JP5670233B2 - Liquid-filled vibration isolator - Google Patents

Liquid-filled vibration isolator Download PDF

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JP5670233B2
JP5670233B2 JP2011065001A JP2011065001A JP5670233B2 JP 5670233 B2 JP5670233 B2 JP 5670233B2 JP 2011065001 A JP2011065001 A JP 2011065001A JP 2011065001 A JP2011065001 A JP 2011065001A JP 5670233 B2 JP5670233 B2 JP 5670233B2
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liquid
vibration
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membrane
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JP2012202426A (en
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貴広 大口
貴広 大口
紀光 古澤
紀光 古澤
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Toyo Tire Corp
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Toyo Tire and Rubber Co Ltd
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本発明は、液封入式防振装置に関し、特に、比較的小振幅の振動入力時の低動ばね特性と比較的大振幅の振動入力時の高減衰特性および高動ばね特性とを確保しつつ、比較的高周波数の振動入力時における低動ばね特性を得ることができる液封入式防振装置に関するものである。   The present invention relates to a liquid filled type vibration isolator, and in particular, while ensuring a low dynamic spring characteristic when a relatively small amplitude vibration is input and a high damping characteristic and a high dynamic spring characteristic when a relatively large amplitude vibration is input. The present invention relates to a liquid filled type vibration isolator capable of obtaining a low dynamic spring characteristic at the time of vibration input at a relatively high frequency.

自動車のエンジンを支持固定しつつ、そのエンジン振動を車体フレームへ伝達させないようにする防振装置として、液封入式防振装置が知られている。   A liquid-filled vibration isolator is known as a vibration isolator that supports and fixes an automobile engine and prevents the engine vibration from being transmitted to a vehicle body frame.

例えば、特許文献１には、内筒金具（第１取付け部材）２２と外筒金具（第２取付け部材）１２との間を弾性体（防振基体）２８で連結し、ダイヤフラム３６と弾性体２８との間に形成される液室３８を、隔壁部材（仕切り部材）４４によって受圧液室（第１液室）４０及び副液室（第２液室）４２に仕切ると共に、それら両液室４０，４２をオリフィス５０により連通させた液封入式防振装置が開示される。   For example, in Patent Document 1, an inner cylinder fitting (first attachment member) 22 and an outer cylinder fitting (second attachment member) 12 are connected by an elastic body (vibration isolation base) 28, and a diaphragm 36 and an elastic body are connected. The liquid chamber 38 formed between the liquid chamber 28 and the liquid chamber 38 is partitioned into a pressure receiving liquid chamber (first liquid chamber) 40 and a sub liquid chamber (second liquid chamber) 42 by a partition member (partition member) 44, and both the liquid chambers are separated. A liquid-filled vibration isolator in which 40 and 42 are communicated by an orifice 50 is disclosed.

この液封入式防振装置によれば、オリフィス５０による両液室４０，４２間の流体流動効果や弾性体（防振基体）２８の制振効果により、振動減衰機能と振動絶縁機能とを果すことができる。   According to this liquid-filled vibration isolator, the vibration damping function and the vibration insulating function are achieved by the fluid flow effect between the liquid chambers 40 and 42 by the orifice 50 and the vibration damping effect of the elastic body (vibration-proof base) 28. be able to.

また、特許文献１は、内筒部材２２の内部に空気室２３を設け、その空気室２３と液室３８との間にメンブラン５２を配設する。これにより、アイドル状態のように、比較的小振幅の振動入力時には、メンブラン５２の弾性変形により、液室３８の液圧上昇を抑制して、低動ばね特性を得ることができる。   In Patent Document 1, an air chamber 23 is provided inside the inner cylinder member 22, and a membrane 52 is disposed between the air chamber 23 and the liquid chamber 38. As a result, when a vibration having a relatively small amplitude is input as in an idle state, an increase in the fluid pressure in the fluid chamber 38 is suppressed by elastic deformation of the membrane 52, and a low dynamic spring characteristic can be obtained.

一方で、特許文献１では、メンブラン５２の弾性変形により、液室３８の液圧上昇が抑制される分、オリフィス５０による両液室４０，４２間の流体流動効果が低下するため、走行時のように、比較的大振幅の振動入力時における高減衰特性・高動ばね特性の発揮が困難となる。   On the other hand, in Patent Document 1, the fluid flow effect between the two liquid chambers 40 and 42 by the orifice 50 is reduced by the amount by which the fluid pressure of the liquid chamber 38 is suppressed due to the elastic deformation of the membrane 52. Thus, it is difficult to exhibit high damping characteristics and high dynamic spring characteristics when a relatively large amplitude vibration is input.

これに対し、特許文献２には、外筒金具（第２取付け部材）２５内の空間２１を仕切部材３０によって主液室（第１液室）５０と副液室（第２液室）５１とに区画し、それら両液室５０，５１をオリフィス４０で連通させるだけでなく、内筒金具（第１取付け部材）２の貫通孔６にアイドルオリフィス１２を形成した液封入式防振装置が開示される。   On the other hand, in Patent Document 2, a main liquid chamber (first liquid chamber) 50 and a sub liquid chamber (second liquid chamber) 51 are separated by a partition member 30 in a space 21 in an outer cylinder fitting (second mounting member) 25. A liquid-filled vibration isolator having not only these two fluid chambers 50 and 51 communicated with each other through the orifice 40 but also an idle orifice 12 formed in the through-hole 6 of the inner cylinder fitting (first mounting member) 2 is provided. Disclosed.

この場合、アイドルオリフィス１２の終端にはダイヤフラム１５が配設され第２副液室１６が形成されると共に、第２副液室１６内には樹脂製の可動メンブラン１９が可動状態で配設される。   In this case, a diaphragm 15 is disposed at the end of the idle orifice 12 to form a second sub liquid chamber 16, and a resin movable membrane 19 is disposed in the second sub liquid chamber 16 in a movable state. The

この特許文献２によれば、アイドル状態のように、比較的小振幅の振動入力時には、可動メンブラン１９と第２副液室１６の内壁との間の隙間を介して液体の流動が許容されることで、アイドルオリフィス１２の終端に位置するダイヤフラム１５の弾性変形により、液圧上昇を抑制する効果と、アイドルオリフィス１２を介して主液室５０と第２副液室１６との間で行われる流体流動効果とを発揮させることができる。   According to Patent Document 2, when a vibration with a relatively small amplitude is input as in an idle state, the flow of liquid is allowed through the gap between the movable membrane 19 and the inner wall of the second sub liquid chamber 16. Thus, the elastic deformation of the diaphragm 15 located at the end of the idle orifice 12 suppresses the increase in the hydraulic pressure, and is performed between the main liquid chamber 50 and the second sub liquid chamber 16 via the idle orifice 12. The fluid flow effect can be exhibited.

一方、走行時のように、比較的大振幅の振動入力時には、可動メンブラン１９が第２副液室１６の内壁に当接され隙間が塞がれる（即ち、液体の流動が規制される）ことで、アイドルオリフィス１２の終端に位置するダイヤフラム１５が弾性変形することを抑制して、弾性変形による液圧の逃げを抑制できる。これにより、オリフィス４０を介して主液室５０と副液室５１との間で行われる流体流動効果により、高減衰特性・高動ばね特性の発揮が可能となる。   On the other hand, when a relatively large amplitude vibration is input, such as during traveling, the movable membrane 19 is brought into contact with the inner wall of the second sub liquid chamber 16 to close the gap (that is, the flow of the liquid is restricted). Thus, the diaphragm 15 positioned at the end of the idle orifice 12 can be prevented from elastically deforming, and the hydraulic pressure escape due to elastic deformation can be suppressed. As a result, a high damping characteristic and a high dynamic spring characteristic can be exhibited by the fluid flow effect performed between the main liquid chamber 50 and the sub liquid chamber 51 via the orifice 40.

特開２００４−２１１８３３号公報（図１、段落［００２０〜００２３］など）Japanese Unexamined Patent Application Publication No. 2004-21833 (FIG. 1, paragraphs [0020 to 0023], etc.) 特開２００８−５１２１４号公報（図２、段落［００１３〜００１６］など）JP 2008-51214 A (FIG. 2, paragraphs [0013 to 0016], etc.)

しかしながら、上述した特許文献２では、液圧上昇の抑制効果を担うダイヤフラム１５がアイドルオリフィス１２の終端に配設されるため、オリフィス４０及びアイドルオリフィス１２の両オリフィスが目詰まりする比較的高周波数の振動入力時には、ダイヤフラム１５の弾性変形による液圧上昇の抑制効果を得ることができず（即ち、液圧を逃がすことができず）、動ばね特性が高くなるという問題点があった。   However, in Patent Document 2 described above, since the diaphragm 15 responsible for suppressing the increase in hydraulic pressure is disposed at the end of the idle orifice 12, the orifice 40 and the idle orifice 12 are clogged at a relatively high frequency. At the time of vibration input, there is a problem that the effect of suppressing the increase in hydraulic pressure due to elastic deformation of the diaphragm 15 cannot be obtained (that is, the hydraulic pressure cannot be released), and the dynamic spring characteristics are improved.

本発明は上述した問題点を解決するためになされたものであり、比較的小振幅の振動入力時の低動ばね特性と比較的大振幅の振動入力時の高減衰特性および高動ばね特性とを確保しつつ、比較的高周波数の振動入力時における低動ばね特性を得ることができる液封入式防振装置を提供することを目的としている。   The present invention has been made to solve the above-described problems, and includes a low dynamic spring characteristic when a relatively small amplitude vibration is input, and a high damping characteristic and a high dynamic spring characteristic when a relatively large amplitude vibration is input. It is an object of the present invention to provide a liquid filled type vibration isolator capable of obtaining a low dynamic spring characteristic at the time of vibration input at a relatively high frequency while ensuring the above.

課題を解決するための手段および発明の効果Means for Solving the Problems and Effects of the Invention

請求項１記載の液封入式防振装置によれば、ゴム状弾性体からなると共に、第１取付け部材の第１液室に面する底面に凹設された凹部の開口を閉封することで、凹部を空気が充填された空気室とするメンブレン部材を備えるので、例えば、アイドル状態のように、比較的小振幅の振動入力時には、メンブレン部材の弾性変形により、液封入室（第１液室）の液圧上昇を抑制して、低動ばね特性を確保することができるという効果がある。   According to the liquid-filled vibration isolator according to claim 1, the rubber-filled vibration isolator is made of a rubber-like elastic body, and the opening of the concave portion provided in the bottom surface facing the first liquid chamber of the first mounting member is closed. Since the concave portion is provided with a membrane member having an air chamber filled with air, for example, when a relatively small amplitude vibration is input as in an idle state, the liquid sealing chamber (first liquid chamber) is caused by elastic deformation of the membrane member. ) Is suppressed, and a low dynamic spring characteristic can be secured.

また、請求項１によれば、メンブレン部材の剛性に入力振幅に対する非線形性を付与する振幅依存付与手段を備えるので、例えば、走行時のように、比較的大振幅の振動入力時には、メンブレン部材の剛性を振幅依存付与手段により高めて、メンブレン部材を弾性変形し難くすることができる。これにより、液封入室（第１液室）の液圧が逃げることを抑制できるので、オリフィスを介して第１液室と第２液室との間で行われる流体流動効果を発揮させ、高減衰特性・高動ばね特性を確保することができるという効果がある。   In addition, according to the first aspect of the invention, since the amplitude dependence imparting means for imparting the nonlinearity to the input amplitude to the rigidity of the membrane member is provided, for example, when the vibration of a relatively large amplitude is input as in traveling, the membrane member The rigidity can be increased by the amplitude dependence applying means, and the membrane member can be made difficult to elastically deform. As a result, it is possible to suppress the escape of the liquid pressure in the liquid enclosure chamber (first liquid chamber), so that the fluid flow effect performed between the first liquid chamber and the second liquid chamber via the orifice is exhibited, and There is an effect that damping characteristics and high dynamic spring characteristics can be secured.

更に、請求項１によれば、第１取付け部材の第１液室に面する底面に凹設された凹部の開口をメンブレン部材により閉封することで空気室を形成するので、メンブレン部材を第１液室の内壁の一部とすることができる。よって、従来品のように、第１液室とメンブレン部材との間にオリフィスが形成されないので、仕切り部材のオリフィスが目詰まりする比較的高周波数の振動入力時であっても、メンブレン部材の弾性変形により、液封入室（第１液室）の液圧上昇を抑制して、低動ばね特性を得ることができるという効果がある。   According to the first aspect of the present invention, the air chamber is formed by sealing the opening of the concave portion provided in the bottom surface facing the first liquid chamber of the first mounting member with the membrane member. It can be a part of the inner wall of one liquid chamber. Therefore, unlike the conventional product, since the orifice is not formed between the first liquid chamber and the membrane member, the elasticity of the membrane member can be obtained even at the time of relatively high frequency vibration input in which the orifice of the partition member is clogged. Due to the deformation, an increase in the fluid pressure in the fluid sealing chamber (first fluid chamber) can be suppressed, and the low dynamic spring characteristics can be obtained.

以上のように、請求項１によれば、比較的小振幅の振動入力時の低動ばね特性と比較的大振幅の振動入力時の高減衰特性・高動ばね特性とを確保しつつも、比較的高周波数の振動入力時における低動ばね特性を得ることができるという効果がある。   As described above, according to claim 1, while ensuring the low dynamic spring characteristics at the time of relatively small amplitude vibration input and the high damping characteristics and high dynamic spring characteristics at the time of relatively large amplitude vibration input, There is an effect that a low dynamic spring characteristic at the time of vibration input of a relatively high frequency can be obtained.

なお、請求項１記載の「少なくとも第１液室および第２液室を連通させるオリフィスを形成する仕切り部材」とは、少なくとも１本のオリフィスが形成されることを意味する。よって、仕切り部材が２本以上のオリフィスを形成する形態を除外するものではない。また、オリフィスを連通状態と遮断状態とに切り替える切替式として、仕切り部材が構成されても良い。この場合、連通状態と遮断状態とに切り替えられるオリフィスの本数は、限定されない。即ち、切り替えの対象となるオリフィスは、仕切り部材により形成されるオリフィスの内の全て（例えば、仕切り部材により形成されるオリフィスが１本の場合は１本、２本の場合は２本など）のオリフィスであっても良く、一部（例えば、仕切り部材により形成されるオリフィスが２本の内の１本など）のオリフィスのみであっても良い。   In addition, the “partition member that forms an orifice for communicating at least the first liquid chamber and the second liquid chamber” according to claim 1 means that at least one orifice is formed. Therefore, the form in which the partition member forms two or more orifices is not excluded. Moreover, a partition member may be comprised as a switching type which switches an orifice between a communication state and a interruption | blocking state. In this case, the number of orifices that can be switched between the communication state and the cutoff state is not limited. That is, the orifices to be switched are all of the orifices formed by the partition member (for example, one if the orifice formed by the partition member is one, two if the orifice is two, etc.) It may be an orifice, or only a part of the orifices (for example, one of the two orifices formed by the partition member).

