JP2008121811A - Fluid-sealed vibration isolator - Google Patents

Fluid-sealed vibration isolator Download PDF

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JP2008121811A
JP2008121811A JP2006307529A JP2006307529A JP2008121811A JP 2008121811 A JP2008121811 A JP 2008121811A JP 2006307529 A JP2006307529 A JP 2006307529A JP 2006307529 A JP2006307529 A JP 2006307529A JP 2008121811 A JP2008121811 A JP 2008121811A
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fluid
flexible rubber
rubber film
opening window
chamber
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Takanobu Minamino
高伸 南野
Jun Nakano
潤 中野
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Sumitomo Riko Co Ltd
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Sumitomo Riko Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid-sealed vibration isolator of a novel structure which can advantageously exhibit a vibration isolating effect against the vibration of a plurality of frequencies or the vibration of a wide-band frequency while being simplified in structure. <P>SOLUTION: An opening window 30 serving as one liquid chamber formed by connecting a pressure receiving chamber 50 and an equilibrium chamber 52 to each other is formed at a partitioning member 24, the opening window 30 is kept in a closed state by pressing the central part 82 of a flexible rubber film 38 against the opening peripheral part of the opening window 30 of the partitioning member 24 by using an output member 62 of an air-pressure type actuator 58 which is arranged at a side opposite to the equilibrium chamber 52 with the flexible rubber film 38 in between, the elastic deformation of the inside of a recess 84 of the flexible rubber film 38 is permitted by forming the recess 84 on the tip face of the output member 62, and a liquid-pressure absorbing mechanism with a deformation-amount limit mechanism is arranged which limits the amount of the elastic deformation of the flexible rubber film 38 by making the flexible rubber film 38 abut on the inside face of the recess 84. By this, a valve body containing the liquid-pressure absorbing mechanism is arranged which opens and closes the opening window 30 by the operation of the air-pressure type actuator 58. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、内部に封入された非圧縮性流体の流動作用に基づいて防振効果を得るようにした流体封入式防振装置に係り、特に、非圧縮性流体が封入された受圧室と平衡室をオリフィス通路を通じて相互に連通せしめた流体封入式防振装置に関するものである。   The present invention relates to a fluid-filled vibration isolator that obtains a vibration-proof effect based on the flow action of an incompressible fluid enclosed therein, and in particular, is balanced with a pressure receiving chamber filled with the incompressible fluid. The present invention relates to a fluid-filled vibration isolator in which chambers communicate with each other through an orifice passage.

従来から、振動伝達系を構成する部材間に介装される防振連結体や防振支持体の一種として、内部に封入された非圧縮性流体の共振作用等の流動作用に基づいて防振効果を得るようにした流体封入式の防振装置が知られている。この流体封入式防振装置は、第一の取付部材が筒状の第二の取付部材の軸方向一方の開口部側に離隔配置されて、それら第一の取付部材と第二の取付部材が本体ゴム弾性体で連結されていると共に、第二の取付部材の軸方向他方の開口部が可撓性膜で覆蓋されていることで、本体ゴム弾性体と可撓性膜の間に非圧縮性流体が封入された流体室を備えている。また、第二の取付部材に支持された仕切部材で流体室が仕切られて、流体室における仕切部材を挟んだ両側に壁部の一部が本体ゴム弾性体で構成された受圧室と壁部の一部が可撓性膜で構成された平衡室が形成され、それら受圧室と平衡室が仕切部材に形成されたオリフィス通路によって相互に連通された構造を呈している。このような構造によれば、振動入力に伴い受圧室と平衡室の間に相対的な圧力変動の差が生じて、オリフィス通路を通じての流体の流動量が確保されることとなり、かかる流体の共振作用等の流動作用に基づいて防振効果が得られるようになっている。例えば、特許文献1(特開平08−028623号公報)に示されているものが、それであり、自動車用のエンジンマウントやボデーマウント、デフマウントの他サスペンションメンバマウント等への適用が検討されている。   Conventionally, as a kind of anti-vibration coupling body and anti-vibration support body interposed between members constituting the vibration transmission system, anti-vibration is based on the flow action such as resonance action of incompressible fluid enclosed inside. 2. Description of the Related Art A fluid-filled vibration isolator that is effective is known. In this fluid-filled vibration isolator, the first mounting member is spaced apart on the one axial side opening side of the cylindrical second mounting member, and the first mounting member and the second mounting member are It is connected with the main rubber elastic body, and the other opening in the axial direction of the second mounting member is covered with a flexible film, so that it is not compressed between the main rubber elastic body and the flexible film. A fluid chamber in which a sexual fluid is sealed. In addition, the fluid chamber is partitioned by the partition member supported by the second mounting member, and the pressure receiving chamber and the wall portion in which part of the wall portion is formed of a main rubber elastic body on both sides of the partition member in the fluid chamber An equilibrium chamber made of a flexible membrane is formed, and the pressure receiving chamber and the equilibrium chamber communicate with each other through an orifice passage formed in the partition member. According to such a structure, a relative pressure fluctuation difference is generated between the pressure receiving chamber and the equilibrium chamber in accordance with the vibration input, and the amount of fluid flowing through the orifice passage is ensured. An anti-vibration effect can be obtained based on a fluid action such as an action. For example, Patent Document 1 (Japanese Patent Application Laid-Open No. 08-028623) discloses that, and application to an engine mount, a body mount, a differential mount for automobiles, and other suspension member mounts is being studied. .

ところが、特許文献1に示される従来構造の流体封入式防振装置では、オリフィス通路を流動せしめられる流体の共振作用に基づいて発揮される防振効果が、予めオリフィス通路がチューニングされた比較的に狭い周波数域に限られるため、要求される高度な防振特性に対応出来ない問題があった。   However, in the conventional fluid-filled vibration isolator shown in Patent Document 1, the vibration isolation effect that is exhibited based on the resonance action of the fluid that flows through the orifice passage is relatively high when the orifice passage is tuned in advance. Since it is limited to a narrow frequency range, there is a problem that it cannot cope with the required advanced anti-vibration characteristics.

そこで、特許文献2(特開平08−270718号公報)には、互いに異なる周波数域にチューニングした第一及び第二のオリフィス通路を設けると共に、高い周波数域にチューニングした方のオリフィス通路の平衡室への開口部を可撓性膜からなる弁体で開閉可能としたものが提案されている。これによれば、防振すべき振動に応じて第二のオリフィス通路を連通状態と遮断状態に切り換えて、二つのオリフィス通路を選択的に機能させることにより、二つの周波数域の振動に対する防振効果が得られることとなる。   Therefore, in Patent Document 2 (Japanese Patent Laid-Open No. 08-270718), the first and second orifice passages tuned to different frequency ranges are provided, and the equilibrium chamber of the orifice passage tuned to the higher frequency range is provided. Have been proposed that can be opened and closed with a valve body made of a flexible membrane. According to this, the second orifice passage is switched between the communication state and the cutoff state according to the vibration to be vibration-isolated, and the two orifice passages are selectively functioned to thereby prevent vibration against vibrations in two frequency ranges. An effect will be acquired.

しかしながら、近年では一層高度な防振性能が要求されるようになってきており、特許文献2に記載の流体封入式防振装置でも、要求される防振性能を未だ十分に実現できない場合がある。具体的には、一般に自動車のエンジンマウントには、その要求される防振性能として、自動車の走行時におけるエンジンシェイク等の低周波大振幅振動に対する防振性能(高減衰効果)と走行こもり音等の高周波小振幅振動に対する防振性能(振動絶縁効果)、更に自動車の停車時におけるアイドリング振動等の中周波中振幅振動に対する防振性能(振動絶縁効果)が、それぞれ要求される。   However, in recent years, a higher level of vibration isolation performance has been demanded, and even with the fluid-filled vibration isolation device described in Patent Document 2, the required vibration isolation performance may still not be sufficiently realized. . Specifically, in general, engine mounts for automobiles are required to have anti-vibration performance (high damping effect) against low-frequency large-amplitude vibrations such as engine shakes when the automobile is running, running noise, etc. Are required to have anti-vibration performance (vibration insulation effect) against high-frequency, small-amplitude vibration of the vehicle, and further, anti-vibration performance (vibration insulation effect) against medium-frequency medium amplitude vibration such as idling vibration when the vehicle is stopped.

このような要求特性に対して、上述の特許文献2に記載の従来構造の防振装置では、二つのオリフィス通路がそれぞれチューニングされた二種類の周波数域の振動に対してしか有効な防振効果を得ることが出来なかった。しかも、二つのオリフィス通路を形成するために、受圧室と平衡室を仕切る仕切部材の構造が複雑となり、製造作業が面倒で製造コストも高くなるという問題があった。   With respect to such required characteristics, the vibration isolator having the conventional structure described in Patent Document 2 described above is effective only for vibrations in two types of frequency ranges in which the two orifice passages are respectively tuned. Could not get. In addition, since the two orifice passages are formed, the structure of the partition member that partitions the pressure receiving chamber and the equilibrium chamber is complicated, and there is a problem that the manufacturing operation is troublesome and the manufacturing cost is increased.

なお、本出願人は、先に、特許文献3(特開平10−089402号公報)において、互いに異なる周波数域にチューニングした二つのオリフィス通路のうち高周波側域にチューニングしたオリフィス通路の開口部をゴム膜で開閉することにより、かかる高周波側チューニングされたオリフィス通路による低動ばね作用が発揮される周波数域を二つの異なる周波数域で選択的に発現可能とした、改良された構造の流体封入式防振装置を提案した。この流体封入式防振装置によれば、低周波側チューニングされたオリフィス通路によってエンジンシェイク等の低周波振動に対する防振効果を得ることが出来ると共に、高周波側オリフィス通路の閉塞状態によってアイドリング振動等の中〜高周波数域で二つの異なる周波数域の振動に対する防振効果も得ることが出来るのである。   In addition, the applicant of the present invention previously described in Patent Document 3 (Japanese Patent Application Laid-Open No. 10-089402), the opening of the orifice passage tuned to the high frequency side region of the two orifice passages tuned to different frequency regions is a rubber. By opening and closing with a membrane, a fluid-filled type anti-blocking structure with an improved structure that can selectively express in two different frequency ranges the frequency range where the low dynamic spring action is exhibited by the high-frequency side tuned orifice passage. A vibration device was proposed. According to this fluid-filled vibration isolator, it is possible to obtain an anti-vibration effect against low-frequency vibration such as engine shake by the low-frequency side tuned orifice passage, and idling vibration or the like depending on the closed state of the high-frequency side orifice passage. It is also possible to obtain an anti-vibration effect against vibrations in two different frequency ranges in the medium to high frequency range.

ところが、特許文献3で開示した流体封入式防振装置においては、高周波側チューニングされたオリフィス通路が連通せしめられた平衡室の壁ばね剛性を択一的に切り換えることにより、かかるオリフィス通路のチューニング周波数を移行させるものであって、オリフィス通路自体の通路長さや通路断面積は一定である。それ故、この高周波側オリフィス通路を開閉させても、その防振効果が発揮される周波数域を大きく変化させることが難しかった。従って、例えば自動車の停車時に問題となる中周波数域のアイドリング振動と、走行時に問題となる高周波数域の中〜高速走行こもり音とを、かかるオリフィス通路の開閉によって両立して発現させることなどは、極めて困難だった。しかも、二つのオリフィス通路を形成する必要があるから、仕切部材の構造が複雑となり、製造作業が面倒で製造コストが高くなるという問題は、そのまま内在していたのである。   However, in the fluid-filled vibration isolator disclosed in Patent Document 3, the tuning frequency of the orifice passage is changed by selectively switching the wall spring rigidity of the equilibrium chamber in which the orifice passage tuned to the high frequency side is communicated. The orifice passage itself has a constant passage length and passage sectional area. Therefore, even if the high frequency side orifice passage is opened and closed, it is difficult to greatly change the frequency range in which the vibration isolation effect is exhibited. Therefore, for example, the idling vibration in the middle frequency range which is a problem when the vehicle is stopped and the middle to high speed traveling booming noise which is a problem in traveling can be expressed by opening and closing the orifice passage. It was extremely difficult. In addition, since it is necessary to form two orifice passages, the problem that the structure of the partition member is complicated, the manufacturing operation is troublesome, and the manufacturing cost is high is inherent.

特開平08−028623号公報Japanese Patent Application Laid-Open No. 08-028623 特開平08−270718号公報Japanese Patent Laid-Open No. 08-270718 特開平10−089402号公報Japanese Patent Laid-Open No. 10-089402

ここにおいて、本発明は上述の如き事情を背景として為されたものであり、その解決課題とするところは、例えば自動車における低周波数域のエンジンシェイクと中周波数域のアイドリング振動と高周波数域の中〜高速こもり音など、周波数が大きく異なった複数の振動に対しても有効な防振効果を発揮し得る、構造が簡単で自動車用エンジンマウント等として好適に新規な構造の流体封入式防振装置を提供することにある。   Here, the present invention has been made in the background as described above, and the problem to be solved is, for example, an engine shake in a low frequency range, an idling vibration in a mid frequency range, and a high frequency range in an automobile. A fluid-filled vibration isolator with a new structure suitable for automobile engine mounts and the like that can exhibit effective vibration isolation effects against multiple vibrations with significantly different frequencies, such as high-speed booming noise. Is to provide.

