cylinder 10 through the opening 17a formed in the holder 17 as a holding member on the lower side. From the top wall 10b, through the notch 14a provided in the ring-shaped top surface of the piston 14, it flows into the inside of the cup-shaped piston 14, and this means that the liquid in the main liquid chamber 6 is liquid. This is repeated each time the pressure is applied based on the deformation of the rubber elastic body 3 in the direction in which the chamber volume decreases.

この一方で、シェイク振動の、主液室容積が増加する向きの変位によって、その主液室６が減圧雰囲気とされても、弁体１９の下面側へ一旦流入した液体は、弁体１９の逆止機能の下で、そのままそこに維持させることになる。   On the other hand, even if the main liquid chamber 6 is in a reduced pressure atmosphere due to the displacement of the shake vibration in the direction in which the main liquid chamber volume increases, the liquid once flowing into the lower surface side of the valve body 19 Under the check function, it will be maintained there.

従って、主液室６の繰返しの加圧によって弁体１９の下面側へ供給された液体は、加圧状態の主液室６内の液体の液圧と実質的に等しい液圧を有することになるので、ピストン１４を主液室６側へ付勢するばね手段１５のばね力を、このときのピストン圧下力より小さく設定しておくことで、ピストン１４は、シェイク振動時に、弁体の下面側へ供給された液体の圧力によって、ばね手段１５のばね力に抗して下降変位して、そのピストン１４の周面をもって、溝部９の底壁に形成した貫通穴１３と副液室７との、シリンダ１０内のピストンストロークスペースを介した連通を遮断することになる。   Therefore, the liquid supplied to the lower surface side of the valve body 19 by repeated pressurization of the main liquid chamber 6 has a liquid pressure substantially equal to the liquid pressure of the liquid in the main liquid chamber 6 in the pressurized state. Therefore, by setting the spring force of the spring means 15 that urges the piston 14 toward the main liquid chamber 6 side to be smaller than the piston rolling force at this time, the piston 14 can move to the lower surface of the valve body during shake vibration. Due to the pressure of the liquid supplied to the side, it is displaced downward against the spring force of the spring means 15, and the through hole 13 formed in the bottom wall of the groove portion 9 and the auxiliary liquid chamber 7 with the peripheral surface of the piston 14, The communication through the piston stroke space in the cylinder 10 is cut off.

これがため、その後の継続的なシェイク振動の入力に対しては、主および副液室６，７内の液体は、制限通路１２のみを通ってそれぞれの液室に流入出することなり、これにより、主には、制限通路１２の、予め選択された、断面積と長さとに由来する液柱共振に基いて、さらには、その制限通路１２を通る液体の粘性抵抗、圧力損失等に基いて、防振および減衰機能が発揮されることになる。   Therefore, for the subsequent continuous shake vibration input, the liquid in the main and sub liquid chambers 6 and 7 flows into and out of the respective liquid chambers only through the restriction passages 12. , Mainly based on the liquid column resonance derived from the cross-sectional area and length selected in advance of the restriction passage 12, and further based on the viscous resistance, pressure loss, etc. of the liquid passing through the restriction passage 12. Thus, the vibration-proof and damping functions are exhibited.

これに対し、エンジンからの伝達振動が、たとえばアイドル振動のように高周波小振幅振動である場合は、主液室６内の液体の加圧状態の下では、その主液室６内の液体は、同様にして、逆止弁機能１６の弁体１９の下面側へ供給されることになるも、このような、小振幅のアイドル振動によっては、主液室６内の液体および、弁体１９の下面側へ流入した液体の圧力はそれほど高くならない。   On the other hand, when the transmission vibration from the engine is high-frequency small-amplitude vibration such as idle vibration, the liquid in the main liquid chamber 6 is under pressure of the liquid in the main liquid chamber 6. Similarly, even if the check valve function 16 is supplied to the lower surface side of the valve body 19, the liquid in the main liquid chamber 6 and the valve body 19 are affected by such small amplitude idle vibration. The pressure of the liquid flowing into the lower surface side of the liquid does not increase so much.