また、請求項１によれば、変位規制部材は、少なくとも１の貫通孔が貫通形成されると共にメンブレン部材と所定間隔を隔てて対向配置される規制板部を備え、第１取付け部材の凹部は、メンブレン部材と所定間隔を隔てて対向すると共に空気室の内壁を形成する内壁部とを備えるので、振動入力に伴いメンブレン部材が変位した場合には、変位規制部材の規制板部または凹部の内壁部によりメンブレン部材を受け止めて、その変位を規制することができる。よって、振幅依存付与手段によるメンブレン部材への振幅依存性の付与を確実に行うことができる。 Further, according to claim 1, displacement of the regulating member is provided with a regulating plate part that is disposed to face the membrane member by a predetermined distance together with at least one through-hole is formed through a recess of the first mounting member Is provided with an inner wall portion that is opposed to the membrane member at a predetermined interval and forms an inner wall of the air chamber. Therefore, when the membrane member is displaced due to vibration input, the restriction plate portion or the recess portion of the displacement restriction member is provided. The membrane member can be received by the inner wall and the displacement can be regulated. Therefore, it is possible to reliably impart amplitude dependency to the membrane member by the amplitude dependency imparting means.

この場合、請求項１によれば、メンブレン部材の変位は、一方側への変位が変位規制部材により規制され、他方側への変位が第１取付け部材の凹部における内壁部により規制されるので、メンブレン部材の両側に変位規制部材を設ける必要がない。即ち、第１取付け部材の凹部の内壁部が、空気室を形成するための役割と、メンブレン部材の変位を規制する役割とを兼用する。これにより、メンブレン部材の変位を規制するための部材の部品点数を削減して、その分、製品コストの低減を図ることができるという効果がある。 In this case, according to the first aspect , the displacement of the membrane member is regulated by the displacement regulating member while the displacement to the other side is regulated by the inner wall portion in the recess of the first mounting member. There is no need to provide displacement regulating members on both sides of the membrane member. That is, the inner wall portion of the concave portion of the first mounting member serves both as a role for forming the air chamber and a role for regulating the displacement of the membrane member. Thereby, the number of parts of the member for regulating the displacement of the membrane member can be reduced, and the product cost can be reduced correspondingly.

請求項２記載の液封入式防振装置によれば、請求項１に記載の液封入式防振装置の奏する効果に加え、第１取付け部材の内部に貫通形成され、空気室を外部に連通させる連通孔を備えるので、空気室の空気ばね（体積弾性率）を安定に保つことができるという効果がある。即ち、第１取付け部材はエンジン側に取り付けられるため、エンジン温度が上昇すると、その上昇に伴って空気室も暖められ、空気室内の空気が膨張する。そのため、メンブレン部材の弾性変形に寄与する空気室の空気ばねの値に変動が生じ、動的特性の不安定化を招く。これに対し、請求項２によれば、空気室内の空気が膨張した場合には、その膨張分を連通孔により外部へ逃がすことができるので、空気室の圧力変動を抑制して、空気ばねの値を安定に保つことができるという効果がある。その結果、動的特性の安定化を得ることができる。 According to the hydraulic antivibration device according to claim 2, in addition to the effects of the hydraulic antivibration device according to claim 1, formed through the interior of the first mounting member, communicating the air chamber to the outside Since the communication hole is provided, there is an effect that the air spring (volume elastic modulus) of the air chamber can be kept stable. That is, since the first attachment member is attached to the engine side, when the engine temperature rises, the air chamber is also warmed with the rise, and the air in the air chamber expands. Therefore, the value of the air spring of the air chamber that contributes to the elastic deformation of the membrane member is fluctuated, leading to instability of dynamic characteristics. On the other hand, according to the second aspect , when the air in the air chamber expands, the expansion can be released to the outside through the communication hole. There is an effect that the value can be kept stable. As a result, stabilization of dynamic characteristics can be obtained.

請求項３記載の液封入式防振装置によれば、請求項２記載の液封入式防振装置の奏する効果に加え、第１取付け部材は、エンジン側に取り付けられる上端面と反対側となる下端面（底面）に凹部が凹設される柱状体に形成され、連通孔は、凹部の内壁部から上端面に向かって延設される縦孔と、その縦孔に一端が接続されると共に上端面側の外周面に他端が開口される横孔とを備えるので、エンジン側に取り付けられる座面としての上端面の面積を確保しつつ、連通孔を形成することができるという効果がある。また、このように連通孔を縦孔および横孔からなる貫通孔として形成することで、空気室内への異物の侵入を抑制することができるという効果がある。 According to the hydraulic antivibration device according to claim 3, in addition to the effects of the hydraulic antivibration device according to claim 2 wherein the first mounting member comprises a side opposite to the upper surface to be attached to the engine side The lower end surface (bottom surface) is formed in a columnar body having a recess, and the communication hole has a vertical hole extending from the inner wall portion of the recess toward the upper end surface, and one end connected to the vertical hole. Since the outer peripheral surface on the upper end surface side is provided with a lateral hole opened at the other end, there is an effect that the communication hole can be formed while ensuring the area of the upper end surface as a seating surface attached to the engine side. . In addition, by forming the communication hole as a through hole composed of a vertical hole and a horizontal hole in this way, there is an effect that it is possible to suppress the entry of foreign matter into the air chamber.

本発明の第１実施の形態における液封入式防振装置の断面図である。It is sectional drawing of the liquid filled type vibration isolator in 1st Embodiment of this invention. （ａ）は、第１取付け金具の上面図であり、（ｂ）は、第１取付け金具の底面図である。(A) is a top view of the first mounting bracket, and (b) is a bottom view of the first mounting bracket. 図２（ａ）のＩＩＩ−ＩＩＩ線における第１取付け金具の断面図である。It is sectional drawing of the 1st attachment bracket in the III-III line of Fig.2 (a). （ａ）は、メンブレン部材の上面図であり、（ｂ）は、図４（ａ）のＩＶｂ−ＩＶｂ線におけるメンブレン部材の断面図である。(A) is a top view of a membrane member, (b) is sectional drawing of the membrane member in the IVb-IVb line | wire of Fig.4 (a). （ａ）は、変位規制部材の上面図であり、（ｂ）は、図５（ａ）のＶｂ−Ｖｂ線における変位規制部材の断面図である。(A) is a top view of a displacement control member, (b) is sectional drawing of the displacement control member in the Vb-Vb line | wire of Fig.5 (a). 図１の一部を拡大して示した液封入式防振装置の部分拡大断面図である。FIG. 2 is a partially enlarged cross-sectional view of the liquid-filled vibration isolator showing a part of FIG. 第２実施の形態における液封入式防振装置の断面図である。It is sectional drawing of the liquid filled type vibration isolator in 2nd Embodiment. （ａ）は、第３実施の形態におけるメンブレン部材の上面図であり、（ｂ）は、図８（ａ）のＶＩＩＩｂ−ＶＩＩＩｂ線におけるメンブレン部材の断面図である。(A) is a top view of the membrane member in 3rd Embodiment, (b) is sectional drawing of the membrane member in the VIIIb-VIIIb line | wire of Fig.8 (a). （ａ）は、第４実施の形態におけるメンブレン部材の上面図であり、（ｂ）は、図９（ａ）のＩＸｂ−ＩＸｂ線におけるメンブレン部材の断面図である。(A) is a top view of the membrane member in 4th Embodiment, (b) is sectional drawing of the membrane member in the IXb-IXb line | wire of Fig.9 (a). （ａ）は、第５実施の形態におけるメンブレン部材の上面図であり、（ｂ）は、図１０（ａ）のＸｂ−Ｘｂ線におけるメンブレン部材の断面図である。(A) is a top view of the membrane member in 5th Embodiment, (b) is sectional drawing of the membrane member in the Xb-Xb line | wire of Fig.10 (a). （ａ）は、第６実施の形態における液封入式防振装置の断面図であり、（ｂ）は、第７実施の形態における液封入式防振装置の断面図であり、（ｃ）は、第８実施の形態における液封入式防振装置の断面図である。(A) is sectional drawing of the liquid filled type vibration isolator in 6th Embodiment, (b) is sectional drawing of the liquid filled type vibration isolator in 7th Embodiment, (c) is FIG. 10 is a cross-sectional view of a liquid filled type vibration damping device according to an eighth embodiment.

以下、本発明の好ましい実施例について、添付図面を参照して説明する。図１は、本発明の第１実施の形態における液封入式防振装置１００の断面図である。   Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. FIG. 1 is a cross-sectional view of a liquid-filled vibration isolator 100 according to the first embodiment of the present invention.

この液封入式防振装置１００は、自動車のエンジンを支持固定しつつ、そのエンジン振動を車体フレームへ伝達させないようにするための防振装置であり、図１に示すように、エンジン側に取り付けられる第１取付け金具１と、車体側に取り付けられると共に筒状に形成される第２取付け金具２と、これら両金具１，２を連結すると共にゴム状弾性体から構成される防振基体３とを主に備える。   The liquid-filled vibration isolator 100 is a vibration isolator for supporting and fixing an automobile engine so that the engine vibration is not transmitted to the vehicle body frame, and is attached to the engine side as shown in FIG. A first mounting bracket 1, a second mounting bracket 2 which is attached to the vehicle body and is formed in a cylindrical shape, and a vibration isolating base 3 which connects both the brackets 1 and 2 and is made of a rubber-like elastic body. Is mainly provided.

第１取付け金具１は、アルミニウム合金などから略円柱状に形成される。ここで、図２及び図３を参照して、第１取付け金具１の詳細構成について説明する。図２（ａ）は、第１取付け金具１の上面図であり、図２（ｂ）は、第１取付け金具１の底面図である。また、図３は、図２（ａ）のＩＩＩ−ＩＩＩ線における第１取付け金具１の断面図である。   The first mounting bracket 1 is formed in a substantially cylindrical shape from aluminum alloy or the like. Here, with reference to FIG.2 and FIG.3, the detailed structure of the 1st attachment bracket 1 is demonstrated. FIG. 2A is a top view of the first mounting bracket 1 and FIG. 2B is a bottom view of the first mounting bracket 1. FIG. 3 is a cross-sectional view of the first mounting bracket 1 taken along the line III-III in FIG.

図２及び図３に示すように、第１取付け金具１は、締結孔１１と、突起部１２と、張出部１３と、凹部１４と、連通孔１５とを主に備える。締結孔１１は、第１取付け金具１の上端面１ａに凹設されると共に内周面にめねじが螺刻されたねじ穴であり、エンジン側の取付けボルトが締結される。また、突起部１２は、第１取付け金具１の上端面１ａから突設される突起であり、エンジン側の部材に凹設された凹部に挿入されることで、第１取付け金具１の位置決めを行う。   As shown in FIGS. 2 and 3, the first mounting bracket 1 mainly includes a fastening hole 11, a protruding portion 12, an overhang portion 13, a concave portion 14, and a communication hole 15. The fastening hole 11 is a screw hole recessed in the upper end surface 1a of the first mounting bracket 1 and having a female screw threaded on the inner peripheral surface thereof, and is fastened with a mounting bolt on the engine side. The protrusion 12 is a protrusion that protrudes from the upper end surface 1a of the first mounting bracket 1 and is inserted into a recess that is recessed in the engine-side member, thereby positioning the first mounting bracket 1. Do.

張出部１３は、第１取付け金具１の外周面から外径方向へ向けてフランジ状に張り出す部位であり、第１取付け金具１の高さ方向（図３上下方向）略中央に位置する。大変位入力時には、張出部１３が後述するストッパ金具５に当接することで、ストッパ機能が発揮される。   The overhanging portion 13 is a portion that projects in a flange shape from the outer peripheral surface of the first mounting bracket 1 toward the outer diameter direction, and is located at the approximate center in the height direction (vertical direction in FIG. 3) of the first mounting bracket 1. . When a large displacement is input, the overhang portion 13 comes into contact with a stopper fitting 5 described later, thereby exhibiting a stopper function.

凹部１４は、第１取付け金具１の底面１ｂに凹設され後述する窪みであり、被圧入壁部１４ａと、その被圧入壁部１４ａに連設される内壁部１４ｂと、その内壁部１４ｂから突設される突条部１４ｃとを備える。被圧入壁部１４ａは、後述する変位規制部材３０の筒部３１ａが内嵌圧入される断面円形の壁面であり、第１取付け金具１の高さ方向（図３上下方向）に沿って略一定の内径を有して形成される。   The recess 14 is a recess that is provided in the bottom surface 1b of the first mounting bracket 1 and will be described later. From the press-fit wall portion 14a, the inner wall portion 14b that is connected to the press-fit wall portion 14a, and the inner wall portion 14b. And a protruding protrusion 14c. The press-fit wall portion 14a is a wall surface having a circular cross section into which a cylindrical portion 31a of a displacement restricting member 30 to be described later is fitted, and is substantially constant along the height direction of the first mounting bracket 1 (vertical direction in FIG. 3). Are formed.

内壁部１４ｂは、凹部１４の天井面（図３上側面）を形成する壁面であり、突条部１４ｃの内周側に位置する部分が、被圧入壁部１４ａと同心で且つ上方（図３上側）へ向けて凸となる球面状に形成されると共に、突条部１４ｃの外周側に位置する部分が、第１取付け金具１の高さ方向（図３上下方向）に垂直な平坦面として形成される。   The inner wall portion 14b is a wall surface forming the ceiling surface (upper side surface in FIG. 3) of the concave portion 14, and the portion located on the inner peripheral side of the ridge portion 14c is concentric with the press-fit wall portion 14a and above (FIG. 3). And a portion located on the outer peripheral side of the protrusion 14c as a flat surface perpendicular to the height direction (the vertical direction in FIG. 3) of the first mounting bracket 1 It is formed.

突条部１４ｃは、周方向に連続し図２（ｂ）に示すように被圧入壁部１４ａと同心の底面視円環状に形成される突条であり、突設先端側が円弧状に湾曲した断面Ｕ字状の断面形状に形成される。また、突条部１４ｃの突設先端（図３下側）を結んで形成される面は、突条部１４ｃの外周側に位置する内壁部１４ｂと平行とされる。   The protrusion 14c is a protrusion that is continuous in the circumferential direction and is formed in an annular shape as viewed from the bottom, concentric with the press-fit wall 14a, as shown in FIG. 2B, and the protruding tip side is curved in an arc shape. It is formed in a U-shaped cross-sectional shape. Further, the surface formed by connecting the protruding tip (lower side in FIG. 3) of the protrusion 14c is parallel to the inner wall 14b located on the outer peripheral side of the protrusion 14c.