以下、前述の課題を解決するために為された本発明の態様を記載する。なお、以下に記載の各態様において採用される構成要素は、可能な限り任意の組み合わせで採用可能である。また、本発明の態様乃至は技術的特徴は、以下に記載のものに限定されることなく、明細書全体および図面に記載されたもの、或いはそれらの記載から当業者が把握することの出来る発明思想に基づいて認識されるものであることが理解されるべきである。   Hereinafter, the aspect of this invention made in order to solve the above-mentioned subject is described. In addition, the component employ | adopted in each aspect as described below is employable by arbitrary combinations as much as possible. Further, aspects or technical features of the present invention are not limited to those described below, but are described in the entire specification and drawings, or an invention that can be understood by those skilled in the art from those descriptions. It should be understood that it is recognized based on thought.

すなわち、本発明の特徴とするところは、第一の取付部材を筒状を有する第二の取付部材の軸方向一方の開口部側に離隔配置して、それら第一の取付部材と第二の取付部材を本体ゴム弾性体で連結すると共に、該第二の取付部材の軸方向他方の開口部を可撓性ゴム膜で覆蓋することにより、該本体ゴム弾性体と該可撓性ゴム膜の間に非圧縮性流体が封入された流体室を形成し、該第二の取付部材で支持された仕切部材で該流体室を仕切って、該流体室における該仕切部材を挟んだ両側に壁部の一部が該本体ゴム弾性体で構成された受圧室と壁部の一部が該可撓性ゴム膜で構成された平衡室を形成して、それら受圧室と平衡室を相互に連通せしめるオリフィス通路を設けた流体封入式防振装置において、前記受圧室と前記平衡室を相互に接続して一つの液室とする開口窓を前記仕切部材の中央部分に設ける一方、前記可撓性ゴム膜を挟んで該平衡室と反対側に空気圧式アクチュエータを配設して該空気圧式アクチュエータにおける硬質の出力部材の先端面を該開口窓に対して該可撓性ゴム膜を挟んで対向位置せしめ、該可撓性ゴム膜の中央部分を該仕切部材における該開口窓の開口周縁部に押し付けることで該開口窓を閉塞状態に保持せしめる付勢手段を該空気圧式アクチュエータに設けると共に、該出力部材の先端面に凹所を形成して、該出力部材により該仕切部材に押し付けられた該可撓性ゴム膜の該凹所内への弾性変形を許容し、且つ該可撓性ゴム膜の該凹所内面への当接によって該可撓性ゴム膜の弾性変形量を制限する変形量制限機構付きの液圧吸収機構を構成することにより、該空気圧式アクチュエータの作動によって前記開口窓を開閉する液圧吸収機構内蔵式弁体を設けたことにある。   That is, the feature of the present invention is that the first mounting member and the second mounting member having a cylindrical shape are spaced apart from each other in the axial direction, and the first mounting member and the second mounting member are separated from each other. The mounting member is connected with the main rubber elastic body, and the other opening in the axial direction of the second mounting member is covered with a flexible rubber film, so that the main rubber elastic body and the flexible rubber film are covered. A fluid chamber in which an incompressible fluid is sealed is formed, the fluid chamber is partitioned by a partition member supported by the second mounting member, and wall portions are provided on both sides of the partition member in the fluid chamber. Forming a pressure receiving chamber made up of a part of the main rubber elastic body and an equilibrium chamber made up of a part of the wall made up of the flexible rubber film, and making the pressure receiving chamber and the equilibrium chamber communicate with each other. In a fluid filled type vibration damping device provided with an orifice passage, the pressure receiving chamber and the equilibrium chamber are connected to each other. An opening window serving as one liquid chamber is provided in the central portion of the partition member, and a pneumatic actuator is disposed on the opposite side of the equilibrium chamber with the flexible rubber film interposed therebetween, so that a rigid actuator in the pneumatic actuator is provided. The front end surface of the output member is opposed to the opening window across the flexible rubber film, and the central portion of the flexible rubber film is pressed against the opening peripheral edge of the opening window in the partition member. The flexible actuator is provided with a biasing means for holding the opening window in a closed state in the pneumatic actuator, and a recess is formed in the front end surface of the output member, and is pressed against the partition member by the output member. With a deformation amount limiting mechanism that allows elastic deformation of the rubber film into the recess and limits the elastic deformation amount of the flexible rubber film by contacting the inner surface of the flexible rubber film. By configuring the hydraulic pressure absorption mechanism Lies in the provision of the liquid pressure absorption mechanism built-valve body for opening and closing the opening window by the operation of the air pressure actuator.

このような本発明に従う構造とされた流体封入式防振装置においては、オリフィス通路のチューニング周波数域の振動入力時に、可撓性ゴム膜を仕切部材の開口窓の周縁部に押し付けて開口窓が閉塞された状態を保持せしめることにより、開口窓を通じての受圧室の圧力漏れを抑えて、受圧室と平衡室の相対的な圧力変動の差を有効に生ぜしめることが出来る。これにより、オリフィス通路を通じて流動せしめられる流体の流動量を十分に確保して、かかる流体の共振作用等の流動作用に基づき目的の防振効果(オリフィス効果)を得ることが出来る。   In such a fluid-filled vibration isolator having a structure according to the present invention, when a vibration is input in the tuning frequency range of the orifice passage, the flexible rubber film is pressed against the peripheral edge of the opening window of the partition member to open the opening window. By maintaining the closed state, the pressure leakage of the pressure receiving chamber through the opening window can be suppressed, and the difference in relative pressure fluctuation between the pressure receiving chamber and the equilibrium chamber can be effectively generated. As a result, it is possible to secure a sufficient amount of fluid flowing through the orifice passage and to obtain a target vibration-proofing effect (orifice effect) based on the fluid action such as the resonance action of the fluid.

特に本構造に従えば、可撓性ゴム膜により仕切部材の開口窓が閉塞された状態下で、オリフィス通路のチューニング周波数域において比較的に大きな振幅の振動が入力された際には、可撓性ゴム膜が凹所内面に当接することで、可撓性ゴム膜の弾性変形量が制限されるようになっている。これにより、受圧室の圧力変動が可撓性ゴム膜の弾性変形で吸収されることが抑えられて、オリフィス通路を通じての流体流動量が安定して確保されることとなり、所期のオリフィス効果、特に低周波大振幅振動に対する防振効果が有利に発揮され得る。   In particular, according to this structure, when vibration with a relatively large amplitude is input in the tuning frequency range of the orifice passage in a state where the opening window of the partition member is closed by the flexible rubber film, the flexible rubber film is flexible. The amount of elastic deformation of the flexible rubber film is limited by the elastic rubber film coming into contact with the inner surface of the recess. As a result, the pressure fluctuation in the pressure receiving chamber is suppressed from being absorbed by the elastic deformation of the flexible rubber film, and the amount of fluid flow through the orifice passage is stably secured. In particular, an anti-vibration effect against low-frequency large-amplitude vibration can be advantageously exhibited.

また、オリフィス通路のチューニング周波数よりも高周波数域の振動が入力されると、オリフィス通路の目詰まり状態に起因して受圧室の圧力変動が大きくなって高動ばね化が惹起されることとなるが、そこで出力部材による可撓性ゴム膜の仕切部材への押し付け状態を解除して開口窓を開口状態とすることにより、受圧室と平衡室が相互に接続されて一体的な室になる。その結果、高動ばね化が回避されて、平衡室における可撓性ゴム膜の弾性変形に基づき防振効果が安定して発揮され得る。   Further, when vibration in a frequency range higher than the tuning frequency of the orifice passage is input, the pressure fluctuation in the pressure receiving chamber increases due to the clogged state of the orifice passage, and high dynamic springs are caused. However, by releasing the pressing state of the flexible rubber film against the partition member by the output member and opening the opening window, the pressure receiving chamber and the equilibrium chamber are connected to each other to form an integral chamber. As a result, high dynamic springs can be avoided, and the anti-vibration effect can be stably exhibited based on the elastic deformation of the flexible rubber film in the equilibrium chamber.

また、可撓性ゴム膜が仕切部材の開口窓の周縁部に押し付けられて開口窓が閉塞された状態下で、オリフィス通路のチューニング周波数よりも高周波数域の振動が入力されると、オリフィス通路の目詰まり状態に起因して高動ばね化が惹起されることとなる。ここで、本発明に係る防振装置では、可撓性ゴム膜が仕切部材に押し付けられた状態で、可撓性ゴム膜の弾性変形が出力部材の凹所により許容されていることから、受圧室の圧力変動が可撓性ゴム膜の弾性変形に基づき吸収されるのであり、その結果、高動ばね化が回避されて、所期の防振効果が安定して得られるのである。   Further, when vibration in a frequency range higher than the tuning frequency of the orifice passage is input in a state where the flexible rubber film is pressed against the peripheral edge of the opening window of the partition member and the opening window is closed, the orifice passage Due to the clogging state, the high dynamic spring is caused. Here, in the vibration isolator according to the present invention, the elastic deformation of the flexible rubber film is allowed by the recess of the output member in a state where the flexible rubber film is pressed against the partition member. The pressure fluctuation in the chamber is absorbed on the basis of the elastic deformation of the flexible rubber film. As a result, the high dynamic spring is avoided and the desired vibration isolation effect can be stably obtained.

要するに、空気圧式アクチュエータの作動により開口窓を開閉する弁体が、出力部材により仕切部材に押し付けられた可撓性ゴム膜の凹所内への弾性変形を許容し且つ可撓性ゴム膜の凹所内面への当接によってその弾性変形量を制限する変形量制限機構付きの液圧吸収機構を内蔵した構造とされている。それによって、全体としてコンパクト化が達成されつつ、オリフィス通路のチューニング周波数域の振動や該チューニング周波数よりも高周波数域の振動、該チューニング周波数域で大振幅の振動など、周波数域や振幅が異なる複数の振動に対して高度な防振性能が発揮され得るのである。   In short, the valve body that opens and closes the opening window by the operation of the pneumatic actuator allows elastic deformation into the recess of the flexible rubber film pressed against the partition member by the output member, and the recess of the flexible rubber film The structure has a built-in hydraulic pressure absorbing mechanism with a deformation amount limiting mechanism that limits the amount of elastic deformation by contact with the inner surface. As a result, a plurality of different frequency ranges and amplitudes such as vibrations in the tuning frequency range of the orifice passage, vibrations in a higher frequency range than the tuning frequency, vibrations having a large amplitude in the tuning frequency range can be achieved while achieving compactness as a whole. High vibration-proof performance can be exhibited against vibrations of

また、オリフィス通路のチューニング周波数よりも高周波数域の振動入力時に受圧室の圧力変動を吸収する可撓性ゴム膜の弾性変形量に関しては、高周波微振幅の振動を吸収するだけの量が確保されれば良いから、一般に変形量が小さくて済み、従って凹所を特別に大きく形成する必要がない。即ち、可撓性ゴム膜と凹所内面の間の離隔距離が小さく設定され得る。それ故、防振装置のコンパクト化が有利に図られ得ることに加えて、問題となる大振幅振動の入力時に可撓性ゴム膜の弾性変形量を確実に抑えることが出来て、オリフィス効果の信頼性が向上され得る。   In addition, the amount of elastic deformation of the flexible rubber film that absorbs pressure fluctuations in the pressure-receiving chamber when vibration is input in a frequency range higher than the tuning frequency of the orifice passage is secured to absorb vibration of high-frequency fine amplitude. Therefore, the amount of deformation is generally small, and therefore it is not necessary to form the recesses with a particularly large size. That is, the separation distance between the flexible rubber film and the inner surface of the recess can be set small. Therefore, in addition to being able to advantageously reduce the size of the vibration isolator, it is possible to reliably suppress the elastic deformation of the flexible rubber film at the time of inputting a large amplitude vibration, which is a problem. Reliability can be improved.

また、本発明に係る流体封入式防振装置では、前記オリフィス通路がエンジンシェイクに相当する低周波数域にチューニングされていると共に、前記開口窓が前記液圧吸収機構内蔵式弁体で閉塞された状態下で走行こもり音に相当する高周波小振幅の振動入力に際しては前記可撓性ゴム膜が前記凹所内面に当接するに至らない変形量とされる一方、エンジンシェイクに相当する低周波大振幅の振動入力に際しては該可撓性ゴム膜が前記凹所内面に当接する変形量となるように、該液圧吸収機構内蔵式弁体を構成する該可撓性ゴム膜の弾性と該凹所の大きさが設定されて自動車用エンジンマウントが構成されるようにしても良い。   In the fluid filled type vibration damping device according to the present invention, the orifice passage is tuned to a low frequency range corresponding to an engine shake, and the opening window is closed by the valve body with a built-in hydraulic pressure absorption mechanism. In the case of vibration input with high frequency and small amplitude corresponding to the traveling noise under the condition, the amount of deformation that does not cause the flexible rubber film to come into contact with the inner surface of the recess is obtained. When the vibration is input, the elasticity of the flexible rubber film constituting the valve body with the built-in hydraulic pressure absorbing mechanism and the recess are set such that the deformation amount of the flexible rubber film contacts the inner surface of the recess. The vehicle engine mount may be configured by setting the size.

このような本発明に従う構造とされた流体封入式防振装置においては、前述の液圧吸収機構内蔵式弁体を備えていることによって、装置のコンパクト化が図られつつ、走行こもり音等の高周波小振幅振動の防振効果やエンジンシェイク等の低周波大振幅振動の防振効果が有利に発揮され得ることとなり、自動車用エンジンマウントとして有利に採用され得る。   In such a fluid-filled vibration isolator having a structure according to the present invention, the above-described valve body with a built-in hydraulic pressure absorption mechanism is provided, so that the device can be made compact and a traveling booming noise or the like can be obtained. The anti-vibration effect of high-frequency small-amplitude vibration and the anti-vibration effect of low-frequency large-amplitude vibration such as engine shake can be advantageously exhibited, and can be advantageously employed as an automobile engine mount.

