JPS5947541A - Vibro-isolating supporting body - Google Patents
Vibro-isolating supporting bodyInfo
- Publication number
- JPS5947541A JPS5947541A JP15845882A JP15845882A JPS5947541A JP S5947541 A JPS5947541 A JP S5947541A JP 15845882 A JP15845882 A JP 15845882A JP 15845882 A JP15845882 A JP 15845882A JP S5947541 A JPS5947541 A JP S5947541A
- Authority
- JP
- Japan
- Prior art keywords
- partition
- working chamber
- plate
- sponge
- sponge body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
- F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
- F16F13/106—Design of constituent elastomeric parts, e.g. decoupling valve elements, or of immediate abutments therefor, e.g. cages
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は防振支持体に係シ、特に高周波域と低周波域で
の防振特性に優わ、た、エンジンマウント等の如き弾性
支持体に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an anti-vibration support, and particularly to an elastic support such as an engine mount, which has excellent anti-vibration properties in high and low frequency ranges.
従来から、自動車のエンジンマウント、ボディマウント
等の防振ゴムマウント （防振支持体）とし２て、ゴム
ブロック全２個の数句金具の間に介在させた構造のもの
が用いられているが、高周波域での振動騒音を低減する
ために動バネ定数の小さなゴムを使用すると、かかるゴ
ムの損失係数が小さく、それ故減衰係数も小さくなって
、防振ゴムマウントに要請される特性を充分に満たし得
ながったのである。けだし、かかるエンジンマウントの
如き防振ゴムマウントには、高周波域（１’００１４近
辺）での振動騒音を低減するための低動バネ特性を備え
ると共に、低周波域（１５１］ｚ近辺）での振動を低減
するための高減衰特性（損失係数が大なること）を備え
るべきことが要求されるからである。Conventionally, vibration-proof rubber mounts (vibration-proof supports) such as automobile engine mounts and body mounts have been used with a structure in which they are interposed between two rubber blocks and a metal fitting. If rubber with a small dynamic spring constant is used to reduce vibration noise in the high frequency range, the loss coefficient of such rubber will be small, and therefore the damping coefficient will also be small, making it sufficient to meet the characteristics required of a vibration-proof rubber mount. It was not possible to satisfy the requirements. However, anti-vibration rubber mounts such as engine mounts have low dynamic spring characteristics to reduce vibration noise in the high frequency range (near 1'0014), as well as low dynamic spring characteristics in the low frequency range (near 151]z). This is because it is required to have high damping characteristics (large loss coefficient) to reduce vibrations.
一方、かかる要求に応するために、ゴムの弾性と流体の
流通抵に［、全利用した構造の各種の弾性支持体、所謂
流体入りマウントが提案されているが、中でも特開昭５
７−９３４０号公報において提案された弾性的緩衝支持
体は、支持プレートと低部プレートとの間に円錐状の弾
性部材ヲ設け、且つ該弾性部材内に所定の流体を充填し
た作動室を形成し、且つ該作動室の外側に形成される可
撓性袋にて囲まれた平衡室と該作動室と全仕切るように
２枚の止めプレートを設け、さらにかかる止めプレート
に所定長さのオリフィスを設けると共に、該止めプレー
トに挾持された可動盤を前記作動室内の流体に加わる圧
力によって移動可能に設けたものであって、これによシ
有効な振動減衰作用を発揮させるようにしているのであ
る。即ち、一般にこの種の流体入りマウントでは、高周
波振動が入力すると作動室内の流体は剛体として作用し
、このため前記弾性部材として動バネ定数の低いゴムを
使用してもマウント全体としては動バネ定数の高いもの
と々９、有効な振動低減効果を連成することが困難であ
ったのであるが、これ全ＭｉＪ記可動盤の移動による作
動室内容積の変動（流体圧の吸収）によって効果的に解
消せしめたのであり、また低周波数振動入力時には該可
動盤の自由な移動ヲ前記止めプレートにて阻止し、以て
前記オリフィスを通じて作動室から平衡室に向って流体
が流動するようにして、その流通抵抗等の作用によって
マウント全体としての損失係数を大きくして、低周波振
動に対する減衰特性をも効果的に発揮せしめ得るように
したのである。On the other hand, in order to meet such demands, various types of elastic supports, so-called fluid-filled mounts, have been proposed that take full advantage of the elasticity of rubber and the resistance to fluid flow.
The elastic buffer support proposed in Publication No. 7-9340 has a conical elastic member provided between a support plate and a lower plate, and forms an operating chamber filled with a predetermined fluid within the elastic member. In addition, two stop plates are provided to completely partition the working chamber from an equilibrium chamber surrounded by a flexible bag formed outside the working chamber, and an orifice of a predetermined length is provided in the stop plates. and a movable plate clamped by the stop plate is provided so as to be movable by the pressure applied to the fluid in the working chamber, thereby exerting an effective vibration damping effect. be. That is, in general, in this type of fluid-filled mount, when high-frequency vibration is input, the fluid in the working chamber acts as a rigid body. Therefore, even if rubber with a low dynamic spring constant is used as the elastic member, the mount as a whole has a low dynamic spring constant. 9, it was difficult to couple an effective vibration reduction effect, but this can be effectively achieved by changing the working chamber internal volume (absorbing fluid pressure) due to the movement of the movable plate. Furthermore, when low-frequency vibrations are input, the free movement of the movable plate is prevented by the stop plate, and the fluid flows from the working chamber to the equilibrium chamber through the orifice. By increasing the loss coefficient of the mount as a whole through the effects of flow resistance, etc., it is possible to effectively exhibit damping characteristics against low-frequency vibrations.