このように構成された凹部１４には、後述するメンブレン部材２０と変位規制部材３０とが順に装着され、突条部１４ｃの内周側に位置する内壁部１４ｂとメンブレン部材２０との間に空気室４０が形成される（図１参照）。   A membrane member 20 and a displacement regulating member 30 to be described later are sequentially attached to the concave portion 14 configured as described above, and air is interposed between the inner wall portion 14b located on the inner peripheral side of the ridge portion 14c and the membrane member 20. A chamber 40 is formed (see FIG. 1).

なお、この空気室４０の形成状態では、内壁部１４ｂとメンブレン部材２０とが所定の間隔を隔てて対向配置される。この間隔は、走行状態において比較的大振幅の振動が入力された場合に、メンブレン部材２０の変位を内壁部１４ｂが受け止め可能な間隔に設定される。   In addition, in the formation state of this air chamber 40, the inner wall part 14b and the membrane member 20 are opposingly arranged at predetermined intervals. This interval is set to an interval at which the inner wall portion 14b can receive the displacement of the membrane member 20 when a relatively large amplitude vibration is input in the running state.

連通孔１５は、空気室４０を外部に連通させるための貫通孔であり、縦孔１５ａと、横孔１５ｂとを備える。縦孔１５ａは、内壁部１４ｂの中心部から上端面１ａへ向かって延設される断面円形の孔であり、その縦孔１５ａの終端は、第１取付け金具１の高さ方向（図３上下方向）において、張出部１３と上端面１ａとの間に位置する。   The communication hole 15 is a through hole for communicating the air chamber 40 to the outside, and includes a vertical hole 15a and a horizontal hole 15b. The vertical hole 15a is a hole having a circular cross section extending from the center of the inner wall portion 14b toward the upper end surface 1a. The end of the vertical hole 15a is in the height direction of the first mounting bracket 1 (upper and lower in FIG. 3). Direction) between the overhang 13 and the upper end surface 1a.

横孔１５ｂは、第１取付け金具１の高さ方向と平行に延設される断面円形の孔であり、一端側（図３左側）が縦孔１５ａの終端に接続されると共に、他端側が張出部１３と上端面１ａとの間において第１取付け金具１の外周面に開口される。   The horizontal hole 15b is a hole having a circular cross section that extends parallel to the height direction of the first mounting bracket 1, and one end side (left side in FIG. 3) is connected to the end of the vertical hole 15a, and the other end side is An opening is formed in the outer peripheral surface of the first mounting bracket 1 between the overhang portion 13 and the upper end surface 1a.

なお、縦孔１５ａの内径は、突条部１４ｃの内周面の内径よりも小径に形成され、本実施の形態では、突条部１４ｃの内径の略０．２倍に設定される。横孔１５ｂの内径は、縦孔１５ａの内径よりも小径に形成され、本実施の形態では、縦孔１５ａの略０．５倍に設定される。   In addition, the internal diameter of the vertical hole 15a is formed smaller than the internal diameter of the inner peripheral surface of the protrusion part 14c, and is set to about 0.2 times the internal diameter of the protrusion part 14c in this Embodiment. The inner diameter of the horizontal hole 15b is formed to be smaller than the inner diameter of the vertical hole 15a, and is set to approximately 0.5 times that of the vertical hole 15a in the present embodiment.

このように、連通孔１５は、横孔１５ｂを備え、その横孔１５ｂの他端側を第１取付け金具１の外周面に開口させるので、縦孔１５ａの終端を上端面１ａに開口させる場合と比較して、エンジン側に取り付けられる座面としての上端面１ａの面積を確保することができる。   In this way, the communication hole 15 includes the horizontal hole 15b, and the other end side of the horizontal hole 15b is opened on the outer peripheral surface of the first mounting bracket 1, so that the end of the vertical hole 15a is opened on the upper end surface 1a. Compared to the above, it is possible to secure the area of the upper end surface 1a as a seating surface attached to the engine side.

この場合、連通孔１５は十分に細く形成される（即ち、縦孔１５ａの内径が突条部１４ｃの内径よりも小径に形成されると共に、その縦孔１５ａよりも横孔１５ｂがさらに小径に形成される）ので、連通孔１５の形成に伴う第１取付け金具１の剛性の低下を抑制できる。   In this case, the communication hole 15 is formed sufficiently thin (that is, the inner diameter of the vertical hole 15a is smaller than the inner diameter of the protrusion 14c, and the horizontal hole 15b is further smaller than the vertical hole 15a. Therefore, it is possible to suppress a decrease in the rigidity of the first mounting bracket 1 due to the formation of the communication hole 15.

また、縦孔１５ａを横孔１５ｂよりも大径とすることで、縦孔１５ａ及び横孔１５ｂの形成がドリル加工や鋳造のいずれで行われる場合であっても、その加工公差を緩やかとして、横孔１５ｂの一端を縦孔１５ａへ容易かつ確実に接続させることができる。   In addition, by making the vertical hole 15a larger in diameter than the horizontal hole 15b, even if the formation of the vertical hole 15a and the horizontal hole 15b is performed by either drilling or casting, the processing tolerance is moderated. One end of the horizontal hole 15b can be easily and reliably connected to the vertical hole 15a.

さらに、縦孔１５ａ及び横孔１５ｂの内の一方を他方と異なる径とする場合に、小径とされる孔を、第１取付け金具１の外周面に他端が開口する横孔１５ｂとすることで、上述のように両孔１５ａ，１５ｂの接続の確実化を図りつつ、空気室４０（図６参照）内への異物の侵入を抑制することができる。   Furthermore, when one of the vertical hole 15a and the horizontal hole 15b has a different diameter from the other, the small hole is a horizontal hole 15b whose other end opens on the outer peripheral surface of the first mounting bracket 1. Thus, as described above, the entry of foreign matter into the air chamber 40 (see FIG. 6) can be suppressed while ensuring the connection between the holes 15a and 15b.

図１に戻って説明する。第２取付け金具２は、防振基体３が加硫成形される筒状金具２ａと、その筒状金具２ａの下方に取着される底金具２ｂとを備えて構成される。筒状金具２ａは上広がりの開口を有する筒状に、底金具２ｂは底部が傾斜したカップ状に、それぞれ鉄鋼材料から構成されている。なお、底金具２ｂの底部には、取付けボルト２１と突起部２２とが突設される。   Returning to FIG. The second mounting bracket 2 includes a cylindrical metal fitting 2a on which the vibration-proof base 3 is vulcanized and a bottom metal fitting 2b attached to the lower side of the cylindrical metal fitting 2a. The cylindrical metal fitting 2a is made of a steel material, and the bottom metal fitting 2b is made of a steel material in a cup shape with an inclined bottom. Note that a mounting bolt 21 and a protrusion 22 project from the bottom of the bottom metal fitting 2b.

防振基体３は、ゴム状弾性体から断面略円錐台形状に形成され、第１取付け金具１の外周面（底面１ｂと張出部１３との間の外周面）と筒状金具２ａの上端開口部の内周面との間に加硫接着されている。また、防振基体３の下端部には、筒状金具２ａの内周面を覆うゴム膜３ａが連なっており、このゴム膜３ａには、後述する仕切り部材４の外周部が密着されている。   The anti-vibration base 3 is formed from a rubber-like elastic body so as to have a substantially frustoconical cross section. Vulcanized and bonded to the inner peripheral surface of the opening. Further, a rubber film 3a covering the inner peripheral surface of the cylindrical metal fitting 2a is connected to the lower end portion of the vibration isolating base 3, and an outer peripheral portion of a partition member 4 described later is in close contact with the rubber film 3a. .

また、防振基体３の上端部には、第１取付け金具１の張出部１３の底面、外周面および上面を覆う覆設部３ｂが連なっており、大変位入力時に第１取付け金具１の張出部１３がストッパ金具５に当接される際には、覆設部３ｂの弾性変形により緩衝作用が得られる。なお、ストッパ金具５は、筒状金具２ａの上端部にかしめ固定される。また、ストッパ金具５の上面側には、ゴム状弾性体から逆カップ状に形成されるカバー部材６が装着される。カバー部材６は、第１取付け金具１が挿通される挿通孔を中央部に備える。   The upper end portion of the vibration isolating base 3 is connected to a covering portion 3b that covers the bottom surface, the outer peripheral surface, and the top surface of the overhanging portion 13 of the first mounting bracket 1. When the overhanging portion 13 is brought into contact with the stopper fitting 5, a buffering action is obtained by elastic deformation of the covering portion 3b. The stopper fitting 5 is fixed by caulking to the upper end portion of the cylindrical fitting 2a. Further, a cover member 6 formed in a reverse cup shape from a rubber-like elastic body is mounted on the upper surface side of the stopper fitting 5. The cover member 6 includes an insertion hole through which the first mounting bracket 1 is inserted at the center.

ダイヤフラム７は、ゴム状弾性体から部分球状を有するゴム膜状に形成され、第２取付け金具２（筒状金具２ａと底金具２ｂとの間）に取着される。その結果、このダイヤフラム７の上面側と防振基体３の下面側との間に、液封入室１０が形成される。なお、ダイヤフラム７は、その周縁部が、金属材料から上面視円環状に形成される取付け板７ａに加硫接着され、取付け板７ａが筒状金具２ａと底金具２ｂとの間でかしめ固定されることにより、第２取付け金具２に取着される。   The diaphragm 7 is formed in a rubber film shape having a partial spherical shape from a rubber-like elastic body, and is attached to the second attachment fitting 2 (between the tubular fitting 2a and the bottom fitting 2b). As a result, a liquid sealing chamber 10 is formed between the upper surface side of the diaphragm 7 and the lower surface side of the vibration isolation base 3. The peripheral edge of the diaphragm 7 is vulcanized and bonded to a mounting plate 7a formed from a metal material in an annular shape when viewed from above, and the mounting plate 7a is caulked and fixed between the cylindrical fitting 2a and the bottom fitting 2b. As a result, the second mounting bracket 2 is attached.

液封入室１０には、エチレングリコールなどの不凍性の液体（図示せず）が封入される。液封入室１０は、仕切り部材４によって、防振基体３側（図１上側）の第１液室１０Ａと、ダイヤフラム７側（図１下側）の第２液室１０Ｂとの２室に仕切られる。また、仕切り部材４は、ゴム状弾性体から部分球状を有するゴム膜状に形成される副ダイヤフラムを備え、仕切り部材４の内部には、副ダイヤフラムによって第１液室１０Ａと区画される第３液室１０Ｃが形成される。   An antifreezing liquid (not shown) such as ethylene glycol is sealed in the liquid sealing chamber 10. The liquid sealing chamber 10 is partitioned by the partition member 4 into two chambers, a first liquid chamber 10A on the vibration isolator base 3 side (upper side in FIG. 1) and a second liquid chamber 10B on the diaphragm 7 side (lower side in FIG. 1). It is done. Further, the partition member 4 includes a sub-diaphragm formed in a rubber film shape having a partial spherical shape from a rubber-like elastic body, and the partition member 4 has a third diaphragm partitioned from the first liquid chamber 10A by the sub-diaphragm. A liquid chamber 10C is formed.

仕切り部材４は、第１液室１０Ａ及び第２液室１０Ｂを連通させる第１オリフィスと、第２液室１０Ｂ及び第３液室１０Ｃを連通させる第２オリフィスとの２本のオリフィスを備える。これにより、液封入式防振装置１００は、例えば、シェイク振動とアイドル振動のように、異なる２つの周波数域の振動に対して、液体流動効果（液柱共振効果）による防振効果を発揮することができる。なお、かかる仕切り部材４の詳細構成については、公知の技術（例えば、特開２００７−１７７８７５号など）と同様であるので、その説明は省略する。   The partition member 4 includes two orifices, a first orifice for communicating the first liquid chamber 10A and the second liquid chamber 10B, and a second orifice for communicating the second liquid chamber 10B and the third liquid chamber 10C. As a result, the liquid filled type vibration damping device 100 exhibits a vibration damping effect due to the liquid flow effect (liquid column resonance effect) against vibrations in two different frequency ranges, such as shake vibration and idle vibration. be able to. Note that the detailed configuration of the partition member 4 is the same as that of a known technique (for example, Japanese Patent Application Laid-Open No. 2007-177875), and thus the description thereof is omitted.

第１取付け金具１の底面１ｂに凹設された凹部１４には、メンブレン部材２０及び変位規制部材３０が装着される。ここで、図４及び図５を参照して、メンブレン部材２０及び変位規制部材３０について説明する。   A membrane member 20 and a displacement restricting member 30 are mounted in the recess 14 provided in the bottom surface 1 b of the first mounting bracket 1. Here, the membrane member 20 and the displacement regulating member 30 will be described with reference to FIGS. 4 and 5.

図４（ａ）は、メンブレン部材２０の上面図であり、図４（ｂ）は、図４（ａ）のＩＶｂ−ＩＶｂ線におけるメンブレン部材２０の断面図である。メンブレン部材２０は、ゴム状弾性体から軸心Ｏを有する上面視円形のゴム膜状に形成される。   4A is a top view of the membrane member 20, and FIG. 4B is a cross-sectional view of the membrane member 20 taken along line IVb-IVb in FIG. 4A. The membrane member 20 is formed from a rubber-like elastic body in a circular rubber film shape having an axis O in a top view.

なお、詳細には、メンブレン部材２０は、中央部に位置し円板状に形成される部位と、その円板状の部位の周縁部が内周面に接続される筒状の部位とを備え、円板状の部位が、凹部１４の突条部１４ｃと変位規制部材３０の突条部３１ｃとの間に挟持されることで（図６参照）、筒状の部位が両突条部１４ｃ，３１ｃに抜き取り不能に係止され、メンブレン部材２０の脱落が防止される。   Specifically, the membrane member 20 includes a portion that is located at the center and is formed in a disc shape, and a cylindrical portion that is connected to the inner peripheral surface of the peripheral portion of the disc-like portion. The disc-shaped portion is sandwiched between the ridge portion 14c of the concave portion 14 and the ridge portion 31c of the displacement regulating member 30 (see FIG. 6), so that the cylindrical portion is the two ridge portions 14c. , 31c, and the membrane member 20 is prevented from falling off.

図５（ａ）は、変位規制部材３０の上面図であり、図５（ｂ）は、図５（ａ）のＶｂ−Ｖｂ線における変位規制部材３０の断面図である。変位規制部材３０は、圧入部３１と、規制板部３２とを備え、これら両部位３１，３２がアルミニウム合金から一体に形成される。   5A is a top view of the displacement regulating member 30, and FIG. 5B is a cross-sectional view of the displacement regulating member 30 taken along the line Vb-Vb in FIG. 5A. The displacement restricting member 30 includes a press-fit portion 31 and a restricting plate portion 32, and both the portions 31, 32 are integrally formed from an aluminum alloy.