さらに、上述の流体封入式防振装置においては、前記空気圧式アクチュエータに接続されて、自動車の停車状態下で該空気圧式アクチュエータに負圧を及ぼすことにより、前記付勢手段の付勢力に抗して前記仕切部材の前記開口窓から前記液圧吸収機構内蔵式弁体を離隔状態に保持せしめて該開口窓を開放させる一方、自動車の走行状態下で該空気圧式アクチュエータを大気に連通させることにより、該付勢手段の付勢力に基づいて該仕切部材の該開口窓に対して該液圧吸収機構内蔵式弁体を押し付け状態に保持せしめて該開口窓を遮断させる空気圧制御手段を設けた構造が、好適に採用され得る。   Further, in the above-described fluid filled type vibration isolator, the biasing force of the biasing means is resisted by being connected to the pneumatic actuator and applying a negative pressure to the pneumatic actuator when the automobile is stopped. By holding the hydraulic pressure absorbing mechanism built-in type valve body from the opening window of the partition member in a separated state to open the opening window, while allowing the pneumatic actuator to communicate with the atmosphere while the automobile is running And a structure including air pressure control means for holding the valve body with a built-in hydraulic pressure absorbing mechanism pressed against the opening window of the partition member based on the urging force of the urging means to block the opening window. Can be suitably employed.

このような構造に従えば、開口窓を開口状態と閉塞状態に切り換える空気圧式アクチュエータが簡単に実現されることとなって、製造作業の容易化や製造コストの削減が有利に図られ得る。   According to such a structure, the pneumatic actuator that switches the opening window between the open state and the closed state can be easily realized, which can facilitate the manufacturing work and reduce the manufacturing cost.

また、本発明に係る流体封入式防振装置においては、前記液圧吸収機構内蔵式弁体には、前記開口窓を閉塞せしめた状態下で前記可撓性ゴム膜で覆蓋された前記凹所の内部空間を外部空間に連通せしめる空気連通路が形成されている構造が、好適に採用される。   Further, in the fluid filled type vibration damping device according to the present invention, the valve body with a built-in hydraulic pressure absorption mechanism includes the concave portion covered with the flexible rubber film in a state where the opening window is closed. A structure in which an air communication path that allows the internal space to communicate with the external space is formed is preferably employed.

このような構造によれば、開口窓の閉塞状態下で可撓性ゴム膜で覆蓋された凹所の内部空間が密閉されないことから、内部空間に空気が溜まることに起因して、開口窓の閉塞状態と開口状態を切り換える際に生じる異音が効果的に抑えられる。   According to such a structure, since the internal space of the recess covered with the flexible rubber film is not sealed under the closed state of the open window, air accumulates in the internal space, and thus the open window Abnormal noise generated when switching between the closed state and the open state is effectively suppressed.

さらに、上述の流体封入式防振装置においては、前記空気圧式アクチュエータの前記出力部材は、先端面の外周部分において環状の弾性押圧突部を備えており、この弾性押圧突部によって該出力部材が前記可撓性ゴム膜を前記仕切部材における前記開口窓の開口周縁部に押し付けるようになっていると共に、該弾性押圧突部には、周上の少なくとも一カ所に連通溝が設けられており、この連通溝によって前記空気連通路が形成されている構造が、好適に採用される。   Furthermore, in the above-described fluid-filled vibration isolator, the output member of the pneumatic actuator includes an annular elastic pressing protrusion on the outer peripheral portion of the tip surface, and the output member is supported by the elastic pressing protrusion. The flexible rubber film is configured to press against the opening peripheral edge of the opening window in the partition member, and the elastic pressing protrusion is provided with a communication groove at least at one place on the circumference, A structure in which the air communication path is formed by the communication groove is preferably employed.

このような構造によれば、出力部材が仕切部材に対して、弾性押圧突部の弾性に基づいて緩衝的に押し付けられることによって、それら出力部材や仕切部材の耐久性が向上され得る。また、弾性押圧突部の連通溝を利用して空気連通路が容易に実現されることから、製造の容易が図られ得る。   According to such a structure, durability of these output members and a partition member can be improved by pressing an output member against a partition member bufferingly based on the elasticity of an elastic press protrusion. In addition, since the air communication passage is easily realized by using the communication groove of the elastic pressing protrusion, the manufacture can be facilitated.

また、本発明に係る流体封入式防振装置においては、前記可撓性ゴム膜には、前記仕切部材における前記開口窓の開口周縁部に対して前記空気圧式アクチュエータの前記出力部材によって押し付けられる環状押付部の少なくとも一方の面において周方向に複数の凹凸が設けられている構造が、好適に採用され得る。   In the fluid filled type vibration damping device according to the present invention, the flexible rubber film is annularly pressed against the opening peripheral edge of the opening window of the partition member by the output member of the pneumatic actuator. A structure in which a plurality of irregularities are provided in the circumferential direction on at least one surface of the pressing portion can be suitably employed.

このような構造によれば、出力部材と仕切部材の当接面間に隙間が設けられることとなり、それによって、当接に伴う打音や当接状態から離隔する際に生じる異音等が効果的に抑えられる。   According to such a structure, a gap is provided between the abutment surfaces of the output member and the partition member, and thereby, an impact sound caused by the abutment or abnormal noise generated when separating from the abutment state is effective. Can be suppressed.

また、本発明に係る流体封入式防振装置においては、前記空気圧式アクチュエータにおける前記出力部材の先端面の外周部分と、該出力部材の先端面の外周部分によって前記可撓性ゴム膜が押し付けられる前記仕切部材の前記開口窓の開口周縁部とが、該可撓性ゴム膜を挟んで互いに相似形状となる円弧状湾曲断面形状で周方向に延びる当接挟持面とされている構造が、好適に採用され得る。   In the fluid filled type vibration damping device according to the present invention, the flexible rubber film is pressed by the outer peripheral portion of the front end surface of the output member and the outer peripheral portion of the front end surface of the output member in the pneumatic actuator. A structure in which the opening peripheral edge portion of the opening window of the partition member is a contact holding surface extending in the circumferential direction with an arcuate curved cross-sectional shape that is similar to each other across the flexible rubber film is preferable. Can be adopted.

このような構造によれば、出力部材と仕切部材の何れか一方が他方に対して嵌り込むように当接して、当接状態が安定することから、可撓性ゴム膜によって開口窓が一層確実に閉塞されて、オリフィス効果の更なる向上が図られ得る。   According to such a structure, one of the output member and the partition member is brought into contact with the other so that the contact state is stabilized, so that the opening window is more reliably secured by the flexible rubber film. The orifice effect can be further improved.

以下、本発明を更に具体的に明らかにするために、本発明の実施形態について説明する。先ず、図1には、本発明の流体封入式防振装置に係る一実施形態としての自動車用エンジンマウント10が示されている。このエンジンマウント10は、第一の取付部材としての第一の取付金具12と第二の取付部材としての第二の取付金具14が本体ゴム弾性体16で連結された構造とされている。第一の取付金具12がパワーユニット側に取り付けられると共に、第二の取付金具14が車両ボデー側に取り付けられることにより、パワーユニットがボデーに対して防振支持されるようになっている。   Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described. First, FIG. 1 shows an automobile engine mount 10 as an embodiment according to the fluid filled type vibration damping device of the present invention. The engine mount 10 has a structure in which a first mounting bracket 12 as a first mounting member and a second mounting bracket 14 as a second mounting member are connected by a main rubber elastic body 16. The first mounting bracket 12 is mounted on the power unit side, and the second mounting bracket 14 is mounted on the vehicle body side, so that the power unit is supported in a vibration-proof manner with respect to the body.

なお、図1では、自動車に装着する前のエンジンマウント10の単体での状態が示されているが、本実施形態では、装着状態において、パワーユニットの分担支持荷重がマウント軸方向(図1中、上下)に入力される。従って、マウント装着状態下では、本体ゴム弾性体16の弾性変形に基づき第一の取付金具12と第二の取付金具14が軸方向で互いに接近する方向に変位する。また、かかる装着状態下、防振すべき主たる振動は、略マウント軸方向に入力されることとなる。以下の説明中、特に断りのない限り、上下方向は、マウント軸方向となる図1中の上下方向をいう。   1 shows the state of the engine mount 10 as a single unit before being mounted on the automobile, but in the present embodiment, in the mounted state, the shared support load of the power unit is in the mount axis direction (in FIG. 1, (Up and down). Therefore, in the mounted state, the first mounting member 12 and the second mounting member 14 are displaced in the axial direction toward each other based on the elastic deformation of the main rubber elastic body 16. In addition, under such a mounted state, main vibrations to be vibrated are input substantially in the mount axis direction. In the following description, unless otherwise specified, the vertical direction refers to the vertical direction in FIG.

より詳細には、第一の取付金具12は、小径の略円柱形状乃至は円錐台形状を呈しており、その中央部分には螺子穴18が設けられている。   More specifically, the first mounting member 12 has a small-diameter substantially cylindrical shape or a truncated cone shape, and a screw hole 18 is provided in the central portion thereof.

一方、第二の取付金具14は、大径の略円筒形状を有していると共に、軸方向下端部に第二の取付金具14よりも大径のリング状を呈するかしめ部20が一体形成されている。また、第一の取付金具12が第二の取付金具14の一方(図1中、上)の開口部側に離隔配置されて、両金具12,14の中心軸が略同一線上に位置せしめられていると共に、第一の取付金具12と第二の取付金具14の間には、本体ゴム弾性体16が配されている。   On the other hand, the second mounting bracket 14 has a substantially cylindrical shape with a large diameter, and a caulking portion 20 that has a ring shape larger in diameter than the second mounting bracket 14 is integrally formed at the lower end in the axial direction. ing. Further, the first mounting bracket 12 is spaced apart from the opening side of one of the second mounting brackets 14 (upper in FIG. 1), and the central axes of both the brackets 12 and 14 are positioned substantially on the same line. In addition, a main rubber elastic body 16 is disposed between the first mounting bracket 12 and the second mounting bracket 14.

本体ゴム弾性体16は、略円錐台形状を有しており、その大径側端面には、下方に開口するすり鉢形状の大径凹所22が設けられている。また、本体ゴム弾性体16の小径側端面には、第一の取付金具12が略全体を埋設された状態で加硫接着されていると共に、本体ゴム弾性体16の大径側端部外周面には、第二の取付金具14の内周面が略全体に亘って加硫接着されている。要するに、本体ゴム弾性体16が、第一の取付金具12と第二の取付金具14を備えた一体加硫成形品として形成されている。これにより、第一の取付金具12と第二の取付金具14が、本体ゴム弾性体16によって相互に弾性的に連結されていると共に、第二の取付金具14の軸方向一方(図1中、上)の開口部が本体ゴム弾性体16によって流体密に閉塞されている。また、第二の取付金具14におけるかしめ部20の内側には、本体ゴム弾性体16と一体形成された薄肉のシールゴム層が被着形成されている。これら第一及び第二の取付金具12,14を備えた本体ゴム弾性体16の一体加硫成形品には、第二の取付金具14の軸方向他方(図1中、下)の開口部側から仕切部材24やオリフィス部材28が組み付けられている。仕切部材24やオリフィス部材28は、合成樹脂材や金属材等の硬質材を用いて形成されている。   The main rubber elastic body 16 has a substantially truncated cone shape, and a mortar-shaped large-diameter recess 22 that opens downward is provided on the large-diameter side end face. In addition, the first mounting bracket 12 is vulcanized and bonded to the small diameter side end surface of the main rubber elastic body 16 in a state where the whole is embedded, and the outer peripheral surface of the large diameter side end portion of the main rubber elastic body 16. In this case, the inner peripheral surface of the second mounting bracket 14 is vulcanized and bonded over substantially the whole. In short, the main rubber elastic body 16 is formed as an integrally vulcanized molded product including the first mounting bracket 12 and the second mounting bracket 14. Thus, the first mounting bracket 12 and the second mounting bracket 14 are elastically connected to each other by the main rubber elastic body 16 and one of the second mounting brackets 14 in the axial direction (in FIG. 1, The upper opening is fluid-tightly closed by the main rubber elastic body 16. A thin seal rubber layer integrally formed with the main rubber elastic body 16 is formed on the inner side of the caulking portion 20 of the second mounting bracket 14. In the integrally vulcanized molded product of the main rubber elastic body 16 provided with the first and second mounting brackets 12 and 14, the opening side on the other side in the axial direction of the second mounting bracket 14 (lower in FIG. 1). The partition member 24 and the orifice member 28 are assembled. The partition member 24 and the orifice member 28 are formed using a hard material such as a synthetic resin material or a metal material.

仕切部材24は、薄肉の円板形状を有していると共に、中央に開口窓としての円形状の透孔30が貫設されている。特に、仕切部材24の中央部分が軸方向一方(図1中、上)に向かって径寸法が段階的に小さくなる段付き板状を呈しており、その中央に透孔30が形成されているため、透孔30の周縁部には、仕切部材24の軸直角方向中間部分および外周部分よりも軸方向一方(図1中、上)に突出して、略円環板形状を呈する当接支持部32が一体形成された構造を呈している。当接支持部32の外周部分は、円弧状の湾曲断面形状で周方向に延びている。   The partition member 24 has a thin disk shape, and a circular through hole 30 serving as an opening window is provided through the center. In particular, the central portion of the partition member 24 has a stepped plate shape whose diameter dimension gradually decreases toward one axial direction (upward in FIG. 1), and a through hole 30 is formed in the center thereof. For this reason, the peripheral portion of the through hole 30 protrudes in one axial direction (upward in FIG. 1) from the intermediate portion and the outer peripheral portion of the partition member 24 in the direction perpendicular to the axis, and has a substantially annular plate shape. 32 has an integrally formed structure. The outer peripheral portion of the contact support portion 32 extends in the circumferential direction with an arcuate curved cross-sectional shape.