従って、かかる場合は、ピストン１４を主液室６側へ付勢するばね手段１５のばね力を、アイドル振動時のピストン圧下力に打勝つ大きさに選択することにより、底壁付きのカップ状をなすピストン１４は、ばね手段１５のばね力に基き、その内部に流入した主液室内の液体を、ピストン１４の底壁に設けた絞り通路１４ｂを経て、ピストン１４のストロークスペース内へ流下させながら次第に上昇変位して、シリンダ１０の溝部９の底壁に設けた貫通穴１３を、図１に示すように開放して、その貫通穴１３と副液室７との、ピストン１４のストロークスペースを介した連通をもたらす。   Therefore, in such a case, by selecting the spring force of the spring means 15 for urging the piston 14 toward the main liquid chamber 6 so as to overcome the piston rolling force during idling vibration, a cup shape with a bottom wall is provided. Based on the spring force of the spring means 15, the piston 14 that forms the flow of the liquid in the main liquid chamber that has flowed into the piston 14 flows down into the stroke space of the piston 14 through the throttle passage 14 b provided in the bottom wall of the piston 14. While gradually moving upward, the through hole 13 provided in the bottom wall of the groove portion 9 of the cylinder 10 is opened as shown in FIG. 1, and the stroke space of the piston 14 between the through hole 13 and the auxiliary liquid chamber 7 is opened. Bring communication through.

このことによれば、アイドル振動の入力時には、主液室６と副液室７とは、溝部９の広幅部分から、貫通穴１３および、シリンダ１０内のピストンストロークスペースを通る制限通路１１によって相互に連通される他、溝部９の広幅部分および狭幅部分の両者を含む制限通路１２によってもまた相互に連通されることになるも、主および副液室６，７内のそれぞれの液体は、主には、流動抵抗の少ない制限通路１１を経て流動することになるので、アイドル振動に対するの防振および減衰作用は、制限通路１１内での液柱共振を主として行われることになる。   According to this, at the time of input of idle vibration, the main liquid chamber 6 and the sub liquid chamber 7 are mutually connected from the wide portion of the groove portion 9 by the through hole 13 and the restriction passage 11 passing through the piston stroke space in the cylinder 10. In addition to being communicated with each other by the restricting passage 12 including both the wide portion and the narrow portion of the groove 9, the respective liquids in the main and sub liquid chambers 6 and 7 are Since the fluid flows mainly through the restricting passage 11 having a low flow resistance, the anti-vibration and damping action against the idle vibration is mainly performed by liquid column resonance in the restricting passage 11.

以上のような防振装置において、ここでは、シリンダ１０に、小径化したピストン１４の外周面と面接触するストローク案内面１０ａを設けるとともに、ピストン１４の直径Ｄの、ピストン高さＨに対する比（Ｄ／Ｈ）を１．０以下、より好ましくは、０．１〜０．５として、そのストローク案内面１０ａをもって、ピストン１４の円滑なる摺動変位をガイドすることにより、装置それ自体の外形寸法等はそのままに、従来技術で述べたガイド軸および、ピストンの軸受穴が不要となり、ピストン外周面とストローク案内面１０ａとを同心加工するだけで、ピストン１４を所期した通りに確実に変位させることができるので、従来技術に比して、ピストン１４の所要のストロークのための加工工数を大きく低減させることができる。   In the vibration isolator as described above, here, the cylinder 10 is provided with the stroke guide surface 10a in surface contact with the outer peripheral surface of the piston 14 having a reduced diameter, and the ratio of the diameter D of the piston 14 to the piston height H ( D / H) is set to 1.0 or less, more preferably 0.1 to 0.5, and the smooth guide displacement of the piston 14 is guided by the stroke guide surface 10a, whereby the external dimensions of the device itself. The guide shaft and the piston bearing hole described in the prior art are no longer necessary, and the piston 14 is reliably displaced as intended simply by concentrating the piston outer peripheral surface and the stroke guide surface 10a. Therefore, compared with the prior art, the number of processing steps for the required stroke of the piston 14 can be greatly reduced.