圧入部３１は、筒状に形成される筒部３１ａと、その筒部３１ａの軸方向一端側（図５（ｂ）下側）に接続され上面視円環状に形成される円環部３１ｂと、その円環部３１ｂの上面側（図５（ｂ）上側面）から突設される突条部３１ｃとを備え、軸心Ｏ周りに対称に形成される。   The press-fit portion 31 includes a cylindrical portion 31a that is formed in a cylindrical shape, and an annular portion 31b that is connected to one axial end side (the lower side in FIG. 5B) of the cylindrical portion 31a and is formed in an annular shape when viewed from above. , And a ridge portion 31c that protrudes from the upper surface side (upper side surface of FIG. 5B) of the annular portion 31b, and is formed symmetrically around the axis O.

筒部３１ａは、第１取付け金具１の凹部１４における被圧入壁部１４ａ（図２及び図３参照）に内嵌圧入される部位であり、被圧入壁部１４ａの内径よりも若干大きな外径に形成される。なお、変位規制部材３０は、筒部３１ａの軸方向一端面（図５（ｂ）上側面）が凹部１４の内壁部１４ｂに当接される位置まで軸心Ｏ方向へ内嵌圧入される。   The cylindrical portion 31a is a portion that is press-fitted into the press-fit wall portion 14a (see FIGS. 2 and 3) in the concave portion 14 of the first mounting bracket 1, and has an outer diameter slightly larger than the inner diameter of the press-fit wall portion 14a. Formed. The displacement regulating member 30 is press-fitted in the direction of the axis O to a position where one axial end surface (upper side surface in FIG. 5B) of the cylindrical portion 31 a comes into contact with the inner wall portion 14 b of the recess 14.

突条部３１ｃは、周方向に連続する突条であり、突設先端側が円弧状に湾曲した断面Ｕ字状の断面形状に形成される。また、突条部３１ｃの突設先端（図５（ｂ）上側）を結んで形成される面は、筒部３１ａの軸方向他端側（図５（ｂ）上側）の端面と平行とされる。なお、突条部３１ｃの上面視形状は、第１取付け金具１の凹部１４における突条部１４ｃ（図２及び図３参照）と同径の円環状に形成される。   The protrusion 31c is a protrusion that is continuous in the circumferential direction, and is formed in a U-shaped cross-sectional shape in which the protruding tip side is curved in an arc shape. Further, the surface formed by connecting the protruding tip (upper side in FIG. 5B) of the protrusion 31c is parallel to the end surface on the other axial end side (upper side in FIG. 5B) of the cylindrical portion 31a. The In addition, the top view shape of the protrusion part 31c is formed in the annular | circular shape of the same diameter as the protrusion part 14c (refer FIG.2 and FIG.3) in the recessed part 14 of the 1st attachment bracket 1. As shown in FIG.

よって、変位規制部材３０の圧入部３１（筒部３１ａ）が第１取付け金具１の凹部１４（被圧入壁部１４ａ）に装着（内嵌圧入）されると、第１取付け金具１の凹部１４及び変位規制部材３０の両突条部１４ｃ，３１ｃがメンブレン部材２０を所定の圧縮代で両側から挟持して、メンブレン部材２０の周縁部が全周にわたってシール状態とされる。   Therefore, when the press-fit portion 31 (cylinder portion 31a) of the displacement regulating member 30 is mounted (internally press-fitted) into the recess 14 (the press-fit wall portion 14a) of the first mounting bracket 1, the recess 14 of the first mounting bracket 1 is mounted. And both the protrusions 14c and 31c of the displacement regulating member 30 sandwich the membrane member 20 from both sides with a predetermined compression allowance, and the peripheral portion of the membrane member 20 is in a sealed state over the entire circumference.

規制板部３２は、圧入部３１（円環部３１ｂ）の内周側に配設される部位であり、本実施の形態では、図５（ａ）に示す上面視において、軸心Ｏから放射直線状に延設される４本の脚部から形成される。よって、これら４本の脚部の間の４箇所に貫通孔が貫通形成され、その貫通孔を介して、液圧がメンブレン部材２０に作用される（図１参照）。   The restricting plate portion 32 is a portion disposed on the inner peripheral side of the press-fit portion 31 (annular portion 31b). In the present embodiment, the restriction plate portion 32 radiates from the axis O in a top view shown in FIG. It is formed from four legs extending in a straight line. Therefore, through holes are formed through four positions between these four leg portions, and hydraulic pressure acts on the membrane member 20 through the through holes (see FIG. 1).

なお、筒部３１ａの高さ寸法（軸心Ｏ方向寸法、図５（ｂ）上下方向寸法）は、凹部１４の被圧入壁部１４ａに内嵌圧入され、軸方向一端面（図５（ｂ）上側面）が凹部１４の内壁部１４ｂに当接されると、軸方向他端面（図５（ｂ）下側面）が第１取付け金具１の底面１ｂに面一となる寸法に設定される（図１及び図６参照）。   In addition, the height dimension (axial center O direction dimension, FIG.5 (b) vertical dimension) of the cylinder part 31a is press-fitted in the press-fit wall part 14a of the recessed part 14, and an axial direction one end surface (FIG.5 (b)). ) When the upper side surface is in contact with the inner wall portion 14b of the recess 14, the other axial end surface (the lower side surface in FIG. 5B) is set to a dimension that is flush with the bottom surface 1b of the first mounting bracket 1. (See FIGS. 1 and 6).

また、筒部３１ａの軸方向一端側が凹部１４の内壁部１４ｂに当接されると、規制板部３２とメンブレン部材２０とは所定の間隔を隔てて対向配置される。この間隔は、走行状態において比較的大振幅の振動が入力された場合に、メンブレン部材２０の変位を規制板部３２が受け止め可能な間隔に設定される。   Further, when one end side in the axial direction of the cylindrical portion 31a is brought into contact with the inner wall portion 14b of the concave portion 14, the regulating plate portion 32 and the membrane member 20 are disposed to face each other with a predetermined interval. This interval is set to an interval at which the restriction plate portion 32 can receive the displacement of the membrane member 20 when a relatively large amplitude vibration is input in the running state.

ここで、規制板部３２は、貫通形成される各貫通孔の面積が十分に確保されると共に、その板厚寸法（図５（ｂ）上下方向寸法）が十分に小さくされるので、少なくとも比較的高周波数の振動入力時に、各貫通孔がオリフィスとして機能することはない。即ち、比較的高周波数の振動入力時に、各貫通孔が目詰まりすることはなく、その結果、メンブレン部材２０の弾性変形により、第１液室１０Ａの液圧上昇を抑制して、低動ばね特性を得ることができる。   Here, the restricting plate portion 32 has a sufficiently large area for each through-hole formed to be penetrated, and the plate thickness dimension (the vertical dimension in FIG. 5B) is sufficiently small. Each through-hole does not function as an orifice at the time of vibration input at a high frequency. That is, each through-hole is not clogged when a relatively high-frequency vibration is input, and as a result, an increase in the fluid pressure in the first fluid chamber 10A is suppressed by the elastic deformation of the membrane member 20, and a low dynamic spring is achieved. Characteristics can be obtained.

図１へ戻って説明する。第１取付け金具１の凹部１４に、メンブレン部材２０及び変位規制部材３０が順に装着されると、凹部１４とメンブレン部材２０とにより空気室４０が形成される。この空気室４０は、連通孔１５を介して、外部に連通される。   Returning to FIG. When the membrane member 20 and the displacement regulating member 30 are sequentially attached to the recess 14 of the first mounting bracket 1, an air chamber 40 is formed by the recess 14 and the membrane member 20. The air chamber 40 communicates with the outside through the communication hole 15.

次いで、液封入式防振装置１００の組立方法について、図１及び図６を参照して説明する。図６は、図１の一部を拡大して示した液封入式防振装置１００の部分拡大断面図である。   Next, an assembly method of the liquid filled type vibration damping device 100 will be described with reference to FIGS. 1 and 6. FIG. 6 is a partially enlarged cross-sectional view of the liquid-filled vibration isolator 100, which shows a part of FIG.

図１及び図６に示すように、液封入式防振装置１００の組み立ては、まず、第１取付け金具１と筒状金具２ａとを防振基体３により連結した加硫成形品を加硫金型により加硫成形し、その加硫成形品における第１取付け金具１の凹部１４に対し、メンブレン部材２０を設置した後、凹部１４の被圧入壁部１４ａに変位規制部材３０の圧入部３１（筒部３１ａ）を内嵌圧入する。   As shown in FIGS. 1 and 6, the assembly of the liquid-filled vibration isolator 100 is performed by first vulcanizing a vulcanized molded product in which the first mounting bracket 1 and the cylindrical bracket 2a are connected by a vibration isolating base 3. After the vulcanization molding is performed using a mold and the membrane member 20 is installed in the concave portion 14 of the first mounting bracket 1 in the vulcanized molded product, the press-fit portion 31 ( The cylinder portion 31a) is press-fitted.

これにより、凹部１４の内壁部１４ｂと、変位規制部材３０の規制板部３２とが、メンブレン部材２０を挟んで対向配置されると共に、内壁部１４ｂ及び規制板部３２とメンブレン部材２０の上下面との間には、それぞれ所定間隔が隔てられる。また、メンブレン部材２０の周縁部は、凹部１４の突条部１４ｃと変位規制部材３０の突条部３１ｃとにより挟持され、シール状態とされる。その結果、内壁部１４ｂとメンブレン部材２０との対向面間に空気室４０が形成される。   As a result, the inner wall portion 14b of the recess 14 and the restriction plate portion 32 of the displacement restriction member 30 are disposed to face each other with the membrane member 20 interposed therebetween, and the upper and lower surfaces of the inner wall portion 14b and the restriction plate portion 32 and the membrane member 20 are disposed. Are spaced apart from each other by a predetermined interval. Further, the peripheral edge portion of the membrane member 20 is sandwiched between the ridge portion 14c of the concave portion 14 and the ridge portion 31c of the displacement regulating member 30 to be in a sealed state. As a result, an air chamber 40 is formed between the opposing surfaces of the inner wall portion 14b and the membrane member 20.

空気室４０を形成した後は、筒状金具２ａの内周側へ仕切り部材４及びダイヤフラム７を順に挿入した後、底金具２ｂを装着し、筒状金具２ａの下端部をかしめ固定すると共に、筒状金具２ａの上端部にストッパ金具５をかしめ固定し、カバー部材６を装着することで、液封入式防振装置１００の製造が完了する。   After the air chamber 40 is formed, the partition member 4 and the diaphragm 7 are sequentially inserted into the inner peripheral side of the cylindrical fitting 2a, and then the bottom fitting 2b is attached, and the lower end portion of the cylindrical fitting 2a is caulked and fixed, The stopper metal fitting 5 is caulked and fixed to the upper end of the cylindrical metal fitting 2a, and the cover member 6 is attached, whereby the manufacture of the liquid-filled vibration isolator 100 is completed.

以上のように構成された液封入式防振装置１００によれば、振動入力時には、変位規制部材３０の規制板部３２に形成された複数の貫通孔を通じて液封入室１０（第１液室１０Ａ）の圧力変動がメンブレン部材２０に作用され、その結果、メンブレン部材２０が変位（弾性変形）される。   According to the liquid-filled vibration isolator 100 configured as described above, when a vibration is input, the liquid-filled chamber 10 (first liquid chamber 10A) is passed through the plurality of through holes formed in the restriction plate portion 32 of the displacement restriction member 30. ) Is applied to the membrane member 20, and as a result, the membrane member 20 is displaced (elastically deformed).

この場合、例えば、アイドル状態のように、比較的小振幅の振動入力時には、メンブレン部材２０が、変位規制部材３０の規制板部３２または凹部１４の内壁部１４ｂに規制されることなく、変位（弾性変形）することにより、液封入室１０（第１液室１０Ａ）の液圧上昇を抑制して、低動ばね特性を確保することができる。   In this case, for example, when a relatively small amplitude vibration is input as in an idle state, the membrane member 20 is not restricted by the restricting plate portion 32 of the displacement restricting member 30 or the inner wall portion 14b of the recess 14 (see FIG. By elastically deforming, an increase in the hydraulic pressure in the liquid sealing chamber 10 (first liquid chamber 10A) can be suppressed, and low dynamic spring characteristics can be ensured.

一方、例えば、走行時のように、比較的大振幅の振動入力時には、メンブレン部材２０が、変位規制部材３０の規制板部３２または凹部１４の内壁部１４ｂに当接され、その変位（弾性変形）が規制されることで、剛性が高められる。これにより、液封入室１０（第１液室１０Ａ）の液圧が逃げることを抑制できるので、流体流動効果を発揮させ、高減衰特性・高動ばね特性を確保することができる。   On the other hand, for example, when a relatively large amplitude vibration is input, such as during traveling, the membrane member 20 is brought into contact with the restriction plate portion 32 of the displacement restriction member 30 or the inner wall portion 14b of the concave portion 14, and the displacement (elastic deformation). ) Is regulated, the rigidity is increased. Thereby, since it can suppress that the hydraulic pressure of the liquid enclosure chamber 10 (1st liquid chamber 10A) escapes, a fluid flow effect can be exhibited and a high damping characteristic and a high dynamic spring characteristic can be ensured.

更に、液封入式防振装置１００によれば、第１取付け部材１の第１液室１０Ａに面する底面１ｂに凹設された凹部１４の開口をメンブレン部材２０により閉封することで空気室４０を形成するので、メンブレン部材２０を、第１液室１０Ａを形成する内壁の一部とすることができる。即ち、従来品のように、第１液室１０Ａとメンブレン部材２０との間にオリフィスは形成されないので、仕切り部材４のオリフィスが目詰まりする比較的高周波数の振動入力時であっても、メンブレン部材２０の弾性変形により、液封入室１０（第１液室１０Ａ）の液圧上昇を抑制して、低動ばね特性を得ることができる。   Further, according to the liquid-filled vibration isolator 100, the air chamber is formed by closing the opening of the concave portion 14 formed in the bottom surface 1b facing the first liquid chamber 10A of the first mounting member 1 with the membrane member 20. 40 is formed, the membrane member 20 can be a part of the inner wall forming the first liquid chamber 10A. That is, since the orifice is not formed between the first liquid chamber 10A and the membrane member 20 unlike the conventional product, the membrane can be used even at the time of relatively high frequency vibration input where the orifice of the partition member 4 is clogged. Due to the elastic deformation of the member 20, an increase in the fluid pressure in the fluid sealing chamber 10 (first fluid chamber 10A) can be suppressed, and a low dynamic spring characteristic can be obtained.