オリフィス部材28は、全体として厚肉の円環板形状を有している。オリフィス部材28の中央の軸方向一方(図1中、下)の開口部分が、軸方向一方から他方(図1中、上)に向かって径寸法が小さくなるテーパ形状とされている。オリフィス部材28の外周部分には、周方向に所定の長さ(本実施形態では一周弱)で延びる周溝36が形成されている。オリフィス部材28の内径寸法が、仕切部材24の透孔30の径寸法よりも大きくされていて、当接支持部32の外径寸法よりも僅かに大きくされている。オリフィス部材28の外径寸法が、仕切部材24の外径寸法よりも小さくされている。   The orifice member 28 has a thick annular plate shape as a whole. The opening part of one axial direction (downward in FIG. 1) of the center of the orifice member 28 is made into the taper shape from which a radial dimension becomes small toward the other (upward in FIG. 1) axial direction. A circumferential groove 36 extending in the circumferential direction with a predetermined length (a little less than one round in the present embodiment) is formed in the outer peripheral portion of the orifice member 28. The inner diameter dimension of the orifice member 28 is larger than the diameter dimension of the through hole 30 of the partition member 24, and is slightly larger than the outer diameter dimension of the contact support portion 32. The outer diameter dimension of the orifice member 28 is made smaller than the outer diameter dimension of the partition member 24.

これら仕切部材24とオリフィス部材28が、同心軸上に位置せしめられて軸方向に互いに重ね合わせられている。仕切部材24の外周縁部が、第二の取付金具14の軸方向端部に一体形成されたかしめ部20に嵌め込まれて、該軸方向端部と軸方向に重ね合わせられている。仕切部材24と第二の取付金具14の軸方向端部の重ね合わせ面間には、本体ゴム弾性体16と一体形成されたシールゴム層が挟圧配置されていることによって、かかる重ね合わせ面が流体密に重ね合わせられている。また、仕切部材24やオリフィス部材28を配した第二の取付金具14の軸方向端部には、可撓性ゴム膜としてのダイヤフラム38が組み付けられている。   The partition member 24 and the orifice member 28 are positioned on the concentric shaft and overlap each other in the axial direction. The outer peripheral edge portion of the partition member 24 is fitted into a caulking portion 20 formed integrally with the axial end portion of the second mounting member 14 and overlapped with the axial end portion in the axial direction. A sealing rubber layer integrally formed with the main rubber elastic body 16 is interposed between the overlapping surfaces of the partition member 24 and the axial end of the second mounting bracket 14 so that the overlapping surface is It is fluidly superimposed. In addition, a diaphragm 38 as a flexible rubber film is assembled to an end portion in the axial direction of the second mounting member 14 provided with the partition member 24 and the orifice member 28.

ダイヤフラム38は、軸方向に弛みを持った薄肉の弾性ゴム膜によって形成されていると共に、全体として略円板形状を有している。また、ダイヤフラム38の外周部分には、固定筒金具40が固設されている。固定筒金具40は、大径の略円筒形状を有しており、その軸方向一方(図1中、上)の端部に軸直角方向外方に広がる円環板形状の外フランジ状部42が一体形成されていると共に、その軸方向他方(図1中、下)の端部に軸直角方向内方に広がる円環板形状の内フランジ状部44が一体形成されている。また、固定筒金具40の筒状本体の内径寸法が、オリフィス部材28の外径寸法よりも大きくされていると共に、外フランジ状部42の外径寸法が、仕切部材24の外径寸法と略同じとされている。この内フランジ状部44がダイヤフラム38の外周部分に加硫接着されていることにより、ダイヤフラム38は、固定筒金具40を備えた一体加硫成形品として形成されている。また、固定筒金具40の筒状の本体や外フランジ状部42、内フランジ状部44の内面には、ダイヤフラム38と一体形成されたシールゴム層46が被着形成されている。   The diaphragm 38 is formed of a thin elastic rubber film having a slack in the axial direction, and has a substantially disk shape as a whole. A fixed tube fitting 40 is fixed to the outer peripheral portion of the diaphragm 38. The fixed cylinder fitting 40 has a substantially cylindrical shape with a large diameter, and an outer flange-like portion 42 in the shape of an annular plate spreading outward in the direction perpendicular to the axis at one end in the axial direction (upper in FIG. 1). Are integrally formed, and an annular flange portion 44 having an annular plate shape extending inwardly in the direction perpendicular to the axis is integrally formed at the other axial end (lower in FIG. 1). In addition, the inner diameter dimension of the cylindrical main body of the fixed tubular fitting 40 is larger than the outer diameter dimension of the orifice member 28, and the outer diameter dimension of the outer flange-shaped portion 42 is substantially the same as the outer diameter dimension of the partition member 24. It is the same. The inner flange-shaped portion 44 is vulcanized and bonded to the outer peripheral portion of the diaphragm 38, so that the diaphragm 38 is formed as an integrally vulcanized molded product including the fixed tube fitting 40. In addition, a seal rubber layer 46 integrally formed with the diaphragm 38 is attached and formed on the inner surface of the cylindrical main body, the outer flange-shaped portion 42, and the inner flange-shaped portion 44 of the fixed tube fitting 40.

このようなダイヤフラム38の加硫成形品における固定筒金具40が、オリフィス部材28に嵌着固定されて、固定筒金具40の外フランジ状部42が仕切部材24の外周部分と軸方向に重ね合わせられていると共に、固定筒金具40の内フランジ状部44がオリフィス部材28の外周部分と軸方向に重ね合わせられている。これら固定筒金具40と仕切部材24やオリフィス部材28の重ね合わせ面間にシールゴム層46が挟圧配置されていることによって、固定筒金具40の内周面と仕切部材24の外周面やオリフィス部材28の外周面が流体密に重ね合わせられている。   The fixed tube fitting 40 in such a vulcanized product of the diaphragm 38 is fitted and fixed to the orifice member 28, and the outer flange-like portion 42 of the fixed tube fitting 40 is overlapped with the outer peripheral portion of the partition member 24 in the axial direction. In addition, the inner flange-shaped portion 44 of the fixed tubular fitting 40 is overlapped with the outer peripheral portion of the orifice member 28 in the axial direction. Since the sealing rubber layer 46 is sandwiched between the overlapping surfaces of the fixed cylindrical metal fitting 40 and the partition member 24 or the orifice member 28, the inner peripheral surface of the fixed cylindrical metal fitting 40, the outer peripheral surface of the partition member 24, or the orifice member. The outer peripheral surface of 28 is superposed fluid tightly.

そして、互いに軸方向に重ね合わせられた仕切部材24の外周部分と固定筒金具40の外フランジ状部42が、第二の取付金具14のかしめ部20に嵌め込まれて、かしめ部20にかしめ加工が施されている。これにより、固定筒金具40を備えたダイヤフラム38の一体加硫成形品や仕切部材24、オリフィス部材28が、第一及び第二の取付金具12,14を備えた本体ゴム弾性体16の一体加硫成形品に組み付けられていると共に、第二の取付金具14の軸方向他方の開口部が、ダイヤフラム38によって流体密に覆蓋されている。また、仕切部材24と固定筒金具40がかしめ固定されていることに基づき、仕切部材24と固定筒金具40の間に配されたオリフィス部材28が軸方向に挟圧固定されている。   Then, the outer peripheral portion of the partition member 24 and the outer flange-shaped portion 42 of the fixed tubular fitting 40 that are overlapped with each other in the axial direction are fitted into the caulking portion 20 of the second mounting bracket 14 and are caulked to the caulking portion 20. Is given. As a result, the integral vulcanized molded product of the diaphragm 38 having the fixed tubular fitting 40, the partition member 24, and the orifice member 28 are integrally joined to the main rubber elastic body 16 having the first and second mounting fittings 12 and 14. While being assembled with the sulfur molded product, the other opening in the axial direction of the second mounting bracket 14 is covered with a diaphragm 38 in a fluid-tight manner. In addition, based on the fact that the partition member 24 and the fixed tube fitting 40 are fixed by caulking, the orifice member 28 disposed between the partition member 24 and the fixed tube fitting 40 is clamped and fixed in the axial direction.

これら本体ゴム弾性体16とダイヤフラム38の対向面間は、外部空間に対して密閉されており、そこに非圧縮性流体が封入された流体室48が形成されている。封入流体としては、例えば水やアルキレングリコール, ポリアルキレングリコール, シリコーン油等が採用されるが、特に流体の共振作用等の流動作用に基づく防振効果を有効に得るためには、0.1Pa・s以下の低粘性流体を採用することが望ましい。流体室48への非圧縮性流体の封入は、例えば、第一及び第二の取付金具12,14を備えた本体ゴム弾性体16の一体加硫成形品に対して、上述の仕切部材24やダイヤフラム38の組み付けを非圧縮性流体中で行うことによって、有利に実現される。   A space between the opposing surfaces of the main rubber elastic body 16 and the diaphragm 38 is sealed with respect to the external space, and a fluid chamber 48 in which an incompressible fluid is sealed is formed. As the sealing fluid, for example, water, alkylene glycol, polyalkylene glycol, silicone oil or the like is adopted, and in order to effectively obtain a vibration isolation effect based on a fluid action such as a resonance action of the fluid, 0.1 Pa · It is desirable to employ a low-viscosity fluid of s or less. The incompressible fluid is sealed in the fluid chamber 48, for example, with respect to the integrally vulcanized molded product of the main rubber elastic body 16 including the first and second mounting brackets 12 and 14, the partition member 24 and This is advantageously realized by performing the assembly of the diaphragm 38 in an incompressible fluid.

また、流体室48の軸方向中間部分に仕切部材24が軸直角方向に拡がるように配設されていることによって、流体室48が仕切部材24を挟んで軸方向上下に二分されている。この仕切部材24を挟んだ軸方向一方(図1中、上)の側には、壁部の一部が本体ゴム弾性体16で構成されて、第一の取付金具12と第二の取付金具14の間への振動入力時に、本体ゴム弾性体16の弾性変形に基づいて圧力変動が生ぜしめられる受圧室50が形成されている。また、仕切部材24を挟んだ軸方向他方(図1中、下)の側には、壁部の一部がダイヤフラム38で構成されて、該ダイヤフラム38の弾性変形に基づいて容積変化が容易に許容される平衡室52が形成されている。   In addition, the partition member 24 is disposed in the axially intermediate portion of the fluid chamber 48 so as to expand in the direction perpendicular to the axis, so that the fluid chamber 48 is divided into two vertically in the axial direction across the partition member 24. A part of the wall portion is composed of the main rubber elastic body 16 on the one axial side (the upper side in FIG. 1) sandwiching the partition member 24, and the first mounting bracket 12 and the second mounting bracket. A pressure receiving chamber 50 is formed in which a pressure fluctuation is generated based on elastic deformation of the main rubber elastic body 16 when vibration is input between the two. Further, on the other side in the axial direction (downward in FIG. 1) across the partition member 24, a part of the wall portion is constituted by the diaphragm 38, and the volume change is easily performed based on the elastic deformation of the diaphragm 38. An allowable equilibrium chamber 52 is formed.

また、オリフィス部材28の周溝36の周方向一方の端部が、仕切部材24を貫通して受圧室50に接続されていると共に、周溝36の周方向他方の端部が、オリフィス部材28の底部乃至は周壁部を貫通して平衡室52に接続されている。これにより、受圧室50と平衡室52を相互に連通せしめるオリフィス通路54が形成されており、それら両室50,52間で、オリフィス通路54を通じての流体流動が許容されるようになっている。   Further, one end in the circumferential direction of the circumferential groove 36 of the orifice member 28 penetrates the partition member 24 and is connected to the pressure receiving chamber 50, and the other end in the circumferential direction of the circumferential groove 36 is connected to the orifice member 28. Are connected to the equilibrium chamber 52 through the bottom or the peripheral wall of each. As a result, an orifice passage 54 that allows the pressure receiving chamber 50 and the equilibrium chamber 52 to communicate with each other is formed, and fluid flow through the orifice passage 54 is allowed between the chambers 50 and 52.

本実施形態では、オリフィス通路54を流動せしめられる流体の共振周波数が、該流体の共振作用に基づいてエンジンシェイク等に相当する10Hz前後の低周波数域の振動に対して有効な防振効果(高減衰効果)が発揮されるようにチューニングされている。オリフィス通路54のチューニングは、例えば、受圧室50や平衡室52の各壁ばね剛性、即ちそれら各室50,52を単位容積だけ変化させるのに必要な圧力変化量に対応する本体ゴム弾性体16やダイヤフラム38の各弾性変形量に基づく特性値を考慮しつつ、オリフィス通路54の通路長さと通路断面積を調節することによって行うことが可能であり、一般に、オリフィス通路54を通じて伝達される圧力変動の位相が変化して略共振状態となる周波数を、当該オリフィス通路54のチューニング周波数として把握することが出来る。   In the present embodiment, the resonance frequency of the fluid that is allowed to flow through the orifice passage 54 is effective against vibrations in a low frequency region around 10 Hz corresponding to an engine shake or the like based on the resonance action of the fluid. It is tuned so that the damping effect is demonstrated. The tuning of the orifice passage 54 is performed by, for example, the rigidity of the wall springs of the pressure receiving chamber 50 and the equilibrium chamber 52, that is, the main rubber elastic body 16 corresponding to the amount of pressure change required to change the chambers 50 and 52 by a unit volume. The pressure fluctuation transmitted through the orifice passage 54 can be adjusted by adjusting the passage length and passage sectional area of the orifice passage 54 in consideration of the characteristic values based on the elastic deformation amounts of the diaphragm 38 and the diaphragm 38. The frequency at which the phase changes to a substantially resonant state can be grasped as the tuning frequency of the orifice passage 54.