しかも、ピストン外周面と、ストローク案内面１０ａとの接触面積は、従来技術の、ピストンの中央部に貫通するガイド軸と、軸受穴との接触面積よりも必然的に大きくなることから、ピストン等の摩耗のおそれなしに、ピストンを、長期間にわたって円滑に、かつ、常に正確にストロークさせることができる。   Moreover, since the contact area between the piston outer peripheral surface and the stroke guide surface 10a is inevitably larger than the contact area between the guide shaft penetrating the central portion of the piston and the bearing hole in the prior art, the piston or the like The piston can be smoothly and accurately stroked over a long period of time without fear of wear.

この場合、上記の比（Ｄ／Ｈ）が１．０を越えると、ピストン１４の直径が大きくなりすぎることにより、ストローク案内面１０ａだけによっては、ピストン１４の傾動変位を十分に拘束することが難しく、その傾動変位の発生に由来する、ピストン１４の、ストローク案内面１０ａへの引っ掛りのおそれが生じ易くなる。   In this case, if the ratio (D / H) exceeds 1.0, the diameter of the piston 14 becomes too large, so that only the stroke guide surface 10a can sufficiently restrain the tilt displacement of the piston 14. It is difficult to easily cause the piston 14 to be caught on the stroke guide surface 10a due to the occurrence of the tilt displacement.

なお、図１中２０は、シリンダ１０のストローク案内面１０ａの下端に形成した、開口付きの底壁上に配置した、ゴム製、プラスチック製等の、ここではリング状をなす緩衝部材を示し、この緩衝部材２０は、その底壁の座ぐり部内に着座させたばね手段１５によって上昇方向に付勢されるピストン１４が、その付勢力に抗して下降変位された場合にピストン１４の下面に当接して、そのピストン１４の、上記底壁への衝突衝撃および、衝突音の発生のそれぞれを緩和するべく機能する。   In FIG. 1, reference numeral 20 denotes a cushioning member having a ring shape, such as rubber or plastic, disposed on the bottom wall with an opening formed at the lower end of the stroke guide surface 10 a of the cylinder 10. The shock absorbing member 20 contacts the lower surface of the piston 14 when the piston 14 urged in the upward direction by the spring means 15 seated in the counterbore portion of the bottom wall is displaced downward against the urging force. In contact therewith, the piston 14 functions to alleviate the impact of the impact on the bottom wall and the generation of the impact sound.

ところで、図に示すところでは、ピストン１４を、シリンダ１０の中央部に同心配置することとしているも、ピストン１４は、シリンダ１０の中心軸線に対して所要の方向にオフセットさせて配置することもでき、このことによれば、シリンダ１０内に比較的大きなフリースペースを確保して、そこに、所要に応じた通路部材等を配置することが可能となる。   By the way, as shown in the figure, the piston 14 is concentrically arranged at the center of the cylinder 10, but the piston 14 can also be arranged offset in a required direction with respect to the central axis of the cylinder 10. According to this, it is possible to secure a relatively large free space in the cylinder 10 and to arrange a passage member or the like according to necessity.

また、以上に述べたところでは、上下の相対関係の下に、ともに同心配置した逆止弁機構とピストンとの相互を、たとえば、図４に、流路構成部材を分解斜視図で例示するようにオフセットさせて配設することもできる。   In addition, as described above, the check valve mechanism and the piston, which are concentrically arranged together in the upper and lower relative relationship, are illustrated as an example in FIG. It is also possible to arrange them with an offset.

ここでは、シリンダ１０の外周面の溝部９等はそのままに、シリンダ頂壁２１の、いずれかの縁部に偏せて、ピストン１４を収納配置するためのシリンダ開口２２を設けるとともに、そのシリンダ頂壁２１の、シリンダ開口２２の近傍部分に、逆止弁機構の、小径化を図った弁体２３の位置決め窪み２４を設け、また、シリンダ１０の上端部外周面に嵌め合わせ固定される仕切蓋２５を設ける。   Here, the groove portion 9 and the like on the outer peripheral surface of the cylinder 10 is left as it is and is biased to any edge portion of the cylinder top wall 21 to provide a cylinder opening 22 for housing and arranging the piston 14, and In the vicinity of the cylinder opening 22 of the wall 21, there is provided a positioning recess 24 of the valve body 23 for reducing the diameter of the check valve mechanism, and a partition lid fitted and fixed to the outer peripheral surface of the upper end portion of the cylinder 10. 25 is provided.