なお、液封入式防振装置１００は、空気室４０を外部（大気）に連通させる連通孔４０を備えるので、空気室４０の空気ばね（体積弾性率）を安定に保つことができる。即ち、第１取付け部材１はエンジン側に取り付けられるため、エンジン温度が上昇すると、その上昇に伴って空気室４０も暖められ、空気室４０内の空気が膨張する。そのため、メンブレン部材２０の弾性変形に寄与する空気室４０の空気ばねの値に変動が生じ、動的特性の不安定化を招く。これに対し、連通孔１５を備えることで、空気室４０内の空気が膨張した場合には、その膨張分を連通孔１５により外部へ逃がすことができるので、空気室４０の圧力変動を抑制して、空気ばねの値を安定に保つことができる。その結果、動的特性の安定化を得ることができる。   In addition, since the liquid filled type vibration isolator 100 includes the communication hole 40 that allows the air chamber 40 to communicate with the outside (atmosphere), the air spring (volume elastic modulus) of the air chamber 40 can be kept stable. That is, since the 1st attachment member 1 is attached to the engine side, when engine temperature rises, the air chamber 40 will also be warmed with the rise, and the air in the air chamber 40 will expand. Therefore, the value of the air spring of the air chamber 40 that contributes to the elastic deformation of the membrane member 20 varies, leading to instability of dynamic characteristics. On the other hand, by providing the communication hole 15, when the air in the air chamber 40 expands, the expanded portion can be released to the outside through the communication hole 15, so that the pressure fluctuation of the air chamber 40 is suppressed. Thus, the value of the air spring can be kept stable. As a result, stabilization of dynamic characteristics can be obtained.

また、メンブレン部材２０の変位が変位規制部材３０の規制板部３２または凹部１４の内壁部１４ｂに規制される際に、それらの衝突に起因して衝撃が発生しても、かかる衝撃の発生点から車体までの振動伝達経路には、防振基体３が存在する。よって、衝撃により振動が発生しても、防振基体３により低減して、車体側で異音が発生することを抑制することができる。   In addition, when the displacement of the membrane member 20 is restricted by the restriction plate portion 32 of the displacement restriction member 30 or the inner wall portion 14b of the recess 14, even if an impact occurs due to the collision, the point of occurrence of such an impact In the vibration transmission path from the vehicle to the vehicle body, the vibration isolating base 3 exists. Therefore, even if vibration is generated due to an impact, it can be reduced by the anti-vibration base 3 to suppress the generation of abnormal noise on the vehicle body side.

ここで、液封入式防振装置１００では、メンブレン部材２０の変位は、一方側（図６下側）への変位が変位規制部材３０の規制板部３２により規制され、他方側（図６上側）への変位が凹部１４の内壁部１４ｂにより規制されるので、メンブレン部材２０の両側に変位規制部材３０（規制板部３２）を設ける必要がない。即ち、第１取付け部材１の凹部１４における内壁部１４ｂが、空気室４０を形成するための役割と、メンブレン部材２０の変位を規制する役割とを兼用する。これにより、メンブレン部材２０の変位を規制するための部材の部品点数を削減して、その分、製品コストの低減を図ることができる。   Here, in the liquid-filled vibration isolator 100, the displacement of the membrane member 20 is restricted to one side (lower side in FIG. 6) by the restriction plate portion 32 of the displacement restriction member 30, and the other side (upper side in FIG. 6). ) Is regulated by the inner wall portion 14b of the recess 14, it is not necessary to provide the displacement regulating members 30 (regulating plate portions 32) on both sides of the membrane member 20. That is, the inner wall portion 14 b in the concave portion 14 of the first attachment member 1 serves both as a role for forming the air chamber 40 and a role for regulating the displacement of the membrane member 20. Thereby, the number of parts of the member for regulating the displacement of the membrane member 20 can be reduced, and the product cost can be reduced accordingly.

次いで、図７を参照して、第２実施の形態における液封入式防振装置２００について説明する。第１実施の形態では、空気室４０を外部（大気）に連通させる場合を説明したが、第２実施の形態における空気室２４０は、密閉された空間として形成される。なお、第１実施の形態と同一の部分については同一の符号を付して、その説明を省略する。   Next, with reference to FIG. 7, a liquid-filled vibration isolator 200 according to the second embodiment will be described. Although the case where the air chamber 40 is communicated with the outside (atmosphere) has been described in the first embodiment, the air chamber 240 in the second embodiment is formed as a sealed space. In addition, the same code | symbol is attached | subjected about the part same as 1st Embodiment, and the description is abbreviate | omitted.

図７は、第２実施の形態における液封入式防振装置２００の断面図であり、図１に対応する。第２実施の形態における第１取付け金具２０１は、第１実施の形態における第１取付け金具１に対して、連通孔１５の形成が省略されている点を除き、他の構成は同一に形成される。   FIG. 7 is a cross-sectional view of a liquid-filled vibration isolator 200 according to the second embodiment, and corresponds to FIG. The first mounting bracket 201 according to the second embodiment is the same as the first mounting bracket 1 according to the first embodiment except that the communication holes 15 are not formed. The

よって、第１取付け金具２０１の凹部１４に、メンブレン部材２０及び変異規制部材３０が順に装着され、メンブレン部材２０の周縁部がシール状態とされると、凹部１４とメンブレン部材２０との間には、密閉された空間（即ち、外部（大気）と連通しない空間）として、空気室２４０が形成される。   Therefore, when the membrane member 20 and the variation regulating member 30 are sequentially attached to the concave portion 14 of the first mounting bracket 201 and the peripheral edge portion of the membrane member 20 is in a sealed state, there is a gap between the concave portion 14 and the membrane member 20. The air chamber 240 is formed as a sealed space (that is, a space that does not communicate with the outside (atmosphere)).

なお、第２実施の形態における液封入式防振装置２００のように、空気室２４０が外部と連通されない空間として形成される場合であっても、メンブレン部材２０の変位（弾性変形）とその変位の変位規制部材３０及び凹部１４による規制とにより、第１実施の形態の場合と同様に、比較的小振幅の振動入力時の低動ばね特性と比較的大振幅の振動入力時の高減衰特性・高動ばね特性とを確保しつつも、比較的高周波数の振動入力時における低動ばね特性を得ることができる。   Even when the air chamber 240 is formed as a space that does not communicate with the outside as in the liquid-filled vibration isolator 200 according to the second embodiment, the displacement (elastic deformation) of the membrane member 20 and the displacement thereof. Due to the restriction by the displacement restricting member 30 and the recess 14, the low dynamic spring characteristic at the time of relatively small amplitude vibration input and the high damping characteristic at the time of relatively large amplitude vibration input, as in the first embodiment. -While ensuring high dynamic spring characteristics, low dynamic spring characteristics at the time of vibration input at a relatively high frequency can be obtained.

次いで、図８を参照して、第３実施の形態におけるメンブレン部材３２０について説明する。第１実施の形態では、メンブレン部材２０の厚み寸法が一定に形成される場合を説明したが、第３実施の形態におけるメンブレン部材３２０は、一部の厚み寸法が大きくされている。なお、第１実施の形態と同一の部分については同一の符号を付して、その説明を省略する。   Next, the membrane member 320 in the third embodiment will be described with reference to FIG. In the first embodiment, the case where the thickness dimension of the membrane member 20 is formed constant has been described. However, a part of the thickness dimension of the membrane member 320 in the third embodiment is increased. In addition, the same code | symbol is attached | subjected about the part same as 1st Embodiment, and the description is abbreviate | omitted.

図８（ａ）は、第３実施の形態におけるメンブレン部材３２０の上面図であり、図８（ｂ）は、図８（ａ）のＶＩＩＩｂ−ＶＩＩＩｂ線におけるメンブレン部材３２０の断面図である。第３実施の形態におけるメンブレン部材３２０は、第１実施の形態におけるメンブレン部材２０に対して、中央部に部分球状の球状部３２０ａが上下両面に突設されている点を除き、他の構成は同一に形成される。このメンブレン部材３２０によっても、第１実施の形態における場合と同様の効果を得ることができる。   FIG. 8A is a top view of the membrane member 320 in the third embodiment, and FIG. 8B is a cross-sectional view of the membrane member 320 taken along line VIIIb-VIIIb in FIG. 8A. The membrane member 320 according to the third embodiment is different from the membrane member 20 according to the first embodiment except that a spherical portion 320a having a spherical shape protrudes from the upper and lower surfaces at the center. Formed identically. This membrane member 320 can also provide the same effects as in the first embodiment.

ここで、メンブレン部材３２０の球状部３２０は、変位規制部材３０の規制板部３２及び第１取付け金具１の凹部１４における内壁部１４ｂの間で挟持される高さ寸法に形成されていても良く、或いは、規制板部３２及び内壁部１４ｂの少なくとも一方との間に隙間を有していても良い。メンブレン部材３２０と規制板部３２及び内壁部１４ｂとの衝突を抑制またはその衝突を段階的として、異音の発生を低減することができる。   Here, the spherical portion 320 of the membrane member 320 may be formed in a height dimension that is sandwiched between the restriction plate portion 32 of the displacement restriction member 30 and the inner wall portion 14b of the concave portion 14 of the first mounting bracket 1. Or you may have a clearance gap between at least one of the control board part 32 and the inner wall part 14b. Generation | occurrence | production of abnormal noise can be reduced by suppressing the collision with the membrane member 320, the control board part 32, and the inner wall part 14b, or making the collision stepwise.

なお、規制板部３２及び内壁部１４ｂの間に球状部３２０ａを挟持させる場合には、連通孔１５の縦孔１５ａを、球状部３２０ａによって塞がれない位置に形成する。   When the spherical portion 320a is sandwiched between the restriction plate portion 32 and the inner wall portion 14b, the vertical hole 15a of the communication hole 15 is formed at a position that is not blocked by the spherical portion 320a.

一方、球状部３２０ａと内壁部１４ｂとの間に隙間を形成する場合には、球状部３２０ａが内壁部１４ｂへ向けて変位した際に、連通孔１５の縦孔１５ａが球状部３２０ａにより塞がれるように構成しても良い。即ち、メンブレン部材３２０の球状部３２０ａと連通孔１の縦孔１５ａとを同心に配置すると共に、縦孔１５ａの内径を、縦孔１５ａへ向けて球状に突出する球状部３２０ａの突出部分の外径よりも小さな値に設定する。   On the other hand, when a gap is formed between the spherical portion 320a and the inner wall portion 14b, the vertical hole 15a of the communication hole 15 is blocked by the spherical portion 320a when the spherical portion 320a is displaced toward the inner wall portion 14b. You may comprise. That is, the spherical portion 320a of the membrane member 320 and the vertical hole 15a of the communication hole 1 are arranged concentrically, and the inner diameter of the vertical hole 15a is outside the protruding portion of the spherical portion 320a that protrudes spherically toward the vertical hole 15a. Set to a value smaller than the diameter.

これにより、連通孔１５が球状部３２ａにより塞がれるまでの間は、空気室４０の空気ばね（体積弾性率）を低くして、メンブレン部材３２０の変形性を確保しつつ、連通口１５が球状部３２０ａにより塞がれた後は、メンブレン部材３２０の変位に伴う空気室４０内の空気の圧縮により、空気室４０の空気ばね（体積弾性率）を高くすることができる。即ち、メンブレン部材３２０の剛性の振幅依存性（入力振幅に対する非線形性）をより大きくする効果もある。   Thus, until the communication hole 15 is closed by the spherical portion 32a, the air spring (volume elastic modulus) of the air chamber 40 is lowered to ensure the deformability of the membrane member 320, and the communication port 15 After being blocked by the spherical portion 320a, the air spring (volume elastic modulus) of the air chamber 40 can be increased by the compression of the air in the air chamber 40 accompanying the displacement of the membrane member 320. That is, there is an effect of increasing the amplitude dependency (nonlinearity with respect to the input amplitude) of the rigidity of the membrane member 320.

次いで、図９を参照して、第４実施の形態におけるメンブレン部材４２０について説明する。第１実施の形態では、メンブレン部材２０の中央部が板状に形成される場合を説明したが、第４実施の形態におけるメンブレン部材４２０は、中央部が蛇腹条に屈曲して形成されている。なお、第１実施の形態と同一の部分については同一の符号を付して、その説明を省略する。   Next, a membrane member 420 according to the fourth embodiment will be described with reference to FIG. In the first embodiment, the case where the central portion of the membrane member 20 is formed in a plate shape has been described. However, the membrane member 420 in the fourth embodiment is formed by bending the central portion into a bellows strip. . In addition, the same code | symbol is attached | subjected about the part same as 1st Embodiment, and the description is abbreviate | omitted.

図９（ａ）は、第４実施の形態におけるメンブレン部材４２０の上面図であり、図９（ｂ）は、図９（ａ）のＩＸｂ−ＩＸｂ線におけるメンブレン部材４２０の断面図である。第４実施の形態におけるメンブレン部材４２０は、第１実施の形態におけるメンブレン部材２０に対して、中央部の形状（蛇腹形状）を除き、他の構成は同一に形成される。このメンブレン部材４２０によっても、第１実施の形態の場合と同様の効果を得ることができる。   FIG. 9A is a top view of the membrane member 420 according to the fourth embodiment, and FIG. 9B is a cross-sectional view of the membrane member 420 taken along the line IXb-IXb in FIG. 9A. The membrane member 420 according to the fourth embodiment is the same as the membrane member 20 according to the first embodiment except for the shape of the central portion (the bellows shape). This membrane member 420 can also provide the same effect as that of the first embodiment.

なお、第４実施の形態では、メンブレン部材４２０の中央部が蛇腹状に屈曲して形成され、剛性が低くされることで、比較的小振幅の振動入力に対しては、メンブレン部材４２０の変位（弾性変形）により液封入室１０（第１液室１０Ａ）の液圧を逃がして、低動ばね特性を確保することができる一方、蛇腹状に屈曲した部位が伸びて展張された状態では、剛性が高くされることで、比較的大振幅の振動入力に対しては、液圧の逃げを抑制して、オリフィスを介して行われる流体流動効果を高めることで、高減衰特性・高動ばね特性を確保することができる。また、比較的高周波数の振動入力に対しては、第１実施の形態の場合と同様に、低動ばね特性を得ることができる。   In the fourth embodiment, the center portion of the membrane member 420 is bent and formed in a bellows shape, and the rigidity is lowered, so that the displacement of the membrane member 420 with respect to vibration input with a relatively small amplitude ( The elastic pressure can release the liquid pressure in the liquid sealing chamber 10 (first liquid chamber 10A) to ensure low dynamic spring characteristics. On the other hand, in a state where the bellows-shaped bent portion is stretched and stretched, the rigidity is reduced. By increasing the flow rate, it is possible to suppress the escape of hydraulic pressure for vibration input with a relatively large amplitude and enhance the fluid flow effect performed through the orifice, thereby achieving high damping characteristics and high dynamic spring characteristics. Can be secured. Further, for a relatively high frequency vibration input, a low dynamic spring characteristic can be obtained as in the case of the first embodiment.