さらに、仕切部材24の中央に形成された透孔30が、受圧室50と平衡室52を相互に接続して一つの液室とする開口窓を構成している。   Further, the through hole 30 formed in the center of the partition member 24 constitutes an opening window that connects the pressure receiving chamber 50 and the equilibrium chamber 52 to each other to form one liquid chamber.

このように内部に受圧室50や平衡室52、オリフィス通路54、開口窓(透孔30)を備えたマウント本体には、空気圧式アクチュエータ58が組み付けられている。この空気圧式アクチュエータ58は、略有底円筒形状を有するハウジング金具60に対して、出力部材としての出力金具62が内側から組み付けられた構造とされている。   Thus, the pneumatic actuator 58 is assembled to the mount body having the pressure receiving chamber 50, the equilibrium chamber 52, the orifice passage 54, and the opening window (through hole 30). This pneumatic actuator 58 has a structure in which an output fitting 62 as an output member is assembled from the inside to a housing fitting 60 having a substantially bottomed cylindrical shape.

出力金具62は、下方に開口する略有底円筒形状を有していると共に、金属材料等の硬質材を用いて形成されている。また、出力金具62の底部における適当な箇所には、通孔が貫設されており、かかる通孔を通じて加硫成形された弾性ゴム層64が、出力金具62の内外周面の略全体に亘って被着形成されている。また、出力金具62の下端開口周縁部には、弾性ゴム層64と一体形成されて、斜め下方に広がるテーパ付き鍔状の周壁ゴム66が設けられている。更に、周壁ゴム66の外周縁部には、環状の圧入金具68が加硫接着されている。また、圧入金具68の下端部には、周壁ゴム66と一体形成されたシールリップが被着形成されている。   The output fitting 62 has a substantially bottomed cylindrical shape that opens downward, and is formed using a hard material such as a metal material. Further, a through hole is provided at an appropriate location in the bottom of the output fitting 62, and an elastic rubber layer 64 vulcanized and molded through the through hole extends over substantially the entire inner and outer peripheral surface of the output fitting 62. Are formed. In addition, a tapered flange-shaped peripheral wall rubber 66 that is integrally formed with the elastic rubber layer 64 and extends obliquely downward is provided at the peripheral edge of the lower end opening of the output fitting 62. Further, an annular press fitting 68 is vulcanized and bonded to the outer peripheral edge of the peripheral wall rubber 66. A seal lip formed integrally with the peripheral wall rubber 66 is attached to the lower end portion of the press-fit metal fitting 68.

圧入金具68がハウジング金具60の周壁部に対して圧入固定されて、下端部がシールリップを介してハウジング金具60の底部に密着状に重ね合わせられている。これにより、出力金具62の開口がハウジング金具60の底部で覆蓋されて、出力金具62とハウジング金具60の底部の間に調圧空気室70が形成されている。   The press-fit metal fitting 68 is press-fitted and fixed to the peripheral wall portion of the housing metal fitting 60, and the lower end portion is closely adhered to the bottom portion of the housing metal fitting 60 via the seal lip. Thereby, the opening of the output metal fitting 62 is covered with the bottom of the housing metal fitting 60, and the pressure adjusting air chamber 70 is formed between the output metal fitting 62 and the bottom of the housing metal fitting 60.

また、軸方向に付勢力を及ぼす付勢手段としてのコイルスプリング72が、調圧空気室70に収容されて、一方(図1中、上)の端部が、弾性ゴム層64を介して出力金具62の上底部に支持されていると共に、他方(図1中、下)の端部が、ハウジング金具60の底部に支持されている。それによって、出力金具62とハウジング金具60の間に離隔方向の付勢力が常時及ぼされるようになっている。また、ハウジング金具60の底部中央を貫通してエアポート74が設けられている。このエアポート74を通じて、外部から、調圧空気室70の圧力を制御することが出来るようになっている。   Further, a coil spring 72 as an urging means that exerts an urging force in the axial direction is accommodated in the regulated air chamber 70, and one end (upper in FIG. 1) is output via the elastic rubber layer 64. While being supported by the upper bottom portion of the metal fitting 62, the other end (lower in FIG. 1) is supported by the bottom portion of the housing metal fitting 60. As a result, a biasing force in the separation direction is constantly exerted between the output fitting 62 and the housing fitting 60. An air port 74 is provided through the center of the bottom of the housing fitting 60. Through this air port 74, the pressure in the regulated air chamber 70 can be controlled from the outside.

このような空気圧式アクチュエータ58のハウジング金具60に対してマウント本体の固定筒金具40が圧入固定されている。特に本実施形態では、ハウジング金具60の開口端部に一体形成されたフランジ状部76が、第二の取付金具14において仕切部材24の外周部分および固定筒金具40の外フランジ状部42をかしめ固定したかしめ部20の下端部に重ね合わせられていることによって、マウント本体に対する空気圧式アクチュエータ58の軸方向位置が規定されている。また、出力金具62の先端面が、仕切部材24の透孔30に対してダイヤフラム38を挟んで対向位置せしめられている。   The fixed barrel fitting 40 of the mount body is press-fitted and fixed to the housing fitting 60 of such a pneumatic actuator 58. Particularly in the present embodiment, the flange-like portion 76 integrally formed at the opening end of the housing fitting 60 caulks the outer peripheral portion of the partition member 24 and the outer flange-like portion 42 of the fixed tubular fitting 40 in the second mounting fitting 14. The position of the pneumatic actuator 58 in the axial direction relative to the mount body is defined by being superimposed on the lower end portion of the fixed caulking portion 20. Further, the front end surface of the output fitting 62 is opposed to the through hole 30 of the partition member 24 with the diaphragm 38 interposed therebetween.

また、第一の取付金具12の螺子穴18が図示しない固定ボルトを用いてパワーユニット側の取付部材に螺着固定されると共に、第二の取付金具14に図示しないアウタブラケットが固定されて、アウタブラケットが車両ボデー側の取付部材にボルト等で固定されるようになっている。これにより、エンジンマウント10が、パワーユニットと車両ボデーの間に装着されて、パワーユニットを車両ボデーに防振支持せしめるようになっている。   In addition, the screw hole 18 of the first mounting bracket 12 is screwed and fixed to the mounting member on the power unit side using a fixing bolt (not shown), and an outer bracket (not shown) is fixed to the second mounting bracket 14. The bracket is fixed to a mounting member on the vehicle body side with a bolt or the like. As a result, the engine mount 10 is mounted between the power unit and the vehicle body so that the power unit is supported on the vehicle body in a vibration-proof manner.

かかる装着状態下において、ハウジング金具60のエアポート74に空気管路78が接続され、空気管路78を通じて、調圧空気室70が切換バルブ80に接続されている。切換バルブ80は、例えば電磁バルブ等によって構成されており、調圧空気室70を、大気中と所定の負圧源81とに択一的に連通せしめるようになっている。負圧源81としては、例えば自動車のインテーク側の吸圧器系統やアキュムレータ等が採用される。また、切換バルブ80は、図示しない制御装置と接続されている。制御装置では、自動車に備え付けられた各種センサ等から、自動車の速度やエンジン回転数、減速機選択位置、スロットル開度など、自動車の状態を表す各種情報のうち、必要なものが入力されるようになっており、かかる情報に基づいて、予め設定されたプログラムに従って、マイクロコンピュータのソフトウエア等により、切換バルブ80を構成する電磁ソレノイドに駆動制御信号を出力して、切換バルブ80を切換作動させるようになっている。   Under such a mounted state, an air pipe 78 is connected to the air port 74 of the housing metal fitting 60, and the pressure regulating air chamber 70 is connected to the switching valve 80 through the air pipe 78. The switching valve 80 is constituted by, for example, an electromagnetic valve or the like, and allows the pressure-controlled air chamber 70 to selectively communicate with the atmosphere and a predetermined negative pressure source 81. As the negative pressure source 81, for example, a suction system on the intake side of an automobile, an accumulator, or the like is employed. The switching valve 80 is connected to a control device (not shown). In the control device, necessary information is input from various sensors provided in the vehicle, such as the vehicle speed, the engine speed, the speed reducer selection position, the throttle opening, etc. Based on such information, a drive control signal is output to an electromagnetic solenoid constituting the switching valve 80 by a microcomputer software or the like according to a preset program to switch the switching valve 80. It is like that.

このような調圧空気室70が大気中に接続された状態では、周壁ゴム66の弾性とコイルスプリング72の弾性が出力金具62に作用することにより、出力金具62が上方に弾性的に突出せしめられて、出力金具62の上底部(先端面)が弾性ゴム層64を介してダイヤフラム38の中央下面に当接していると共に、ダイヤフラム38の上面が仕切部材24の透孔30の周縁部(面)に当接している。   In such a state where the pressure adjusting air chamber 70 is connected to the atmosphere, the elasticity of the peripheral wall rubber 66 and the elasticity of the coil spring 72 act on the output fitting 62, so that the output fitting 62 elastically protrudes upward. The upper bottom portion (tip surface) of the output fitting 62 is in contact with the lower center surface of the diaphragm 38 via the elastic rubber layer 64, and the upper surface of the diaphragm 38 is the peripheral portion (surface) of the through hole 30 of the partition member 24. ).

特に、出力金具62が当接するダイヤフラム38の中央部分は、略円板形状を呈する可動膜部82とされており、ダイヤフラム38の径方向中間部分や外周部分に比して厚くされている。   In particular, the central portion of the diaphragm 38 with which the output fitting 62 abuts is a movable film portion 82 having a substantially disk shape, and is thicker than the radially intermediate portion and the outer peripheral portion of the diaphragm 38.

また、出力金具62の先端面の中央部分には、上方に向かって略円形状に開口する凹所84が形成されており、それによって、出力金具62の先端面の外周部分86が、中央部分よりも軸方向外方に突出した形態とされている。特に、出力金具62の先端面の外周部分86が、円弧状の湾曲断面形状とされている。   In addition, a recess 84 is formed in the central portion of the front end surface of the output metal fitting 62 so as to open upward in a substantially circular shape, whereby the outer peripheral portion 86 of the front end surface of the output metal fitting 62 is formed in the central portion. It is set as the form which protruded axially outward rather than. In particular, the outer peripheral portion 86 of the front end surface of the output fitting 62 has an arcuate curved cross-sectional shape.

さらに、凹所84に略全体に亘って弾性ゴム層64が被着されていることに基づき、出力金具62の外周部分86にも弾性ゴム層64が被着されている。この外周部分86に被着された弾性ゴム層64が環状の弾性押圧突部88とされている。弾性押圧突部88は、外周部分86の全体に亘って略一定の厚さ寸法で周方向に延びていることによって、外周部分86と相似形状の円弧状湾曲断面形状を呈している。   Further, the elastic rubber layer 64 is also applied to the outer peripheral portion 86 of the output fitting 62 based on the fact that the elastic rubber layer 64 is applied to the recess 84 over substantially the whole. The elastic rubber layer 64 attached to the outer peripheral portion 86 is an annular elastic pressing protrusion 88. The elastic pressing protrusion 88 extends in the circumferential direction with a substantially constant thickness dimension over the entire outer peripheral portion 86, thereby exhibiting an arcuate curved cross-sectional shape similar to the outer peripheral portion 86.

また、弾性押圧突部88には、図2にも示されているように、径方向に延びて弾性押圧突部88の内周縁部と外周縁部を相互に連通せしめる連通溝90の複数が形成されている。本実施形態では、4つの連通溝90,90,90,90が、弾性押圧突部88の周方向に略等間隔に設けられている。   Further, as shown in FIG. 2, the elastic pressing protrusion 88 has a plurality of communication grooves 90 that extend in the radial direction and allow the inner peripheral edge and the outer peripheral edge of the elastic pressing protrusion 88 to communicate with each other. Is formed. In the present embodiment, four communication grooves 90, 90, 90, 90 are provided at substantially equal intervals in the circumferential direction of the elastic pressing protrusion 88.

而して、上述の如く調圧空気室70が大気中に接続されて、出力金具62がコイルスプリング72により上方に付勢せしめられると、出力金具62の外周部分86が弾性押圧突部88を介してダイヤフラム38の可動膜部82の外周部分に当接すると共に、可動膜部82の外周部分が、仕切部材24の透孔30の周縁部における当接支持部32に当接して、コイルスプリング72の付勢力に基づき、押し付けられた状態が保持されている。本実施形態では、可動膜部82の外周部分が環状押付部として構成されている。   Thus, as described above, when the regulated air chamber 70 is connected to the atmosphere and the output fitting 62 is urged upward by the coil spring 72, the outer peripheral portion 86 of the output fitting 62 causes the elastic pressing projection 88 to move. The outer peripheral portion of the movable film portion 82 of the diaphragm 38, and the outer peripheral portion of the movable film portion 82 contacts the abutting support portion 32 at the peripheral edge portion of the through hole 30 of the partition member 24. The pressed state is held based on the urging force. In the present embodiment, the outer peripheral portion of the movable film portion 82 is configured as an annular pressing portion.