この仕切蓋２５は、前述した仕切蓋１８と同様に、シリンダ１０にかしめ固定等される金属フレームに、ゴムを加硫接着等させてなり、この仕切蓋２５もまた、弁体２３のボス状肉厚部を嵌め込む貫通穴２５ａおよび、この貫通穴２５ａの周りにあって、弁体２３の周辺部分に、主液室６内の液体の液圧を作用させるための複数個の開口２５ｂを有する。   The partition lid 25 is formed by vulcanizing and bonding rubber to a metal frame that is caulked and fixed to the cylinder 10 in the same manner as the partition lid 18 described above. A through hole 25a into which the thick wall portion is fitted, and a plurality of openings 25b around the through hole 25a for allowing the liquid pressure in the main liquid chamber 6 to act on the peripheral portion of the valve body 23. Have.

このような流路構成部材は、図５に縦断面図で示すように組立てることができ、とくに、弁体２３の中央部分の、下面側のボス状肉厚部を、シリンダ頂壁２１に設けた位置決め窪み２４に直接的に嵌め込んで、その弁体２３の半径方向の位置決めを行う場合には、前述した逆止弁機構１６の、保持部材１７としての金属製等のホルダを不要ならしめて、部品点数の低減を図ることができる。   Such a flow path component can be assembled as shown in a longitudinal sectional view in FIG. 5. In particular, a boss-like thick portion on the lower surface side of the central portion of the valve body 23 is provided on the cylinder top wall 21. When the valve body 23 is positioned in the radial direction by directly fitting into the positioning recess 24, a metal holder or the like as the holding member 17 of the check valve mechanism 16 described above is unnecessary. The number of parts can be reduced.

そして、この流路構成部材によってもまた、図５に示すようなそれの組立て状態で、弁体２３の中央部分の、上下のボス状肉厚部を、仕切壁２５の貫通穴２５ａおよび、シリンダ頂壁２１の位置決め窪み２４のそれぞれに嵌め込むとともにそれらの間に拘束し、また、弁体２３の上面を、仕切壁２５の下面に面接触させて逆止機能の発揮を担保し、そして、シリンダ開口２２内に収納配置した、直径Ｄの、高さＨに対する比（Ｄ／Ｈ）が１．０以下の小径ピストン１４のストロークを、その開口２２の周壁としてのストローク案内面により、両者の面接触下でガイドするとともに、そのピストン１４を、ばね力を前述したように設定したばね手段１５によって、溝部底壁の貫通穴１３を開放する向きに、図の上方へ付勢することにより、前述した流路構成部材８と同様の機能を発揮させることができる。   And also with this flow path component member, in the assembled state as shown in FIG. 5, the upper and lower boss-like thick portions of the central portion of the valve body 23 are replaced with the through holes 25a of the partition wall 25 and the cylinders. The positioning recesses 24 of the top wall 21 are fitted into the positioning recesses 24 and restrained between them, and the upper surface of the valve body 23 is brought into surface contact with the lower surface of the partition wall 25 to ensure the performance of the check function. The stroke of the small-diameter piston 14 accommodated in the cylinder opening 22 and having a ratio of the diameter D to the height H (D / H) of 1.0 or less is reduced by a stroke guide surface as a peripheral wall of the opening 22. While guiding under surface contact, the piston 14 is urged upward in the figure by a spring means 15 whose spring force is set as described above in a direction to open the through hole 13 in the groove bottom wall, Above It can exhibit the same function as the other flow path constituting member 8.