なお、このように、第４実施の形態では、メンブレン部材４２０自体に非線形特性を持たせることができるので、変位規制部材３０の規制板部３２を省略すると共に、凹部１４の内壁部１４ｂの凹設深さを大きくして、これら両部３２、１４ｂによってメンブレン部材４２０の変位を規制しない構成としても良い。   As described above, in the fourth embodiment, since the membrane member 420 itself can have nonlinear characteristics, the restriction plate portion 32 of the displacement restriction member 30 is omitted, and the inner wall portion 14b of the recessed portion 14 is recessed. It is good also as a structure which enlarges the installation depth and does not regulate the displacement of the membrane member 420 by these both parts 32 and 14b.

次いで、図１０を参照して、第５実施の形態におけるメンブレン部材５２０について説明する。第１実施の形態では、メンブレン部材２０がゴム状弾性体のみから形成される場合を説明したが、第５実施の形態におけるメンブレン部材５２０は、内部に非伸縮性の布状体５２０ａが埋設されている。なお、第１実施の形態と同一の部分については同一の符号を付して、その説明を省略する。   Next, the membrane member 520 in the fifth embodiment will be described with reference to FIG. In the first embodiment, the case where the membrane member 20 is formed only from a rubber-like elastic body has been described. However, the membrane member 520 in the fifth embodiment has a non-stretchable cloth-like body 520a embedded therein. ing. In addition, the same code | symbol is attached | subjected about the part same as 1st Embodiment, and the description is abbreviate | omitted.

図１０（ａ）は、第５実施の形態におけるメンブレン部材５２０の上面図であり、図１０（ｂ）は、図１０（ａ）のＸｂ−Ｘｂ線におけるメンブレン部材５２０の断面図である。第５実施の形態におけるメンブレン部材５２０は、第１実施の形態におけるメンブレン部材２０に対して、内部に布状体５２０ａが埋設される点を除き、他の構成は同一に形成される。このメンブレン部材４２０によっても、第１実施の形態の場合と同様の効果を得ることができる。   FIG. 10A is a top view of the membrane member 520 in the fifth embodiment, and FIG. 10B is a cross-sectional view of the membrane member 520 taken along the line Xb-Xb in FIG. The membrane member 520 in the fifth embodiment has the same configuration as the membrane member 20 in the first embodiment except that a cloth-like body 520a is embedded therein. This membrane member 420 can also provide the same effect as that of the first embodiment.

布状体５２０ａは、複数本の繊維（本実施の形態では、互いに直行する経糸及び緯糸）を平織りした繊維織布の両面にエラストマーをコーティングした引き布として構成される。なお、エラストマーとしては、メンブレン部材５２０を加硫する際に架橋反応を得られるものであれば特に限定されるものではなく、例えば、天然ゴムやＳＢＲ、ＢＲ、ＮＢＲ、ＣＲ、ＥＰＤＭなどの架橋タイプのエラストマーが例示される。また、繊維には、ポリアミド繊維を使用することが好ましい。   The cloth-like body 520a is configured as a draw cloth in which a plurality of fibers (in this embodiment, warp yarns and weft yarns orthogonal to each other) are plain woven and coated with an elastomer on both sides. The elastomer is not particularly limited as long as it can obtain a cross-linking reaction when the membrane member 520 is vulcanized. For example, natural rubber or a cross-linking type such as SBR, BR, NBR, CR, EPDM or the like. These elastomers are exemplified. Moreover, it is preferable to use a polyamide fiber for a fiber.

本実施の形態では、布状体５２０ａは、メンブレン部材５２０の厚み方向（図１０（ｂ）上下方向）中央に埋設されると共に、上面視円形に形成される。なお、布状体５２０ａの外径は、突条部１４ｃ，３１ｃ（図２及び図５参照）よりも大径に設定されている。即ち、第１取付け金具１の凹部１４に装着されると、布状体５２０ａの周縁部が突条部１４ｃ，３１ｃ間に挟持される。これにより、比較的大振幅の振動入力時には、布状体５２０ａを構成する繊維の張力を利用して、メンブレン部材５２０の剛性を高くすることができる。   In the present embodiment, the cloth-like body 520a is embedded in the center of the membrane member 520 in the thickness direction (the vertical direction in FIG. 10B) and is formed in a circular shape when viewed from above. In addition, the outer diameter of the cloth-like body 520a is set to be larger than the protrusions 14c and 31c (see FIGS. 2 and 5). That is, when the first mounting member 1 is attached to the recess 14, the peripheral portion of the cloth-like body 520 a is sandwiched between the protrusions 14 c and 31 c. Thereby, at the time of vibration input having a relatively large amplitude, the rigidity of the membrane member 520 can be increased by using the tension of the fibers constituting the cloth-like body 520a.

よって、第５実施の形態においても、比較的小振幅の振動入力に対しては、メンブレン部材５２０の変位（弾性変形）により液封入室１０（第１液室１０Ａ）の液圧を逃がして、低動ばね特性を確保することができる一方、比較的大振幅の振動入力に対しては、液圧の逃げを抑制して、オリフィスを介して行われる流体流動効果を高めることで、高減衰特性・高動ばね特性を確保することができる。また、比較的高周波数の振動入力に対しては、第１実施の形態の場合と同様に、低動ばね特性を得ることができる。   Therefore, also in the fifth embodiment, with respect to vibration input having a relatively small amplitude, the fluid pressure in the liquid sealing chamber 10 (first liquid chamber 10A) is released by the displacement (elastic deformation) of the membrane member 520, While a low dynamic spring characteristic can be ensured, a relatively large amplitude vibration input can be achieved by suppressing the escape of hydraulic pressure and enhancing the fluid flow effect performed through the orifice.・ High dynamic spring characteristics can be secured. Further, for a relatively high frequency vibration input, a low dynamic spring characteristic can be obtained as in the case of the first embodiment.

なお、このように、第５実施の形態においては、第４実施の形態の場合と同様に、メンブレン部材５２０自体に非線形特性を持たせることができるので、変位規制部材３０の規制板部３２を省略すると共に、凹部１４の内壁部１４ｂの凹設深さを大きくして、これら両部３２、１４ｂによってメンブレン部材４２０の変位を規制しない構成としても良い。   In this way, in the fifth embodiment, as in the case of the fourth embodiment, the membrane member 520 itself can be given non-linear characteristics, so that the restriction plate portion 32 of the displacement restriction member 30 is provided. While omitting, it is good also as a structure which enlarges the recessed depth of the inner wall part 14b of the recessed part 14, and does not regulate the displacement of the membrane member 420 by these both parts 32 and 14b.

次いで、図１１を参照して、第６実施の形態から第８実施の形態における液封入式防振装置６００〜８００について説明する。第６実施の形態から第８実施の形態における液封入式防振装置６００〜８００は、第１実施の形態における液封入式防振装置１００に対して、第１取付け金具６０１〜８０１に形成される横孔６１５ｂ〜８１５ｂの形成位置（及び縦孔６１５ａ〜８１５ａの長さ）が異なる点を除き、他の構成はそれぞれ同一に形成される。   Next, with reference to FIG. 11, liquid-filled vibration isolator 600 to 800 in the sixth to eighth embodiments will be described. The liquid-filled vibration isolator 600 to 800 in the sixth to eighth embodiments is formed on the first mounting brackets 601 to 801 with respect to the liquid-filled vibration isolator 100 in the first embodiment. Other configurations are the same except that the horizontal holes 615b to 815b are formed at different positions (and the lengths of the vertical holes 615a to 815a).

図１１（ａ）は、第６実施の形態における液封入式防振装置６００の断面図であり、図１に対応する。第１実施の形態では、横孔１５ｂの他端側がカバー部材６よりも上方となる位置で、第１取付け金具１の外周面に開口される場合を説明したが、第６実施の形態における横孔６１５ｂは、カバー部材６よりも下方となる位置で、第１取付け金具６０１の外周面に他端側を開口させる。なお、第１実施の形態と同一の部分については同一の符号を付して、その説明を省略する。   FIG. 11A is a cross-sectional view of a liquid filled type vibration damping device 600 according to the sixth embodiment, and corresponds to FIG. In the first embodiment, the case where the other end side of the horizontal hole 15b is opened to the outer peripheral surface of the first mounting bracket 1 at a position above the cover member 6 has been described. The hole 615 b opens the other end side on the outer peripheral surface of the first mounting bracket 601 at a position below the cover member 6. In addition, the same code | symbol is attached | subjected about the part same as 1st Embodiment, and the description is abbreviate | omitted.

この液封入式防振装置６００によれば、横孔６１５ｂの開口をカバー部材６により覆うことができるので、空気室４０内への異物の侵入を抑制することができる。   According to this liquid-filled vibration isolator 600, the opening of the horizontal hole 615b can be covered with the cover member 6, so that the entry of foreign matter into the air chamber 40 can be suppressed.

図１１（ｂ）は、第７実施の形態における液封入式防振装置７００の断面図であり、図１に対応する。第１実施の形態では、横孔１５ｂが第１取付け金具１の内部に形成される場合を説明したが、第７実施の形態における横孔７１５ｂは、第１取付け金具７０１の上端面１ａに凹設される。なお、第１実施の形態と同一の部分については同一の符号を付して、その説明を省略する。   FIG. 11B is a cross-sectional view of a liquid filled type vibration damping device 700 according to the seventh embodiment, and corresponds to FIG. In the first embodiment, the case where the lateral hole 15b is formed inside the first mounting bracket 1 has been described. However, the lateral hole 715b in the seventh embodiment is recessed in the upper end surface 1a of the first mounting bracket 701. Established. In addition, the same code | symbol is attached | subjected about the part same as 1st Embodiment, and the description is abbreviate | omitted.

この液封入式防振装置７００によれば、第１取付け金具４０１の上端面１ａに対し、縦孔７１５ａの終端から第１取付け金具７０１の外周面まで溝を凹設することで、横孔７１５ｂを形成するので、かかる横孔７１５ｂの形成に要するコストの削減を図ることができる。   According to this liquid-filled vibration isolator 700, a groove is formed in the upper end surface 1a of the first mounting bracket 401 from the end of the vertical hole 715a to the outer peripheral surface of the first mounting bracket 701, thereby forming the horizontal hole 715b. Therefore, the cost required for forming the lateral hole 715b can be reduced.

図１１（ｃ）は、第８実施の形態における液封入式防振装置８００の断面図であり、図１に対応する。第１実施の形態では、横孔１５ｂが水平に形成される場合を説明したが、第８実施の形態における横孔８１５ｂは、縦孔８１５ａの終端から他端側（開口側）へ向けて下降傾斜して形成される。なお、第１実施の形態と同一の部分については同一の符号を付して、その説明を省略する。   FIG. 11C is a cross-sectional view of the liquid filled type vibration damping device 800 according to the eighth embodiment, and corresponds to FIG. In the first embodiment, the case where the horizontal hole 15b is formed horizontally has been described. However, the horizontal hole 815b in the eighth embodiment descends from the end of the vertical hole 815a toward the other end side (opening side). Inclined. In addition, the same code | symbol is attached | subjected about the part same as 1st Embodiment, and the description is abbreviate | omitted.

この液封入式防振装置８００によれば、横孔８１５ｂが下降傾斜して形成されているので、空気室４０内への異物の侵入を抑制することができる。   According to this liquid-filled vibration isolator 800, the horizontal hole 815b is formed to be inclined downward, so that the entry of foreign matter into the air chamber 40 can be suppressed.

以上、実施の形態に基づき本発明を説明したが、本発明は上記実施の形態に何ら限定されるものではなく、本発明の趣旨を逸脱しない範囲内で種々の改良変形が可能であることは容易に推察できるものである。   The present invention has been described above based on the embodiments. However, the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily guessed.

上記各実施の形態で挙げた数値は一例であり、他の数値を採用することは当然可能である。また、各構成の大小関係は一例であり、他の関係を採用することは当然可能である。例えば、連通孔１５〜８１５の形成本数は一例であり、２本以上を設けても良い。また、縦孔１５ａ〜８１５ａの内径と横孔１５ｂ〜８１５ｂの内径との大小関係は一例であり、逆の関係としても良い。   The numerical values given in the above embodiments are merely examples, and other numerical values can naturally be adopted. Moreover, the magnitude relationship of each structure is an example, and it is naturally possible to employ other relationships. For example, the number of communication holes 15 to 815 formed is an example, and two or more may be provided. Further, the magnitude relationship between the inner diameters of the vertical holes 15a to 815a and the inner diameters of the horizontal holes 15b to 815b is merely an example, and may be reversed.

上記各実施の形態では、仕切り部材４が２本のオリフィスを備えて構成される場合（いわゆるダブルオリフィスタイプ）を説明したが、必ずしもこれに限られるものではなく、仕切り部材４を他の構成としても良い。他の構成としては、例えば、第１液室１０Ａと第２液室１０Ｂとを連通させるオリフィスを１本のみ備える構成（いわゆるシングルオリフィスタイプ）や、異なる特性の２本のオリフィスを備えると共にそれら２本のオリフィスを選択的に切り替える構成（いわゆる切り替え式タイプ、例えば、特開２００９−０８５４０５号）であっても良い。   In each of the above embodiments, the case where the partition member 4 is configured to include two orifices (so-called double orifice type) has been described. However, the present invention is not necessarily limited to this, and the partition member 4 is configured as another configuration. Also good. Other configurations include, for example, a configuration including only one orifice (so-called single-orifice type) for communicating the first liquid chamber 10A and the second liquid chamber 10B, or two orifices having different characteristics and two of them. A configuration in which the orifices of the book are selectively switched (a so-called switching type, for example, JP 2009-085405 A) may be used.

上記各実施の形態において説明した液圧上昇とは、液圧の絶対値が増加することを意味し、第１取付け金具１が仕切り部材４へ近接する方向（図１下方）へ相対変位して、第１液室１０ａが正圧となる場合と、第１取付け金具１が仕切り部材４から離間する方向（図１上方向）へ相対変位して、第１液室１０ａが負圧となる場合との両者を含む。   The increase in hydraulic pressure described in the above embodiments means that the absolute value of the hydraulic pressure increases, and the first mounting bracket 1 is relatively displaced in the direction approaching the partition member 4 (downward in FIG. 1). When the first liquid chamber 10a has a positive pressure and when the first mounting bracket 1 is relatively displaced in a direction away from the partition member 4 (upward in FIG. 1), the first liquid chamber 10a has a negative pressure. And both.