これにより、受圧室50と平衡室52を相互に連通せしめる透孔30がダイヤフラム38の中央の可動膜部82によって閉塞された状態が保持されて、透孔30が遮断状態とされている。上述の説明からも明らかなように、出力金具62の先端面の外周部分86と仕切部材24の当接支持部32の外周部分が、ダイヤフラム38を挟んで互いに相似形状となる円弧状湾曲断面形状で周方向に延びる当接挟持面とされている。   Thus, the state in which the through hole 30 that allows the pressure receiving chamber 50 and the equilibrium chamber 52 to communicate with each other is closed by the movable film portion 82 at the center of the diaphragm 38 is maintained, and the through hole 30 is blocked. As is clear from the above description, the outer peripheral portion 86 of the front end surface of the output fitting 62 and the outer peripheral portion of the abutting support portion 32 of the partition member 24 are similar to each other with an arcuate curved cross-sectional shape sandwiching the diaphragm 38. The contact clamping surface extends in the circumferential direction.

また、可動膜部82が出力金具62により仕切部材24の当接支持部32に押し付けられた状態では、出力金具62の先端面の中央に凹所84が設けられていることによって、可動膜部82が略軸直角方向に平坦に広がる形態で、それら可動膜部82と出力金具62の先端面の中央の間には、内部空間92が形成されている。   Further, when the movable film portion 82 is pressed against the abutting support portion 32 of the partition member 24 by the output metal fitting 62, the movable film portion is provided by providing the recess 84 at the center of the front end surface of the output metal fitting 62. An internal space 92 is formed between the movable film portion 82 and the center of the front end surface of the output fitting 62 in a form in which the 82 is spread flat in a direction substantially perpendicular to the axis.

従って、可動膜部82には、その外周部分が出力金具62の外周部分により仕切部材24の当接支持部32に押し付けられた状態下において、凹所84内の内部空間92に向かう弾性変形が許容されている。   Therefore, the movable film portion 82 is elastically deformed toward the internal space 92 in the recess 84 in a state where the outer peripheral portion is pressed against the abutting support portion 32 of the partition member 24 by the outer peripheral portion of the output fitting 62. Is allowed.

特に本実施形態では、透孔30が可動膜部82で閉塞された状態下で走行こもり音等に相当する高周波小振幅の振動入力に際しては可動膜部82が凹所84の内面に被着された弾性ゴム層64に当接するに至らない変形量とされている一方、エンジンシェイクに相当する低周波大振幅の振動入力に際しては可動膜部82が凹所84(弾性ゴム層64)の内面に当接する変形量となるように、可動膜部82の弾性や凹所84の大きさが設定されている。また、可動膜部82の固有振動数が、走行こもり音等に相当する80〜100Hz前後の高周波の振動周波数域にチューニングされている。   In particular, in the present embodiment, the movable film portion 82 is attached to the inner surface of the recess 84 when a high-frequency, small-amplitude vibration corresponding to a traveling boom noise or the like is input with the through hole 30 closed by the movable film portion 82. While the amount of deformation does not reach the elastic rubber layer 64, the movable film portion 82 is formed on the inner surface of the recess 84 (elastic rubber layer 64) when low-frequency and large-amplitude vibration corresponding to engine shake is input. The elasticity of the movable film portion 82 and the size of the recess 84 are set so that the deformation amount comes into contact. In addition, the natural frequency of the movable film portion 82 is tuned to a high-frequency vibration frequency range of about 80 to 100 Hz corresponding to traveling noise and the like.

また、内部空間92は、出力金具62の弾性押圧突部88に形成された連通溝90を通じてハウジング金具60内のダイヤフラム38の外周部分と周壁ゴム66の間の空間に連通せしめられており、更にハウジング金具60の周壁部に貫設された通孔94を通じて外部空間に連通せしめられている。即ち、かかる連通溝90によって、透孔30を閉塞せしめた状態下でダイヤフラム38の可動膜部82で覆蓋された凹所84の内部空間92を外部空間に連通せしめる空気連通路が形成されている。   The internal space 92 is communicated with the space between the outer peripheral portion of the diaphragm 38 in the housing metal fitting 60 and the peripheral wall rubber 66 through the communication groove 90 formed in the elastic pressing protrusion 88 of the output metal fitting 62. The housing fitting 60 is communicated with the external space through a through hole 94 penetrating the peripheral wall portion. That is, the communication groove 90 forms an air communication path that allows the internal space 92 of the recess 84 covered with the movable film portion 82 of the diaphragm 38 to communicate with the external space with the through hole 30 closed. .

一方、調圧空気室70が負圧源81に接続された状態下では、周壁ゴム66の弾性とコイルスプリング72の弾性に抗して、空気室70内に及ぼされる負圧と外部大気圧との圧力差に基づいて出力金具62が調圧空気室70の内方に吸引され、軸方向下方に変位せしめられることとなる。その結果、図3にも示されているように、ダイヤフラム38の可動膜部82の外周部分が仕切部材24の透孔30の周縁部における当接支持部32から離隔せしめられて、透孔30が開放され、透孔30を通じて受圧室50と平衡室52が連通状態とされている。   On the other hand, under the state in which the regulated air chamber 70 is connected to the negative pressure source 81, the negative pressure exerted in the air chamber 70 and the external atmospheric pressure are resisted against the elasticity of the peripheral wall rubber 66 and the elasticity of the coil spring 72. Based on the pressure difference, the output fitting 62 is sucked inward of the regulated air chamber 70 and is displaced downward in the axial direction. As a result, as shown in FIG. 3, the outer peripheral portion of the movable film portion 82 of the diaphragm 38 is separated from the abutting support portion 32 at the peripheral edge portion of the through hole 30 of the partition member 24. Is opened, and the pressure receiving chamber 50 and the equilibrium chamber 52 are in communication with each other through the through hole 30.

本実施形態では、切換バルブ80が制御装置により、自動車の走行状態と、停車状態によって切り換えられるようになっている。即ち、走行状態下では、調圧空気室70が大気中に接続される。一方、停車状態下では、調圧空気室70が負圧源81に接続されるようになっている。本実施形態では、コイルスプリング72の付勢力に基づいて可動膜部82を透孔30の周縁部に対して押し付け状態に保持せしめて透孔30を遮断する空気圧制御手段が、切換バルブ80や制御装置を含んで構成されている。   In the present embodiment, the switching valve 80 is switched by the control device according to the traveling state of the automobile and the stopped state. That is, under the traveling state, the regulated air chamber 70 is connected to the atmosphere. On the other hand, the regulated air chamber 70 is connected to the negative pressure source 81 when the vehicle is stopped. In the present embodiment, the pneumatic control means for holding the movable film portion 82 against the peripheral edge of the through hole 30 based on the biasing force of the coil spring 72 and blocking the through hole 30 is the switching valve 80 or the control. It is configured to include the device.

ここでエンジンマウント10における具体的な作動態様の一つを示す。防振すべき振動として、(1)低周波大振幅振動であるエンジンシェイクや(2)高周波小振幅振動である走行こもり音、(3)中周波中振幅振動であるアイドリング振動の3種類の振動を考慮することとし、各振動に対する防振効果を以下に説明する。なお、(1)エンジンシェイクおよび(2)走行こもり音は、何れも自動車の走行時に問題となる振動であり、(3)アイドリング振動は、自動車の停車時に問題となる振動である。   Here, one of the specific operation | movement aspects in the engine mount 10 is shown. There are three types of vibration that should be isolated: (1) engine shake, which is low-frequency, large-amplitude vibration, (2) running noise, which is high-frequency, small-amplitude vibration, and (3) idle vibration, which is medium-frequency, medium-amplitude vibration. The anti-vibration effect for each vibration will be described below. Note that (1) the engine shake and (2) the running-over noise are vibrations that are problematic when the automobile is running, and (3) idling vibrations are vibrations that are problematic when the automobile is stopped.

(1)エンジンシェイクに対する防振効果
エンジンシェイク等の低周波大振幅振動の入力時には、受圧室50に対して大きな振幅の圧力変動が惹起されることとなる。その際、調圧空気室70が大気中に接続されていて、コイルスプリング72の付勢力に基づき仕切部材24の透孔30がダイヤフラム38の可動膜部82で閉塞された状態が保持されている。そこで、受圧室50に大きな圧力変動が生ぜしめられることに伴い、可動膜部82が凹所84内に向かって弾性変形する。特に、スピードブレーカや凹凸状の荒れた路面等を走行すると、一層大きな圧力変動が惹起されて、可動膜部82の凹所84内に向かう弾性変形量が大きくなる。なお、コイルスプリング72の付勢力は、透孔30を通じて可動膜部82に及ぼされる振動入力時の受圧室50の正圧に抗して、可動膜部82を透孔30の周囲に押しつけて透孔30を閉塞状態に保持し得るだけの十分な大きさに設定される。
(1) Anti-Vibration Effect against Engine Shake When a low-frequency large-amplitude vibration such as an engine shake is input, a large amplitude pressure fluctuation is induced in the pressure receiving chamber 50. At that time, the regulated air chamber 70 is connected to the atmosphere, and the state in which the through hole 30 of the partition member 24 is closed by the movable film portion 82 of the diaphragm 38 based on the biasing force of the coil spring 72 is maintained. . Therefore, as the large pressure fluctuation is generated in the pressure receiving chamber 50, the movable film portion 82 is elastically deformed into the recess 84. In particular, when the vehicle travels on a speed breaker, a rough road surface, or the like, a larger pressure fluctuation is induced, and the amount of elastic deformation toward the recess 84 of the movable film portion 82 increases. The urging force of the coil spring 72 presses the movable film portion 82 around the through hole 30 against the positive pressure of the pressure receiving chamber 50 at the time of vibration input exerted on the movable film portion 82 through the through hole 30. It is set to a size large enough to hold the hole 30 in the closed state.

そこにおいて、図4にも示されているように、可動膜部82が出力金具62の上端面における凹所84の内面に被着された弾性ゴム層64に当接することによって、可動膜部82の弾性変形量が制限されるようになっている。即ち、可動膜部82の弾性変形量を制限する変形量制限機構が出力金具62や凹所84の内面を含んで構成されている。   In this case, as shown in FIG. 4, the movable film portion 82 is brought into contact with the elastic rubber layer 64 attached to the inner surface of the recess 84 in the upper end surface of the output metal fitting 62. The amount of elastic deformation is limited. That is, the deformation amount limiting mechanism for limiting the elastic deformation amount of the movable film portion 82 includes the output fitting 62 and the inner surface of the recess 84.

これにより、可動膜部82の圧力吸収作用は、エンジンシェイクなどの低周波大振幅振動に対しては実質的に機能し得ず、かかる大振幅の振動入力時に受圧室50と平衡室52の間に生ぜしめられる相対的な圧力変動によりオリフィス通路54を通じての流体流動量が効果的に確保されて、オリフィス通路54を流動せしめられる流体の共振作用に基づいて、エンジンシェイクに対して有効な防振効果(高減衰効果)が発揮されるのである。   As a result, the pressure absorbing action of the movable film portion 82 cannot substantially function for low-frequency large-amplitude vibration such as engine shake. The amount of fluid flow through the orifice passage 54 is effectively ensured by the relative pressure fluctuation generated in the engine, and the vibration isolation effective for the engine shake is based on the resonance action of the fluid flowing through the orifice passage 54. The effect (high attenuation effect) is exhibited.

(2)走行こもり音等に対する防振効果
オリフィス通路54のチューニング周波数よりも高い走行こもり音等の高周波小振幅振動の入力時には、受圧室50に対して小さな振幅の圧力変動が惹起されることとなる。その際には、上記(1)に記載のように調圧空気室70が大気中に接続されていて、コイルスプリング72の付勢力に基づき仕切部材24の透孔30がダイヤフラム38の可動膜部82で閉塞された状態が保持されている。そこで、受圧室50に圧力変動が生ぜしめられることに伴い、可動膜部82が弾性変形する。特に受圧室50の圧力変動は小さいことから、可動膜部82が凹所84の内面に当接することなく、有効に弾性変形する。
(2) Anti-vibration effect against traveling boom noise, etc. When a high frequency small amplitude vibration such as a traveling boom noise higher than the tuning frequency of the orifice passage 54 is input, a pressure fluctuation with a small amplitude is induced in the pressure receiving chamber 50. Become. At that time, as described in the above (1), the regulated air chamber 70 is connected to the atmosphere, and the through-hole 30 of the partition member 24 is formed on the movable film portion of the diaphragm 38 based on the urging force of the coil spring 72. The state closed at 82 is maintained. Therefore, the movable film portion 82 is elastically deformed as pressure fluctuations are generated in the pressure receiving chamber 50. In particular, since the pressure fluctuation in the pressure receiving chamber 50 is small, the movable film portion 82 is effectively elastically deformed without contacting the inner surface of the recess 84.

すなわち、高周波小振幅振動の入力に際して、それよりも低周波数域にチューニングされたオリフィス通路54が反共振的な作用によって流体流通抵抗が著しく大きくなって、実質的に閉塞状態とされることとなっても、可動膜部82の弾性変形による液圧吸収機能がはたらいて、受圧室50の圧力変動が吸収されることにより、オリフィス通路54の実質的な閉塞化に起因する著しい高動ばね化が回避されることとなる。それ故、高周波小振幅振動に対する良好な防振効果(低動ばね特性に基づく振動絶縁効果)が発揮されるのである。   That is, when high frequency small amplitude vibration is input, the orifice passage 54 tuned to a lower frequency range than that has a significantly increased fluid flow resistance due to antiresonant action, and is substantially closed. However, the hydraulic pressure absorption function due to the elastic deformation of the movable film portion 82 works, and the pressure fluctuation in the pressure receiving chamber 50 is absorbed, so that a significantly high dynamic spring due to the substantial blockage of the orifice passage 54 is achieved. It will be avoided. Therefore, a good anti-vibration effect (vibration insulation effect based on low dynamic spring characteristics) against high-frequency small-amplitude vibration is exhibited.