なお、図５に示すところでは、ピストン１４の下降ストロークエンドに、先に述べたと同様のリング状の緩衝部材２０を配設することに加え、ピストン１４の上昇ストロークエンドにもまた、仕切蓋２５に一体形成してなる緩衝部材２６を設け、これにより、ピストン１４がばね手段１５によって上昇限位置に復帰されるに当っての、衝突衝撃を緩和し、衝突音を低減させることにしているので、この流路構成部材の適用下で、主液室６内の液圧増加に基いて、その主液室６内の液体を、弁体２３の下面側を経てピストン１４の内側へ流入させるためには、ピストン１４のリング状の頂面に当接する緩衝部材２６に、ピストン１４の内側への液体の供給を許容する切欠き流路を設けることが必要になる。   5, in addition to disposing the same ring-shaped cushioning member 20 as described above at the descending stroke end of the piston 14, the partition lid 25 is also provided at the ascending stroke end of the piston 14. The shock absorbing member 26 formed integrally with the shock absorber 26 is provided so that the impact of the piston 14 when the piston 14 is returned to the ascending limit position by the spring means 15 is mitigated and the impact noise is reduced. In order to cause the liquid in the main liquid chamber 6 to flow into the inside of the piston 14 through the lower surface side of the valve body 23 based on the increase in the liquid pressure in the main liquid chamber 6 under the application of this flow path component. In this case, it is necessary to provide a notch flow path that allows the supply of liquid to the inside of the piston 14 in the buffer member 26 that contacts the ring-shaped top surface of the piston 14.

そしてさらに、このような流路構成部材および／または、ピストンをシリンダの中心に対してオフセットさせて設けた流路構成部材にあっては、逆止弁機構の、主液室６との境界を特定する仕切蓋、図６に平面図で示すところでは仕切蓋２５の、弁体２３およびピストン１４のいずれの配設位置とも重ならない部分に、たとえば、金属フレームへの加硫接着ゴムのゴム厚みをとくに薄くすることによって形成できるメンブラン２７を設けることが好ましく、このメンブラン２７を、制限通路１１，１２内を液体が流動し得ないほどの高周波振動の、防振装置への入力に際して、主液室６内の液体圧力の増減に応じて振動させて、主液室６内の液体圧力の増減分をそのメンブラン２７の変形によって吸収するときは、防振装置が、振動の低減等に寄与し得ない剛状態となるのを効果的に防ぐことができる。   Furthermore, in such a flow path component and / or a flow path structure member provided by offsetting the piston with respect to the center of the cylinder, the boundary between the check valve mechanism and the main liquid chamber 6 is defined. For example, the rubber thickness of the vulcanized adhesive rubber to the metal frame is provided on a part of the partition lid that is not overlapped with any position of the valve body 23 and the piston 14 as shown in the plan view of FIG. It is preferable to provide a membrane 27 that can be formed by reducing the thickness of the membrane, and this membrane 27 is used as a main liquid when inputting high-frequency vibrations such that the liquid cannot flow in the restriction passages 11 and 12 to the vibration isolator. When vibration is caused in accordance with the increase or decrease of the liquid pressure in the chamber 6 and the increase or decrease in the liquid pressure in the main liquid chamber 6 is absorbed by the deformation of the membrane 27, the vibration isolator reduces vibration, etc. Can be prevented from becoming rigid state not contribute effectively.

なおこの場合、メンブラン２７の十分大きな変形を許容するためには、図４に示すところから明らかなように、シリンダ頂壁２１に、メンブラン２７と対応する形態の抜き穴２８を設けることが好ましい。   In this case, in order to allow a sufficiently large deformation of the membrane 27, it is preferable to provide a punch hole 28 in a form corresponding to the membrane 27 in the cylinder top wall 21, as is apparent from FIG.

このように、主液室６の境界を特定する仕切蓋２５にメンブラン２７を設けたときは、先にも述べたように、すぐれた応答性の下で、防振装置の圧力変動を効果的に吸収することができ、装置のチューニングの自由度を大きく広げることができる。   Thus, when the membrane 27 is provided in the partition lid 25 that specifies the boundary of the main liquid chamber 6, as described above, the pressure fluctuation of the vibration isolator is effectively reduced with excellent responsiveness. The degree of freedom in tuning the device can be greatly expanded.