上記各実施の形態では、連通孔１５，６１５〜８１５の縦孔１５ａ，６１５ａ〜８１５ａが軸心Ｏに一致する位置に形成される場合を説明したが、必ずしもこれに限られるものではなく、軸心Ｏからずれた位置に形成することは当然可能である。なお、横孔１５ｂ，６１５ｂ〜８１５ｂについても同様であり、任意の位置に形成することができる。   In each of the above-described embodiments, the case where the vertical holes 15a and 615a to 815a of the communication holes 15 and 615 to 815 are formed at positions that coincide with the axis O has been described. It is naturally possible to form it at a position shifted from the center O. The same applies to the lateral holes 15b and 615b to 815b, and they can be formed at arbitrary positions.

また、上記各実施の形態で説明した連通孔１５，６１５〜８１５（縦孔１５ａ，６１５ａ〜８１５ａ及び横孔１５ｂ，６１５ｂ〜８１５ｂ）の形成角度は一例であり、それらの角度とは異なる他の角度に設定することは当然可能である。   In addition, the formation angles of the communication holes 15, 615 to 815 (vertical holes 15a, 615a to 815a and horizontal holes 15b and 615b to 815b) described in the above embodiments are merely examples, and other angles different from those angles may be used. It is naturally possible to set the angle.

なお、第１取付け金具１，６０１〜８０１の少なくとも一部（例えば、張出部１３と上端面１ａとの間）が横断面長円形状または横断面楕円形状に形成される場合には、第１取付け金具の上面視において、縦孔１５ａ等が長軸上に位置し、かつ、横孔１５ｂ等が長軸に沿う位置に形成されても良く、縦孔１５ａ等が短軸上に位置し、かつ、横孔１５ｂ等が短軸に沿う位置に形成されても良い。前者の場合には、第１取付け金具の剛性を確保でき、後者の場合には、第１取付け金具への連通口１５等の形成コストを低減できる。   In addition, when at least a part of the first mounting brackets 1, 601 to 801 (for example, between the overhanging portion 13 and the upper end surface 1 a) is formed in an elliptical cross section or an elliptical cross section, In the top view of one mounting bracket, the vertical holes 15a and the like may be located on the long axis, and the horizontal holes 15b and the like may be formed along the long axis, and the vertical holes 15a and the like are located on the short axis. And the horizontal hole 15b etc. may be formed in the position along a short axis. In the former case, the rigidity of the first mounting bracket can be secured, and in the latter case, the formation cost of the communication port 15 and the like to the first mounting bracket can be reduced.

ここで、上記各実施の形態において説明した比較的小振幅の振動としては、例えば、０．０５ｍｍ〜０．３ｍｍの振幅の振動が、比較的大振幅の振動としては、例えば、０．３ｍｍ〜１．５ｍｍの振幅の振動が、比較的高周波数の振動としては、例えば、１００Ｈｚ以上の振動が、それぞれ例示される。なお、比較的小振幅の振動は、例えば、アイドル状態における振動（問えば、２０Ｈｚ〜４０Ｈｚ）が想定され、比較的大振幅の振動は、例えば、走行中のシェイク振動（例えば、１０Ｈｚ〜２０Ｈｚ）が想定される。また、比較的高周波数の振動は、上記振幅よりも更に小振幅の振動となる。   Here, as the relatively small amplitude vibration described in each of the above embodiments, for example, a vibration having an amplitude of 0.05 mm to 0.3 mm is used, and as a relatively large amplitude vibration, for example, 0.3 mm to 0.3 mm is used. Examples of the vibration having an amplitude of 1.5 mm and the vibration having a relatively high frequency include vibrations of 100 Hz or more. The relatively small amplitude vibration is assumed to be, for example, vibration in an idle state (for example, 20 Hz to 40 Hz), and the relatively large amplitude vibration is, for example, shake vibration during driving (for example, 10 Hz to 20 Hz). Is assumed. In addition, the vibration having a relatively high frequency becomes a vibration having a smaller amplitude than the above amplitude.

また、請求項に記載の振幅依存付与手段としては、例えば、上記第１から第８実施の形態では、凹部１４及び変位規制部材３０が、第３から第５実施の形態では、メンブレン部材３２０，４２０，５２０（球状部３２０ａ、蛇腹状形状または布状体５２０ａ）が、それぞれ該当する。
＜その他＞
＜手段＞
技術的思想１の液封入式防振装置は、エンジン側に取り付けられる第１取付け部材と、車体側に取り付けられる第２取付け部材と、前記第２取付け部材および第１取付け部材を連結すると共にゴム状弾性体からなる防振基体と、前記第２取付け部材に取り付けられ前記防振基体との間に液封入室を形成すると共にゴム状弾性体からなるダイヤフラムと、前記液封入室を前記防振基体側の第１液室および前記ダイヤフラム側の第２液室に仕切ると共に少なくとも前記第１液室および第２液室を連通させるオリフィスを形成する仕切り部材と、を備えるものであり、ゴム状弾性体からなると共に、前記第１取付け部材の前記第１液室に面する底面に凹設された凹部の開口を閉封することで、前記凹部を空気が充填された空気室とするメンブレン部材と、前記メンブレン部材の剛性に入力振幅に対する非線形性を付与する振幅依存付与手段と、を備える。
技術的思想２の液封入式防振装置は、技術的思想１の液封入式防振装置において、変位規制部材を備え、前記変位規制部材は、前記第１取付け部材の凹部に内嵌圧入され前記メンブレン部材の周縁部をシールする円環状の圧入部と、前記圧入部の内周側に配設され少なくとも１の貫通孔が貫通形成されると共に前記メンブレン部材と所定間隔を隔てて対向配置される規制板部と、を備え、前記第１取付け部材の凹部は、前記変位規制部材の圧入部が内嵌圧入される被圧入壁部と、前記被圧入壁部に連設され前記メンブレン部材と所定間隔を隔てて対向すると共に前記空気室の内壁を形成する内壁部と、を備え、前記振幅依存付与手段は、前記メンブレン部材の変位を、前記変位規制部材の規制板部または前記凹部の内壁部に規制させることで、前記メンブレン部材に入力振幅に対する振幅依存性を付与する。
技術的思想３の液封入式防振装置は、技術的思想１又は２に記載の液封入式防振装置において、前記第１取付け部材の内部に貫通形成され、前記空気室を外部に連通させる連通孔を備える。
技術的思想４の液封入式防振装置は、技術的思想３に記載の液封入式防振装置において、
前記第１取付け部材は、上端面が前記エンジン側に取り付けられると共に、前記上端面と反対側となる下端面が前記第１液室に面し前記凹部が凹設される前記底面とされ、前記下端面側の外周面に前記防振基体が加硫接着される柱状体に形成され、前記連通孔は、前記凹部の内壁部から前記上端面へ向かって延設される縦孔と、前記縦孔に一端が接続されると共に前記上端面側の外周面に他端が開口される横孔と、を備える。
＜効果＞
技術的思想１記載の液封入式防振装置によれば、ゴム状弾性体からなると共に、第１取付け部材の第１液室に面する底面に凹設された凹部の開口を閉封することで、凹部を空気が充填された空気室とするメンブレン部材を備えるので、例えば、アイドル状態のように、比較的小振幅の振動入力時には、メンブレン部材の弾性変形により、液封入室（第１液室）の液圧上昇を抑制して、低動ばね特性を確保することができるという効果がある。
また、技術的思想１によれば、メンブレン部材の剛性に入力振幅に対する非線形性を付与する振幅依存付与手段を備えるので、例えば、走行時のように、比較的大振幅の振動入力時には、メンブレン部材の剛性を振幅依存付与手段により高めて、メンブレン部材を弾性変形し難くすることができる。これにより、液封入室（第１液室）の液圧が逃げることを抑制できるので、オリフィスを介して第１液室と第２液室との間で行われる流体流動効果を発揮させ、高減衰特性・高動ばね特性を確保することができるという効果がある。
更に、技術的思想１によれば、第１取付け部材の第１液室に面する底面に凹設された凹部の開口をメンブレン部材により閉封することで空気室を形成するので、メンブレン部材を第１液室の内壁の一部とすることができる。よって、従来品のように、第１液室とメンブレン部材との間にオリフィスが形成されないので、仕切り部材のオリフィスが目詰まりする比較的高周波数の振動入力時であっても、メンブレン部材の弾性変形により、液封入室（第１液室）の液圧上昇を抑制して、低動ばね特性を得ることができるという効果がある。
以上のように、技術的思想１によれば、比較的小振幅の振動入力時の低動ばね特性と比較的大振幅の振動入力時の高減衰特性・高動ばね特性とを確保しつつも、比較的高周波数の振動入力時における低動ばね特性を得ることができるという効果がある。
なお、技術的思想１記載の「少なくとも第１液室および第２液室を連通させるオリフィスを形成する仕切り部材」とは、少なくとも１本のオリフィスが形成されることを意味する。よって、仕切り部材が２本以上のオリフィスを形成する形態を除外するものではない。また、オリフィスを連通状態と遮断状態とに切り替える切替式として、仕切り部材が構成されても良い。この場合、連通状態と遮断状態とに切り替えられるオリフィスの本数は、限定されない。即ち、切り替えの対象となるオリフィスは、仕切り部材により形成されるオリフィスの内の全て（例えば、仕切り部材により形成されるオリフィスが１本の場合は１本、２本の場合は２本など）のオリフィスであっても良く、一部（例えば、仕切り部材により形成されるオリフィスが２本の内の１本など）のオリフィスのみであっても良い。
また、技術的思想１記載の振幅依存付与手段としては、例えば、メンブレン部材の内部にゴム状弾性体よりも剛性が高い部材（例えば、非伸縮性の布状の部材）を埋設し、その部材によりメンブレン部材の所定量以上の変位を規制する形態、或いは、メンブレン部材から所定間隔を隔てた位置に部材を配設し、その部材によりメンブレン部材の所定量以上の変位を規制する形態などが例示される。
この場合、技術的思想１によれば、メンブレン部材は、エンジン側に取り付けられる第１取付け部材に配設されるので、メンブレン部材から車体までの振動伝達経路の一部を防振基体により形成することができる。よって、メンブレン部材の剛性が振幅依存付与手段の機能により高められることに起因して、衝撃（例えば、上記布状の部材が展張される際の衝撃やメンブレンが上記変位を規制する部材に衝突する際の衝撃）が発生しても、かかる衝撃の振動伝達を防振基体により低減して、車体側で異音が発生することを抑制することができる。
技術的思想２記載の液封入式防振装置によれば、技術的思想１記載の液封入式防振装置の奏する効果に加え、変位規制部材は、少なくとも１の貫通孔が貫通形成されると共にメンブレン部材と所定間隔を隔てて対向配置される規制板部を備え、第１取付け部材の凹部は、メンブレン部材と所定間隔を隔てて対向すると共に空気室の内壁を形成する内壁部とを備えるので、振動入力に伴いメンブレン部材が変位した場合には、変位規制部材の規制板部または凹部の内壁部によりメンブレン部材を受け止めて、その変位を規制することができる。よって、振幅依存付与手段によるメンブレン部材への振幅依存性の付与を確実に行うことができる。
この場合、技術的思想２によれば、メンブレン部材の変位は、一方側への変位が変位規制部材により規制され、他方側への変位が第１取付け部材の凹部における内壁部により規制されるので、メンブレン部材の両側に変位規制部材を設ける必要がない。即ち、第１取付け部材の凹部の内壁部が、空気室を形成するための役割と、メンブレン部材の変位を規制する役割とを兼用する。これにより、メンブレン部材の変位を規制するための部材の部品点数を削減して、その分、製品コストの低減を図ることができるという効果がある。
技術的思想３記載の液封入式防振装置によれば、技術的思想１又は２に記載の液封入式防振装置の奏する効果に加え、第１取付け部材の内部に貫通形成され、空気室を外部に連通させる連通孔を備えるので、空気室の空気ばね（体積弾性率）を安定に保つことができるという効果がある。即ち、第１取付け部材はエンジン側に取り付けられるため、エンジン温度が上昇すると、その上昇に伴って空気室も暖められ、空気室内の空気が膨張する。そのため、メンブレン部材の弾性変形に寄与する空気室の空気ばねの値に変動が生じ、動的特性の不安定化を招く。これに対し、技術的思想３によれば、空気室内の空気が膨張した場合には、その膨張分を連通孔により外部へ逃がすことができるので、空気室の圧力変動を抑制して、空気ばねの値を安定に保つことができるという効果がある。その結果、動的特性の安定化を得ることができる。
技術的思想４記載の液封入式防振装置によれば、技術的思想３記載の液封入式防振装置の奏する効果に加え、第１取付け部材は、エンジン側に取り付けられる上端面と反対側となる下端面（底面）に凹部が凹設される柱状体に形成され、連通孔は、凹部の内壁部から上端面に向かって延設される縦孔と、その縦孔に一端が接続されると共に上端面側の外周面に他端が開口される横孔とを備えるので、エンジン側に取り付けられる座面としての上端面の面積を確保しつつ、連通孔を形成することができるという効果がある。また、このように連通孔を縦孔および横孔からなる貫通孔として形成することで、空気室内への異物の侵入を抑制することができるという効果がある。 Further, as the amplitude dependence imparting means described in the claims, for example, in the first to eighth embodiments, the concave portion 14 and the displacement regulating member 30 are used. In the third to fifth embodiments, the membrane member 320, 420 and 520 (spherical portion 320a, bellows-like shape or cloth-like body 520a) correspond to each.
<Others>
<Means>
The liquid-filled vibration isolator of the technical idea 1 includes a first attachment member attached to the engine side, a second attachment member attached to the vehicle body side, the second attachment member and the first attachment member, and a rubber. A liquid sealing chamber is formed between the vibration-proof base made of a rubber-like elastic body and the vibration-proof base attached to the second mounting member, and a diaphragm made of a rubber-like elastic body, and the liquid-filled chamber is made of the vibration-proof chamber A partition member for partitioning into a first liquid chamber on the substrate side and a second liquid chamber on the diaphragm side and forming an orifice for communicating at least the first liquid chamber and the second liquid chamber. A membrane part comprising a body and sealing the opening of a recess formed in a bottom surface facing the first liquid chamber of the first mounting member, thereby making the recess an air chamber filled with air When provided with an amplitude-dependent applying means for applying a non-linear with respect to the input amplitude to the stiffness of the membrane member.
The liquid-filled vibration isolator of the technical idea 2 is the liquid-filled vibration isolator of the technical idea 1 and includes a displacement restricting member, and the displacement restricting member is press-fitted into the recess of the first mounting member. An annular press-fit portion that seals the peripheral edge of the membrane member, and at least one through hole is formed on the inner peripheral side of the press-fit portion, and is disposed opposite to the membrane member at a predetermined interval. And a concave portion of the first mounting member includes a press-fitted wall portion into which the press-fitted portion of the displacement regulating member is press-fitted, and a membrane member connected to the press-fitted wall portion. And an inner wall portion that forms an inner wall of the air chamber, and the amplitude dependency imparting means is configured to change the displacement of the membrane member with respect to the restriction plate portion of the displacement restriction member or the inner wall of the recess. By letting the part regulate Imparting amplitude dependency on the input amplitude on the membrane member.
The liquid-filled vibration isolator according to technical idea 3 is the liquid-filled vibration isolator according to technical idea 1 or 2, wherein the liquid-filled vibration isolator is penetratingly formed inside the first mounting member to communicate the air chamber to the outside. A communication hole is provided.
The liquid-filled vibration isolator of technical idea 4 is the liquid-filled vibration isolator described in technical idea 3;
The first attachment member has an upper end surface attached to the engine side, a lower end surface opposite to the upper end surface facing the first liquid chamber, and the bottom surface in which the concave portion is provided, The vibration-proof base is formed in a columnar body that is vulcanized and bonded to the outer peripheral surface on the lower end surface side, and the communication hole includes a vertical hole extending from the inner wall portion of the concave portion toward the upper end surface, and the vertical And a horizontal hole having one end connected to the hole and the other end opened on the outer peripheral surface on the upper end surface side.
<Effect>
According to the liquid-filled vibration isolator described in the technical idea 1, it is made of a rubber-like elastic body and closes the opening of the concave portion provided in the bottom surface facing the first liquid chamber of the first mounting member. Since the membrane member having an air chamber filled with air is provided, for example, when a relatively small amplitude vibration is input, such as in an idle state, the liquid sealing chamber (first liquid There is an effect that a low dynamic spring characteristic can be secured by suppressing an increase in the hydraulic pressure in the chamber.
Further, according to the technical idea 1, since the amplitude dependence imparting means for imparting non-linearity to the input amplitude to the rigidity of the membrane member is provided, for example, when a relatively large amplitude vibration is input as in traveling, the membrane member The rigidity of the membrane member can be increased by the amplitude dependence applying means, and the membrane member can be made difficult to elastically deform. As a result, it is possible to suppress the escape of the liquid pressure in the liquid enclosure chamber (first liquid chamber), so that the fluid flow effect performed between the first liquid chamber and the second liquid chamber via the orifice is exhibited, and There is an effect that damping characteristics and high dynamic spring characteristics can be secured.
Furthermore, according to the technical idea 1, since the air chamber is formed by closing the opening of the recessed portion provided in the bottom surface facing the first liquid chamber of the first mounting member with the membrane member, the membrane member is It can be a part of the inner wall of the first liquid chamber. Therefore, unlike the conventional product, since the orifice is not formed between the first liquid chamber and the membrane member, the elasticity of the membrane member can be obtained even at the time of relatively high frequency vibration input in which the orifice of the partition member is clogged. Due to the deformation, an increase in the fluid pressure in the fluid sealing chamber (first fluid chamber) can be suppressed, and the low dynamic spring characteristics can be obtained.
As described above, according to the technical idea 1, the low dynamic spring characteristic at the time of relatively small amplitude vibration input and the high damping characteristic and the high dynamic spring characteristic at the time of relatively large amplitude vibration input are ensured. There is an effect that a low dynamic spring characteristic at the time of vibration input at a relatively high frequency can be obtained.
Note that “a partition member that forms an orifice for communicating at least the first liquid chamber and the second liquid chamber” described in the technical idea 1 means that at least one orifice is formed. Therefore, the form in which the partition member forms two or more orifices is not excluded. Moreover, a partition member may be comprised as a switching type which switches an orifice between a communication state and a interruption | blocking state. In this case, the number of orifices that can be switched between the communication state and the cutoff state is not limited. That is, the orifices to be switched are all of the orifices formed by the partition member (for example, one if the orifice formed by the partition member is one, two if the orifice is two, etc.) It may be an orifice, or only a part of the orifices (for example, one of the two orifices formed by the partition member).
Further, as the amplitude dependence imparting means described in the technical idea 1, for example, a member (for example, a non-stretchable cloth-like member) having higher rigidity than a rubber-like elastic body is embedded in the membrane member, and the member Examples include a mode in which the displacement of the membrane member by a predetermined amount is regulated by the above, or a mode in which the member is disposed at a position spaced from the membrane member by a predetermined distance and the displacement of the membrane member by a predetermined amount is regulated by the member. Is done.
In this case, according to the technical idea 1, since the membrane member is disposed on the first attachment member attached to the engine side, a part of the vibration transmission path from the membrane member to the vehicle body is formed by the vibration isolation base. be able to. Therefore, due to the rigidity of the membrane member being increased by the function of the amplitude dependence imparting means, the impact (for example, the impact when the cloth-like member is stretched or the membrane collides with the member that regulates the displacement). Even if an impact is generated, the vibration transmission of the impact can be reduced by the vibration-proof base, and the generation of abnormal noise on the vehicle body side can be suppressed.
According to the liquid-filled vibration isolator described in the technical idea 2, in addition to the effect exhibited by the liquid-filled vibration isolator described in the technical idea 1, the displacement regulating member has at least one through hole formed therethrough. Since it includes a regulating plate portion arranged to face the membrane member at a predetermined interval, the concave portion of the first mounting member has an inner wall portion that faces the membrane member at a predetermined interval and forms an inner wall of the air chamber. When the membrane member is displaced due to vibration input, the displacement can be regulated by receiving the membrane member by the regulating plate portion of the displacement regulating member or the inner wall portion of the recess. Therefore, it is possible to reliably impart amplitude dependency to the membrane member by the amplitude dependency imparting means.
In this case, according to the technical idea 2, since the displacement of the membrane member is restricted by the displacement restricting member and the displacement to the other side is restricted by the inner wall portion in the recess of the first mounting member. There is no need to provide displacement regulating members on both sides of the membrane member. That is, the inner wall portion of the concave portion of the first mounting member serves both as a role for forming the air chamber and a role for regulating the displacement of the membrane member. Thereby, the number of parts of the member for regulating the displacement of the membrane member can be reduced, and the product cost can be reduced correspondingly.
According to the liquid-filled vibration isolator described in the technical idea 3, in addition to the effect exhibited by the liquid-filled vibration isolator described in the technical idea 1 or 2, it is formed through the inside of the first mounting member, and the air chamber As a result, the air spring (volume modulus) of the air chamber can be kept stable. That is, since the first attachment member is attached to the engine side, when the engine temperature rises, the air chamber is also warmed with the rise, and the air in the air chamber expands. Therefore, the value of the air spring of the air chamber that contributes to the elastic deformation of the membrane member is fluctuated, leading to instability of dynamic characteristics. On the other hand, according to the technical idea 3, when the air in the air chamber expands, the expanded portion can be released to the outside through the communication hole. The value of can be kept stable. As a result, stabilization of dynamic characteristics can be obtained.
According to the liquid-filled vibration isolator described in the technical idea 4, in addition to the effect exhibited by the liquid-filled vibration isolator described in the technical idea 3, the first mounting member is opposite to the upper end surface attached to the engine side. The lower end surface (bottom surface) is formed in a columnar body having a recess, and the communication hole has a vertical hole extending from the inner wall portion of the recess toward the upper end surface, and one end connected to the vertical hole. And a lateral hole with the other end opened on the outer peripheral surface on the upper end surface side, so that the communication hole can be formed while ensuring the area of the upper end surface as a seating surface attached to the engine side. There is. In addition, by forming the communication hole as a through hole composed of a vertical hole and a horizontal hole in this way, there is an effect that it is possible to suppress the entry of foreign matter into the air chamber.