上述の説明からも明らかなように、本実施形態では、受圧室50の圧力変動を吸収する液圧吸収機構が、ダイヤフラム38の可動膜部82や空間92を含んで構成されていると共に、可動膜部82が当接せしめられる凹所84の内面を含んで可動膜部82の変形量制限機構が構成されている。また、空気圧式アクチュエータ58の作動によって透孔30を開閉する液圧吸収機構内蔵式弁体が、可動膜部82や空間92、出力金具62を含んで構成されている。   As is clear from the above description, in this embodiment, the hydraulic pressure absorption mechanism that absorbs pressure fluctuations in the pressure receiving chamber 50 includes the movable film portion 82 and the space 92 of the diaphragm 38 and is movable. A deformation amount limiting mechanism for the movable film portion 82 is configured including the inner surface of the recess 84 with which the film portion 82 is brought into contact. Further, the valve body with a built-in hydraulic pressure absorbing mechanism that opens and closes the through hole 30 by the operation of the pneumatic actuator 58 includes the movable film portion 82, the space 92, and the output fitting 62.

(3)アイドリング振動に対する防振効果
オリフィス通路54のチューニング周波数よりも高いアイドリング振動等の中周波中振幅振動の入力時には、受圧室50に対して或る程度の振幅の圧力変動が惹起されることとなる。その際、オリフィス通路54は、上記(2)の場合と同様に、反共振的な作用によって流体流通抵抗が著しく大きくなり、実質的に閉塞状態とされる。
(3) Anti-vibration effect against idling vibration When a medium frequency medium amplitude vibration such as idling vibration higher than the tuning frequency of the orifice passage 54 is input, a pressure fluctuation with a certain amplitude is induced in the pressure receiving chamber 50. It becomes. At that time, as in the case of (2), the orifice passage 54 is substantially closed due to a significantly increased fluid flow resistance due to an anti-resonant action.

そのようなアイドリング振動が入力される自動車の停車状態下では、調圧空気室70が負圧源81に接続されるように、空気圧制御回路が切り換え制御されることとなる。なお、この切り換え制御は、例えば自動車の速度信号やギヤ信号(ニュートラル又はパーキング)とエンジン回転信号によって自動車が停車アイドリング状態であることを確認して、切換バルブ80を切り換えることで実現される。このように調圧空気室70が負圧源81に接続されると、コイルスプリング72の付勢力に抗して、ダイヤフラム38の可動膜部82の外周部分が仕切部材24の透孔30の周縁部から離隔せしめられて、受圧室50と平衡室52が透孔30を通じて連通状態とされる。要するに、アイドリング状態で調圧空気室70に及ぼされる負圧駆動力の方が、コイルスプリング72による付勢力よりも大きな力で出力金具62をマウント中心軸下方に変位せしめ得るように調節されている。   When the idling vibration is input, the air pressure control circuit is switched and controlled so that the regulated air chamber 70 is connected to the negative pressure source 81. This switching control is realized, for example, by switching the switching valve 80 after confirming that the vehicle is in the idling state by the vehicle speed signal, gear signal (neutral or parking) and engine rotation signal. When the regulated air chamber 70 is connected to the negative pressure source 81 in this way, the outer peripheral portion of the movable film portion 82 of the diaphragm 38 is against the peripheral edge of the through hole 30 of the partition member 24 against the urging force of the coil spring 72. The pressure receiving chamber 50 and the equilibrium chamber 52 are in communication with each other through the through hole 30. In short, the negative pressure driving force exerted on the regulated air chamber 70 in the idling state is adjusted so that the output fitting 62 can be displaced below the mount center axis with a force larger than the biasing force by the coil spring 72. .

これにより、受圧室50と平衡室52の仕切りが解除されて、実質的に一つの流体室48となり、本体ゴム弾性体16の弾性変形に基づく流体室48の圧力変動が、ダイヤフラム38の弾性変形に基づき吸収される。それ故、アイドリング振動に対して有効な防振効果(低動ばね特性に基づく振動絶縁効果)が発揮され得るのである。要するに、受圧室50と平衡室52が透孔30で連通せしめられた状態下で発現される一体的な流体封入領域(流体室48)は、その壁部の一部がダイヤフラム38で構成されていることにより、容積変化が容易に許容されて実質的に単一の大きな平衡室として機能し得るようになっている。   As a result, the partition between the pressure receiving chamber 50 and the equilibrium chamber 52 is released to substantially become one fluid chamber 48, and the pressure fluctuation of the fluid chamber 48 based on the elastic deformation of the main rubber elastic body 16 causes the elastic deformation of the diaphragm 38. To be absorbed. Therefore, an effective anti-vibration effect (vibration insulation effect based on low dynamic spring characteristics) against idling vibration can be exhibited. In short, the integral fluid-filled region (fluid chamber 48) that is expressed in a state where the pressure-receiving chamber 50 and the equilibrium chamber 52 are communicated with each other through the through-hole 30 is configured such that a part of the wall portion is configured by the diaphragm 38. This allows volume changes to be easily tolerated so that it can function as a substantially single large equilibrium chamber.

ここにおいて、透孔30は、受圧室50と平衡室52を仕切るものでなく、防振すべき振動の入力時、具体的にはアイドリング振動の入力時において透孔30を通じて流動せしめられる流体の共振作用による悪影響が発生しないように、十分に大きな開口面積をもって形成されている。より具体的には、少なくとも50Hz以下、より好適には100Hz以下の周波数域の振動入力時においては、透孔30を流動せしめられる流体に共振現象などが生ぜしめられることなく、受圧室50と平衡室52に対して略位相差のない一体的な圧力変動が惹起されるように、かかる透孔30が大きな開口面積と小さな長さ寸法をもって、形成されているのである。これによって、アイドリング振動の入力時には、実質的に封入流体が存在せずに本体ゴム弾性体16のばね特性だけによるかのような低動ばね特性が効果的に発揮されるように設定されている。   Here, the through-hole 30 does not separate the pressure receiving chamber 50 and the equilibrium chamber 52, and resonance of the fluid that is caused to flow through the through-hole 30 at the time of input of vibration to be vibrated, specifically, at the time of input of idling vibration. It is formed with a sufficiently large opening area so that adverse effects due to the action do not occur. More specifically, at the time of vibration input in a frequency range of at least 50 Hz or less, more preferably 100 Hz or less, the fluid that is caused to flow through the through-hole 30 is not balanced with the pressure receiving chamber 50 without causing a resonance phenomenon or the like. The through-hole 30 is formed with a large opening area and a small length so that an integrated pressure fluctuation with substantially no phase difference is induced with respect to the chamber 52. Thus, at the time of idling vibration input, the low dynamic spring characteristic as if by only the spring characteristic of the main rubber elastic body 16 is effectively exhibited without substantially containing the sealed fluid. .

従って、上述の如き構造とされた自動車用エンジンマウント10においては、空気圧式アクチュエータ58の作動により透孔30を開閉する弁体が、出力金具62により仕切部材24に押し付けられたダイヤフラム38の可動膜部82の凹所84内への弾性変形を許容し且つ可動膜部82の凹所84内面への当接によってその弾性変形量を制限する変形量制限機構付きの液圧吸収機構を内蔵した構造とされていることから、全体としてコンパクト化が達成されつつ、自動車の走行時におけるエンジンシェイク等の低周波大振幅振動や走行こもり音等の高周波小振幅振動、自動車の停車時におけるアイドリング振動等の中周波中振幅振動など、周波数域や振幅が異なる複数の振動に対して高度な防振性能が発揮され得るのである。   Therefore, in the automobile engine mount 10 having the above-described structure, the movable body of the diaphragm 38 in which the valve body that opens and closes the through hole 30 by the operation of the pneumatic actuator 58 is pressed against the partition member 24 by the output fitting 62. Structure having a built-in hydraulic pressure absorbing mechanism with a deformation amount limiting mechanism that allows elastic deformation of the portion 82 into the recess 84 and limits the amount of elastic deformation by contacting the inner surface of the movable film portion 82 with the recess 84 Therefore, while achieving compactness as a whole, low-frequency large-amplitude vibrations such as engine shake during driving of automobiles, high-frequency small-amplitude vibrations such as running-over noise, idling vibrations when the automobile stops, etc. A high level of anti-vibration performance can be exhibited against a plurality of vibrations having different frequency ranges and amplitudes, such as medium frequency medium amplitude vibrations.

また、本実施形態では、空気圧式アクチュエータ58のハウジング金具60のフランジ状部76が、仕切部材24の外周部分と共に第二の取付金具14のかしめ部20にかしめ固定されず、かしめ部20の下端部に当接された構造とされていることによって、組み付け作業が容易になることに加え、フランジ状部76をかしめ固定する程にかしめ部20を大形化する必要がないことから、マウント10の更なるコンパクト化が達成され得る。   Further, in the present embodiment, the flange-like portion 76 of the housing bracket 60 of the pneumatic actuator 58 is not caulked and fixed to the caulking portion 20 of the second mounting bracket 14 together with the outer peripheral portion of the partition member 24, and the lower end of the caulking portion 20. Since the structure abutted on the portion facilitates the assembling work, it is not necessary to enlarge the caulking portion 20 to the extent that the flange-like portion 76 is caulked and fixed. Further downsizing can be achieved.

さらに、本実施形態では、透孔30がダイヤフラム38の可動膜部82により閉塞される状態下において、可動膜部82の外周部分が、互いに相似形状の円弧状湾曲断面形状を呈する仕切部材24の当接支持部32と出力金具62の外周部分86の間に挟圧支持せしめられている。これにより、挟圧力を可動膜部86の外周部分に効果的に作用せしめることが可能となり、可動膜部82による透孔30の閉塞性が向上されて、透孔30を通じての受圧室50の圧力漏れが一層効果的に抑えられる。   Furthermore, in the present embodiment, the outer peripheral portion of the movable film portion 82 has a similar arcuate curved cross-sectional shape in a state where the through hole 30 is closed by the movable film portion 82 of the diaphragm 38. The abutting support portion 32 and the outer peripheral portion 86 of the output metal fitting 62 are supported by pressing. As a result, it is possible to effectively apply the clamping pressure to the outer peripheral portion of the movable film portion 86, and the closing performance of the through hole 30 by the movable film portion 82 is improved, and the pressure of the pressure receiving chamber 50 through the through hole 30 is improved. Leakage is more effectively suppressed.

更にまた、出力金具62の外周部分86が弾性押圧突部88を介して可動膜部82に当接するようになっているため、可動膜部82の耐久性能が向上され得る。   Furthermore, since the outer peripheral portion 86 of the output metal fitting 62 comes into contact with the movable film portion 82 via the elastic pressing projection 88, the durability performance of the movable film portion 82 can be improved.

また、本実施形態では、透孔30がダイヤフラム38の可動膜部82により閉塞されて、凹所84の開口部が可動膜部82により覆蓋された形態下、凹所84の内部空間92が、弾性押圧突部88に形成された連通溝90やハウジング金具60に形成された通孔94を通じて外部空間に連通せしめられていることによって、内部空間92に空気が留まることに起因する弾性押圧突部88の可動膜部82への当接乃至は離隔時の異音の発生が好適に抑えられる。   In the present embodiment, the through-hole 30 is closed by the movable film portion 82 of the diaphragm 38 and the opening of the recess 84 is covered with the movable film portion 82. The elastic pressing protrusion due to air remaining in the internal space 92 by being communicated with the external space through the communication groove 90 formed in the elastic pressing protrusion 88 and the through hole 94 formed in the housing fitting 60. The generation of abnormal noise during contact or separation of the movable film 88 with the movable film portion 82 is preferably suppressed.

以上、本発明の一実施形態について詳述してきたが、かかる実施形態における具体的な記載によって、本発明は、何等限定されるものでなく、当業者の知識に基づいて種々なる変更、修正、改良等を加えた態様で実施可能であり、また、そのような実施態様が、本発明の趣旨を逸脱しない限り、何れも、本発明の範囲内に含まれるものであることは、言うまでもない。   As mentioned above, although one embodiment of the present invention has been described in detail, the present invention is not limited in any way by the specific description in the embodiment, and various changes, modifications, and modifications based on the knowledge of those skilled in the art. Needless to say, the present invention can be implemented in a mode with improvements and the like, and all such modes are included in the scope of the present invention without departing from the gist of the present invention.

例えば、可動膜部82や出力金具62、凹所84、仕切部材24、オリフィス部材28、透孔30等における形状や大きさ、構造等の形態は、例示の如きものに限定されるものでない。   For example, the shapes of the movable film portion 82, the output metal fitting 62, the recess 84, the partition member 24, the orifice member 28, the through hole 30, and the like are not limited to those illustrated.