この発明の基本形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows the basic form of this invention. シリンダの外周面の螺旋溝部を例示する図である。It is a figure which illustrates the spiral groove part of the outer peripheral surface of a cylinder. 逆止弁機構を示す分解斜視図である。It is a disassembled perspective view which shows a non-return valve mechanism. 流路構成部材の変更例を示す分解斜視図である。It is a disassembled perspective view which shows the example of a change of a flow-path structural member. 図４に示す流路構成部材を組立て状態で示す縦断面図である。It is a longitudinal cross-sectional view which shows the flow-path structural member shown in FIG. 4 in an assembly state. 仕切蓋の変更例を示す平面図である。It is a top view which shows the example of a change of a partition lid. 従来技術を示す縦断面図である。It is a longitudinal cross-sectional view which shows a prior art.

符号の説明Explanation of symbols

１ コア状取付部材
２ スリーブ状取付部材
３ ゴム弾性体
４ 支持リング
５ ダイアフラム
６ 主液室
７ 副液室
８ 流路構成部材
９ 溝部
１０ シリンダ
１０ａ ストローク案内図
１０ｂ 頂壁
１１，１２ 制限通路
１３ 貫通穴
１４ ピストン
１４ａ 切欠き
１４ｂ 絞り通路
１５ ばね手段
１６ 逆止弁機構
１７ ホルダ
１７ａ，１８ａ 開口
１８，２５ 仕切蓋
１９，２３ 弁体
２０，２６ 緩衝部材
２１ シリンダ頂壁
２２ シリンダ開口
２４ 位置決め窪み
２５ａ 貫通穴
２５ｂ 開口
２７ メンブラン
２８ 抜き穴
Ｗ１ 広い溝幅
Ｗ２ 狭い溝幅
Ｄ 直径
Ｈ ピストン高さ DESCRIPTION OF SYMBOLS 1 Core-shaped attachment member 2 Sleeve-like attachment member 3 Rubber elastic body 4 Support ring 5 Diaphragm 6 Main liquid chamber 7 Sub liquid chamber 8 Flow path component 9 Groove part 10 Cylinder 10a Stroke guide figure 10b Top wall 11, 12 Restriction passage 13 Through Hole 14 Piston 14a Notch 14b Restriction passage 15 Spring means 16 Check valve mechanism 17 Holders 17a and 18a Openings 18 and 25 Partition lids 19 and 23 Valve body 20 and 26 Buffer member 21 Cylinder top wall 22 Cylinder opening 24 Positioning recess 25a Through Hole 25b Opening 27 Membrane 28 Punching hole W 1 Wide groove width W 2 Narrow groove width D Diameter H Piston height

Claims (4)