１００，２００，６００，７００，８００ 液封入式防振装置
１，２０１，６０１，７０１，８０１ 第１取付け金具（第１取付け部材）
１ａ 上端面
１ｂ 底面
２ 第２取付け金具（第２取付け部材）
２ａ 筒状金具（第２取付け部材の一部）
２ｂ 底金具（第２取付け部材の一部）
３ 防振基体
４ 仕切り部材
７ ダイヤフラム
１０ 液封入室
１０Ａ 第１液室
１０Ｂ 第２液室
１４ 凹部
１４ａ 被圧入壁部
１４ｂ 内壁部
１５，６１５，７１５，８１５ 連通孔
１５ａ，６１５ａ，７１５ａ，８１５ａ 縦孔
１５ｂ，６１５ｂ，７１５ｂ，８１５ｂ 横孔
２０，３２０，４２０，５２０ メンブレン部材
３０ 変位規制部材
３１ 圧入部
３１ａ 筒部（圧入部の一部）
３１ｂ 円環部（圧入部の一部）
３１ｃ 突条部（圧入部の一部）
３２ 規制板部
４０，２４０ 空気室 100, 200, 600, 700, 800 Liquid-filled vibration isolator 1, 201, 601, 701, 801 First mounting bracket (first mounting member)
1a Upper end surface 1b Bottom surface 2 Second mounting bracket (second mounting member)
2a Cylindrical bracket (part of the second mounting member)
2b Bottom bracket (part of second mounting member)
3 Anti-vibration base 4 Partition member 7 Diaphragm 10 Liquid enclosure chamber 10A First liquid chamber 10B Second liquid chamber 14 Recess 14a Press-fit wall portion 14b Inner wall portion 15,615,715,815 Communication holes 15a, 615a, 715a, 815a Vertical Holes 15b, 615b, 715b, 815b Lateral holes 20, 320, 420, 520 Membrane member 30 Displacement regulating member 31 Press-fit portion 31a Tube portion (part of press-fit portion)
31b Annular part (part of press-fit part)
31c Projection part (part of press-fit part)
32 Regulating plate 40,240 Air chamber

Claims (3)

エンジン側に取り付けられる第１取付け部材と、車体側に取り付けられる第２取付け部材と、前記第２取付け部材および第１取付け部材を連結すると共にゴム状弾性体からなる防振基体と、前記第２取付け部材に取り付けられ前記防振基体との間に液封入室を形成すると共にゴム状弾性体からなるダイヤフラムと、前記液封入室を前記防振基体側の第１液室および前記ダイヤフラム側の第２液室に仕切ると共に少なくとも前記第１液室および第２液室を連通させるオリフィスを形成する仕切り部材と、を備える液封入式防振装置において、
ゴム状弾性体からなると共に、前記第１取付け部材の前記第１液室に面する底面に凹設された凹部の開口を閉封することで、前記凹部を空気が充填された空気室とするメンブレン部材と、
前記メンブレン部材の剛性に入力振幅に対する非線形性を付与する振幅依存付与手段と、変位規制部材と、を備え、
前記変位規制部材は、前記第１取付け部材の凹部に内嵌圧入され前記メンブレン部材の周縁部をシールする円環状の圧入部と、前記圧入部の内周側に配設され少なくとも１の貫通孔が貫通形成されると共に前記メンブレン部材と所定間隔を隔てて対向配置される規制板部と、を備え、
前記第１取付け部材の凹部は、前記変位規制部材の圧入部が内嵌圧入される被圧入壁部と、前記被圧入壁部に連設され前記メンブレン部材と所定間隔を隔てて対向すると共に前記空気室の内壁を形成する内壁部と、を備え、
前記振幅依存付与手段は、前記メンブレン部材の変位を、前記変位規制部材の規制板部または前記凹部の内壁部に規制させることで、前記メンブレン部材に入力振幅に対する振幅依存性を付与することを特徴とする液封入式防振装置。 A first attachment member attached to the engine side, a second attachment member attached to the vehicle body side, the vibration-damping base member connecting the second attachment member and the first attachment member and made of a rubber-like elastic body, and the second A liquid-filled chamber is formed between the vibration-proof base and the vibration-proof base attached to the mounting member, and a diaphragm made of a rubber-like elastic body, and the liquid-filled chamber is defined as a first liquid chamber on the vibration-proof base and a diaphragm-side first In a liquid-filled vibration isolator comprising: a partition member that partitions into two liquid chambers and forms an orifice that communicates at least the first liquid chamber and the second liquid chamber.
It is made of a rubber-like elastic body, and by closing the opening of the recess formed in the bottom surface facing the first liquid chamber of the first mounting member, the recess is made an air chamber filled with air. A membrane member;
Amplitude dependence imparting means for imparting non-linearity to the input amplitude to the rigidity of the membrane member, and a displacement regulating member,
The displacement regulating member includes an annular press-fit portion that is press-fitted into a recess of the first mounting member and seals a peripheral portion of the membrane member, and at least one through-hole disposed on the inner peripheral side of the press-fit portion. And a restricting plate portion that is formed to penetrate and face the membrane member at a predetermined interval.
The concave portion of the first mounting member includes a press-fit wall portion into which the press-fit portion of the displacement restricting member is press-fitted, and is opposed to the membrane member that is connected to the press-fit wall portion with a predetermined interval. An inner wall forming an inner wall of the air chamber,
The amplitude dependence imparting means imparts amplitude dependence on input amplitude to the membrane member by restricting displacement of the membrane member to a restriction plate portion of the displacement restriction member or an inner wall portion of the recess. Liquid-filled vibration isolator. 前記第１取付け部材の内部に貫通形成され、前記空気室を外部に連通させる連通孔を備えることを特徴とする請求項１に記載の液封入式防振装置。 The formed through the interior of the first mounting member, the hydraulic antivibration device according to claim 1, characterized in that it comprises a communicating hole for communicating said air chamber to the outside. 前記第１取付け部材は、上端面が前記エンジン側に取り付けられると共に、前記上端面と反対側となる下端面が前記第１液室に面し前記凹部が凹設される前記底面とされ、前記下端面側の外周面に前記防振基体が加硫接着される柱状体に形成され、
前記連通孔は、前記凹部の内壁部から前記上端面へ向かって延設される縦孔と、前記縦孔に一端が接続されると共に前記上端面側の外周面に他端が開口される横孔と、を備えることを特徴とする請求項２記載の液封入式防振装置。
The first attachment member has an upper end surface attached to the engine side, a lower end surface opposite to the upper end surface facing the first liquid chamber, and the bottom surface in which the concave portion is provided, Formed in a columnar body to which the vibration-proof substrate is vulcanized and bonded to the outer peripheral surface on the lower end surface side,
The communication hole includes a vertical hole extending from the inner wall portion of the recess toward the upper end surface, and a horizontal hole having one end connected to the vertical hole and the other end opened to the outer peripheral surface on the upper end surface side. The liquid-filled vibration isolator according to claim 2 , further comprising a hole.
JP2011065001A 2011-03-23 2011-03-23 Liquid-filled vibration isolator Expired - Fee Related JP5670233B2 (en)

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