前記実施形態では、可動膜部82が略全体に亘って略一定の厚さ寸法とされていたが、要求される変形特性乃至は防振特性や製作性等に応じて、可動膜部82に凹凸が形成されても良い。特に、可動膜部82において、仕切部材24における透孔30の開口周縁部(当接支持部32)に対して空気圧式アクチュエータ58の出力金具62によって押し付けられる環状押付部(外周部分)の少なくとも一方の面において周方向に複数の凹凸が設けられていても良い。これにより、環状押付部が透孔30の周縁部乃至は出力金具62に当接した際に、当接部分の面積が小さくされて、当接乃至は離隔に伴う異音の発生が抑えられるのである。   In the above-described embodiment, the movable film portion 82 has a substantially constant thickness dimension over substantially the whole. However, the movable film portion 82 is provided with the movable film portion 82 according to required deformation characteristics, vibration proof characteristics, manufacturability, or the like. Irregularities may be formed. In particular, in the movable film portion 82, at least one of the annular pressing portions (outer peripheral portions) pressed by the output fitting 62 of the pneumatic actuator 58 against the opening peripheral portion (contact support portion 32) of the through hole 30 in the partition member 24. A plurality of irregularities may be provided in the circumferential direction on the surface. As a result, when the annular pressing portion comes into contact with the peripheral portion of the through hole 30 or the output fitting 62, the area of the contact portion is reduced, and the generation of abnormal noise due to contact or separation is suppressed. is there.

加えて、前記実施形態では、本発明を自動車用エンジンマウント10に適用したものの具体例について説明したが、本発明は、自動車用ボデーマウントやデフマウント等の他、自動車以外の各種振動体の防振マウントに対して、何れも、適用可能である。   In addition, in the above-described embodiments, specific examples of applying the present invention to the engine mount 10 for automobiles have been described. However, the present invention can prevent various vibration bodies other than automobiles other than automobile body mounts and differential mounts. Any of the vibration mounts can be applied.

本発明の一実施形態としての自動車用エンジンマウントを示す縦断面図であって、図2のI−I断面に相当する図。It is a longitudinal cross-sectional view which shows the engine mount for motor vehicles as one Embodiment of this invention, Comprising: The figure equivalent to the II cross section of FIG. 同自動車用エンジンマウントの一部を構成する出力金具を備えた弾性ゴム層の一体加硫成形品の平面図。The top view of the integral vulcanization molding product of the elastic rubber layer provided with the output metal fitting which constitutes a part of engine mount for the vehicles. 同自動車用エンジンマウントの一作動状態を拡大して示す縦断面図。The longitudinal cross-sectional view which expands and shows the operating state of the engine mount for the said motor vehicles. 同自動車用エンジンマウントの別の一作動形態を拡大して示す縦断面図。The longitudinal cross-sectional view which expands and shows another one operating form of the engine mount for the said motor vehicles.

符号の説明Explanation of symbols

10:自動車用エンジンマウント、12:第一の取付金具、14:第二の取付金具、16:本体ゴム弾性体、24:仕切部材、30:透孔、32:当接支持部、38:ダイヤフラム、48:流体室、50:受圧室、52:平衡室、54:オリフィス通路、58:空気圧式アクチュエータ、60:ハウジング金具、62:出力金具、72:コイルスプリング、82:可動膜部、84:凹所、92:空間 DESCRIPTION OF SYMBOLS 10: Engine mount for motor vehicles, 12: 1st attachment metal fitting, 14: 2nd attachment metal fitting, 16: Main body rubber elastic body, 24: Partition member, 30: Through-hole, 32: Abutting support part, 38: Diaphragm 48: Fluid chamber, 50: Pressure receiving chamber, 52: Equilibrium chamber, 54: Orifice passage, 58: Pneumatic actuator, 60: Housing fitting, 62: Output fitting, 72: Coil spring, 82: Movable membrane part, 84: Recess, 92: space

Claims (7)

第一の取付部材を筒状を有する第二の取付部材の軸方向一方の開口部側に離隔配置して、それら第一の取付部材と第二の取付部材を本体ゴム弾性体で連結すると共に、該第二の取付部材の軸方向他方の開口部を可撓性ゴム膜で覆蓋することにより、該本体ゴム弾性体と該可撓性ゴム膜の間に非圧縮性流体が封入された流体室を形成し、該第二の取付部材で支持された仕切部材で該流体室を仕切って、該流体室における該仕切部材を挟んだ両側に壁部の一部が該本体ゴム弾性体で構成された受圧室と壁部の一部が該可撓性ゴム膜で構成された平衡室を形成して、それら受圧室と平衡室を相互に連通せしめるオリフィス通路を設けた流体封入式防振装置において、
前記受圧室と前記平衡室を相互に接続して一つの液室とする開口窓を前記仕切部材の中央部分に設ける一方、前記可撓性ゴム膜を挟んで該平衡室と反対側に空気圧式アクチュエータを配設して該空気圧式アクチュエータにおける硬質の出力部材の先端面を該開口窓に対して該可撓性ゴム膜を挟んで対向位置せしめ、該可撓性ゴム膜の中央部分を該仕切部材における該開口窓の開口周縁部に押し付けることで該開口窓を閉塞状態に保持せしめる付勢手段を該空気圧式アクチュエータに設けると共に、該出力部材の先端面に凹所を形成して、該出力部材により該仕切部材に押し付けられた該可撓性ゴム膜の該凹所内への弾性変形を許容し、且つ該可撓性ゴム膜の該凹所内面への当接によって該可撓性ゴム膜の弾性変形量を制限する変形量制限機構付きの液圧吸収機構を構成することにより、該空気圧式アクチュエータの作動によって前記開口窓を開閉する液圧吸収機構内蔵式弁体を設けたことを特徴とする流体封入式防振装置。
The first mounting member is spaced apart on the one opening side in the axial direction of the second mounting member having a cylindrical shape, and the first mounting member and the second mounting member are connected by the main rubber elastic body. A fluid in which an incompressible fluid is sealed between the main rubber elastic body and the flexible rubber film by covering the other opening in the axial direction of the second mounting member with a flexible rubber film. Forming a chamber, partitioning the fluid chamber with a partition member supported by the second mounting member, and forming part of the wall portion on both sides of the partition member in the fluid chamber with the main rubber elastic body A fluid-filled vibration isolator having an orifice passage that forms a balanced chamber in which a part of the pressure receiving chamber and a wall portion are formed of the flexible rubber film and communicates the pressure receiving chamber and the balanced chamber with each other In
An opening window that connects the pressure receiving chamber and the equilibrium chamber to each other to form one liquid chamber is provided in a central portion of the partition member, and on the opposite side to the equilibrium chamber with the flexible rubber film interposed therebetween. An actuator is disposed so that the distal end surface of the rigid output member in the pneumatic actuator is positioned opposite to the opening window with the flexible rubber film interposed therebetween, and the central portion of the flexible rubber film is divided into the partition The pneumatic actuator is provided with urging means for holding the opening window in a closed state by being pressed against the peripheral edge of the opening window of the member, and a recess is formed in the front end surface of the output member to The flexible rubber film is allowed to elastically deform into the recess of the flexible rubber film pressed against the partition member by a member, and the flexible rubber film is brought into contact with the inner surface of the recess. Deformation Limiting Mechanism for Limiting Elastic Deformation of Steel By configuring the Kino hydraulic absorbing mechanism, the fluid filled type vibration damping device, characterized in that a fluid pressure absorbing mechanism built-valve body for opening and closing the opening window by the operation of the air pressure actuator.
前記オリフィス通路がエンジンシェイクに相当する低周波数域にチューニングされていると共に、前記開口窓が前記液圧吸収機構内蔵式弁体で閉塞された状態下で走行こもり音に相当する高周波小振幅の振動入力に際しては前記可撓性ゴム膜が前記凹所内面に当接するに至らない変形量とされる一方、エンジンシェイクに相当する低周波大振幅の振動入力に際しては該可撓性ゴム膜が前記凹所内面に当接する変形量となるように、該液圧吸収機構内蔵式弁体を構成する該可撓性ゴム膜の弾性と該凹所の大きさが設定されて自動車用エンジンマウントが構成されている請求項1に記載の流体封入式防振装置。   The orifice passage is tuned to a low frequency range corresponding to an engine shake, and the vibration having a high frequency and a small amplitude corresponding to a traveling booming noise is obtained in a state where the opening window is closed by the valve body with a built-in hydraulic pressure absorption mechanism. When the input is performed, the amount of deformation is such that the flexible rubber film does not come into contact with the inner surface of the recess. On the other hand, when the vibration is input at a low frequency and a large amplitude corresponding to an engine shake, the flexible rubber film is not deformed. The engine mount for automobiles is configured by setting the elasticity of the flexible rubber film and the size of the recess constituting the valve body with a built-in hydraulic pressure absorption mechanism so that the deformation amount comes into contact with the inner surface. The fluid-filled vibration isolator according to claim 1. 前記空気圧式アクチュエータに接続されて、自動車の停車状態下で該空気圧式アクチュエータに負圧を及ぼすことにより、前記付勢手段の付勢力に抗して前記仕切部材の前記開口窓から前記液圧吸収機構内蔵式弁体を離隔状態に保持せしめて該開口窓を開放させる一方、自動車の走行状態下で該空気圧式アクチュエータを大気に連通させることにより、該付勢手段の付勢力に基づいて該仕切部材の該開口窓に対して該液圧吸収機構内蔵式弁体を押し付け状態に保持せしめて該開口窓を遮断させる空気圧制御手段を設けた請求項2に記載の流体封入式防振装置。   The hydraulic pressure is absorbed from the opening window of the partition member against the urging force of the urging means by applying a negative pressure to the pneumatic actuator in a stationary state of the automobile connected to the pneumatic actuator. The mechanism-equipped valve body is held in a separated state to open the opening window, while the pneumatic actuator is communicated with the atmosphere while the automobile is running, so that the partition is based on the urging force of the urging means. 3. The fluid filled type vibration damping device according to claim 2, further comprising air pressure control means for holding the valve body with a built-in hydraulic pressure absorption mechanism pressed against the opening window of the member to block the opening window. 前記液圧吸収機構内蔵式弁体には、前記開口窓を閉塞せしめた状態下で前記可撓性ゴム膜で覆蓋された前記凹所の内部空間を外部空間に連通せしめる空気連通路が形成されている請求項1乃至3の何れか一項に記載の流体封入式防振装置。   The valve body with a built-in hydraulic pressure absorption mechanism is formed with an air communication path that allows the internal space of the recess, which is covered with the flexible rubber film, to communicate with the external space with the opening window closed. The fluid-filled vibration isolator according to any one of claims 1 to 3. 前記空気圧式アクチュエータの前記出力部材は、先端面の外周部分において環状の弾性押圧突部を備えており、この弾性押圧突部によって該出力部材が前記可撓性ゴム膜を前記仕切部材における前記開口窓の開口周縁部に押し付けるようになっていると共に、該弾性押圧突部には、周上の少なくとも一カ所に連通溝が設けられており、この連通溝によって前記空気連通路が形成されている請求項4に記載の流体封入式防振装置。   The output member of the pneumatic actuator is provided with an annular elastic pressing protrusion at the outer peripheral portion of the distal end surface, and the output member causes the flexible rubber film to open the flexible rubber film by the elastic pressing protrusion. The elastic pressing projection is provided with a communication groove in at least one place on the circumference, and the air communication path is formed by the communication groove. The fluid-filled vibration isolator according to claim 4. 前記可撓性ゴム膜には、前記仕切部材における前記開口窓の開口周縁部に対して前記空気圧式アクチュエータの前記出力部材によって押し付けられる環状押付部の少なくとも一方の面において周方向に複数の凹凸が設けられている請求項1乃至5の何れか一項に記載の流体封入式防振装置。   The flexible rubber film has a plurality of irregularities in the circumferential direction on at least one surface of an annular pressing portion that is pressed by the output member of the pneumatic actuator against an opening peripheral portion of the opening window in the partition member. The fluid-filled type vibration damping device according to claim 1, wherein the fluid-filled type vibration damping device is provided. 前記空気圧式アクチュエータにおける前記出力部材の先端面の外周部分と、該出力部材の先端面の外周部分によって前記可撓性ゴム膜が押し付けられる前記仕切部材の前記開口窓の開口周縁部とが、該可撓性ゴム膜を挟んで互いに相似形状となる円弧状湾曲断面形状で周方向に延びる当接挟持面とされている請求項1乃至6の何れか一項に記載の流体封入式防振装置。   An outer peripheral portion of the front end surface of the output member in the pneumatic actuator, and an opening peripheral portion of the opening window of the partition member against which the flexible rubber film is pressed by the outer peripheral portion of the front end surface of the output member, The fluid-filled vibration isolator according to any one of claims 1 to 6, wherein the fluid-filled vibration isolator is an abutting and clamping surface extending in the circumferential direction with arcuate curved cross-sectional shapes that are similar to each other with the flexible rubber film interposed therebetween. .
JP2006307529A 2006-11-14 2006-11-14 Fluid-sealed vibration isolator Pending JP2008121811A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010090923A (en) * 2008-10-03 2010-04-22 Komatsu Ltd Liquid sealed mount
JP2010249288A (en) * 2009-04-20 2010-11-04 Bridgestone Corp Vibration control device
JP2010255831A (en) * 2009-04-28 2010-11-11 Bridgestone Corp Vibration control device
JP2014085004A (en) * 2012-10-26 2014-05-12 Tokai Rubber Ind Ltd Fluid sealed type vibration control device

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010090923A (en) * 2008-10-03 2010-04-22 Komatsu Ltd Liquid sealed mount
US9086114B2 (en) 2008-10-03 2015-07-21 Komatsu Ltd. Liquid sealed mount
JP2010249288A (en) * 2009-04-20 2010-11-04 Bridgestone Corp Vibration control device
JP2010255831A (en) * 2009-04-28 2010-11-11 Bridgestone Corp Vibration control device
JP2014085004A (en) * 2012-10-26 2014-05-12 Tokai Rubber Ind Ltd Fluid sealed type vibration control device
US9394964B2 (en) 2012-10-26 2016-07-19 Sumitomo Riko Company Limited Fluid-filled vibration damping device

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