振動の発生側および受動側へのそれぞれの取付部材と、一方のコア状取付部材の周りに、他方のスリーブ状取付部材の一端部を液密に連結するゴム弾性体と、スリーブ状取付部材の他端を液密に封止して、その取付部材の内側に密閉空間を画成するダイアフラムと、密閉空間の中間部に配設されて、液体を充填したその密閉空間を、主液室と副液室とに区画する流路構成部材とを具え、この流路構成部材を、スリーブ状取付部材の内周面に固定されて主液室と副液室との連通をもたらす制限通路を形成する流路部分と、流路部分と副液室とのバイパス路の開閉を司る、シリンダ内でストロークされるピストンと、バイパス路を開放する向きに該ピストンを付勢するばね手段と、主液室内の液体のピストン側への流入を許容する、主液室側に取付けられた逆止弁機構とで構成してなる防振装置であって、
シリンダに、ピストンの外周面と接触するストローク案内面を設けるとともに、ピストンの直径の、ピストン高さに対する比を１．０以下とし、ピストンを、シリンダの中心に対して、オフセットさせて配設してなる防振装置。 Each of the vibration generating side and passive side mounting members, a rubber elastic body for liquid-tightly connecting one end of the other sleeve-shaped mounting member around one core-shaped mounting member, and a sleeve-shaped mounting member The other end is liquid-tightly sealed, a diaphragm that defines a sealed space inside the mounting member, and the sealed space that is disposed in the middle of the sealed space and is filled with liquid is separated from the main liquid chamber. A flow path component that divides into a secondary liquid chamber, and the flow path component is fixed to the inner peripheral surface of the sleeve-shaped mounting member to form a restriction passage that provides communication between the main liquid chamber and the secondary liquid chamber A flow path portion that opens and closes the bypass path between the flow path portion and the sub liquid chamber, a piston that is stroked in the cylinder, a spring means that biases the piston in a direction to open the bypass path, and a main liquid Allow the liquid in the room to flow into the piston side, allowing it to flow into the main liquid chamber. A vibration damping device comprising constituted by the vignetting the check valve mechanism,
The cylinder is provided with a stroke guide surface that comes into contact with the outer peripheral surface of the piston, and the ratio of the piston diameter to the piston height is set to 1.0 or less, and the piston is offset from the center of the cylinder. consisting of Te anti-vibration device. 振動の発生側および受動側へのそれぞれの取付部材と、一方のコア状取付部材の周りに、他方のスリーブ状取付部材の一端部を液密に連結するゴム弾性体と、スリーブ状取付部材の他端を液密に封止して、その取付部材の内側に密閉空間を画成するダイアフラムと、密閉空間の中間部に配設されて、液体を充填したその密閉空間を、主液室と副液室とに区画する流路構成部材とを具え、この流路構成部材を、スリーブ状取付部材の内周面に固定されて主液室と副液室との連通をもたらす制限通路を形成する流路部分と、流路部分と副液室とのバイパス路の開閉を司る、シリンダ内でストロークされるピストンと、バイパス路を開放する向きに該ピストンを付勢するばね手段と、主液室内の液体のピストン側への流入を許容する、主液室側に取付けられた逆止弁機構とで構成してなる防振装置であって、Each of the vibration generating side and passive side mounting members, a rubber elastic body for liquid-tightly connecting one end of the other sleeve-shaped mounting member around one core-shaped mounting member, and a sleeve-shaped mounting member The other end is liquid-tightly sealed, a diaphragm that defines a sealed space inside the mounting member, and the sealed space that is disposed in the middle of the sealed space and is filled with liquid is separated from the main liquid chamber. A flow path component that divides into a secondary liquid chamber, and the flow path component is fixed to the inner peripheral surface of the sleeve-shaped mounting member to form a restriction passage that provides communication between the main liquid chamber and the secondary liquid chamber A flow path portion that opens and closes the bypass path between the flow path portion and the sub liquid chamber, a piston that is stroked in the cylinder, a spring means that biases the piston in a direction to open the bypass path, and a main liquid Allow the liquid in the room to flow into the piston side, allowing it to flow into the main liquid chamber. A vibration damping device comprising constituted by the vignetting the check valve mechanism,
シリンダに、ピストンの外周面と接触するストローク案内面を設けるとともに、ピストンの直径の、ピストン高さに対する比を１．０以下とし、ピストンと逆止弁機構とを相互にオフセットさせて配設してなる防振装置。  The cylinder is provided with a stroke guide surface that comes into contact with the outer peripheral surface of the piston, the ratio of the piston diameter to the piston height is 1.0 or less, and the piston and the check valve mechanism are offset from each other. Anti-vibration device. 逆止弁機構の、主液室との境界を特定する仕切蓋にメンブランを設けてなる請求項１もしくは２に記載の防振装置。The vibration isolator according to claim 1 or 2, wherein the check valve mechanism is provided with a membrane on a partition lid that specifies a boundary with the main liquid chamber. シリンダおよび逆止弁機構の少なくとも一方に、ストローク端に達したピストンが衝接する緩衝部材を配設してなる請求項１〜３のいずれかに記載の防振装置。The vibration isolator according to any one of claims 1 to 3, wherein at least one of the cylinder and the check valve mechanism is provided with a buffer member that comes into contact with the piston that reaches the stroke end.
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