このように、かかる特開昭５７−９３４０号公報に提案
された可動盤利用の流体入りマウントは、これまでの流
体入りマウントに内在する間ｂｔ巧妙に）ψ１決した優
れたものであるが、これとても未だ解決されるべきいく
つかの問題が内在していることが本発明者らの検削によ
って明らかになったのである。即ち、高周波振動の入力
時においては翁効な低動バネ定数を示し、また低周波振
動の入力時においては大きな損失係数を示すべく設泪さ
れた可動盤を有する流体入りマウントが、成る低周波領
域の振動が入力１．たときには大きな損失係数が得られ
たいことがあシ、このためその尚減衰特性を充分に発揮
できない場合があると層りことが明らかとなったのであ
る。そして、またかかる構造のマウントにあっては、作
動室と平衡室を仕切る二つの止めプレート間に、それら
画室のシ−ルを行ないつつ、所定の可動盤を移動可能に
挾持せしめ、且つ高周波振動の入力時における作動室の
圧力変動音吸収し得るように、その要求特性に応じて設
計し、組み付ける必要が生じるが、各周波数領域におけ
る要求特性全勘案してその設計を行なうことは容易でな
く、しかも微細な隙間に可動盤を正確に組み付けること
も非常に困難であって、これがその製作を著しく困難な
らしめているのである。In this way, the fluid-filled mount using a movable plate proposed in Japanese Patent Application Laid-Open No. 57-9340 is superior to the conventional fluid-filled mounts. The inventors' examination revealed that there are some problems that still need to be solved. In other words, a low-frequency mount consisting of a fluid-filled mount with a movable plate that is designed to exhibit a low dynamic spring constant when high-frequency vibrations are input, and a large loss coefficient when low-frequency vibrations are input. The vibration of the area is input 1. In some cases, it is desirable to obtain a large loss coefficient, and it has become clear that there are cases where the damping characteristics cannot be fully demonstrated. In addition, in a mount having such a structure, a predetermined movable plate is movably held between two stop plates that partition the working chamber and the equilibrium chamber while sealing these compartments, and a high-frequency vibration It is necessary to design and assemble according to the required characteristics so that the sound of pressure fluctuations in the working chamber can be absorbed when the input frequency is input, but it is not easy to design by taking into account all the required characteristics in each frequency range. Furthermore, it is extremely difficult to assemble the movable plate accurately in a minute gap, which makes its manufacture extremely difficult.
ここにおいて、本発明は、かがる事情に鑑みて為された
ものであって、その主たる目的とするところは、流体媒
体を利用した防振支持体において高周波域で低動バネ特
性を発揮する一方、低周波域でもその入力される低周波
振動の如何にかかわらず優れた高減衰特性を発揮せしめ
るようにすることにあり、寸た他の目的は、そのような
優れた防振特性を有する防振支持体を容易に設計、製作
し得るようにすることにある。The present invention has been made in view of the above circumstances, and its main purpose is to exhibit low dynamic spring characteristics in a high frequency range in a vibration isolating support using a fluid medium. On the other hand, the objective is to exhibit excellent high damping characteristics even in the low frequency range, regardless of the input low frequency vibration. An object of the present invention is to enable a vibration-proof support to be easily designed and produced.
そして、これらの目的を達成するため、本発明にあって
は、ゴム弾性体からなる肉厚の筒状体のフィスを有する
仕切９手段を設けて該筒状体内に作動室−ｔＪＷ成する
と共に、該仕切９手段の外側に少なくとも一部が可撓性
薄膜からなる囲いにて平衡室を形成して、該平衡室とｍ
Ｊ記作動室とをｎｌＪ記オリフィスを介して連通せしめ
る一方、該作動室及び該平衡室内に所定の非圧縮性流体
を封入した防振支持体において、ＡＩＪ記仕切シ手段に
、所定厚さのスポンジ体を収容、保持せしめると共に、
該スポンジ体の一方の面の少なくとも一部分子 ｔ４’
Ｊ ＲＬ作動室に対して露出せしめ、該作動室内の非圧
縮性流体の正方が該スポンジ体に作用せしめられるよう
にしたことにある。In order to achieve these objects, the present invention provides a partition 9 means having a fin of a thick cylindrical body made of a rubber elastic body to form a working chamber -tJW in the cylindrical body. , an equilibrium chamber is formed by an enclosure at least partially made of a flexible thin film on the outside of the partition 9 means, and m is connected to the equilibrium chamber.
In the vibration-proof support body, which communicates with the working chamber J through the orifice nlJ, and in which the working chamber and the equilibrium chamber are filled with a predetermined incompressible fluid, the partitioning means AIJ is provided with a predetermined thickness. In addition to housing and holding the sponge body,
At least some molecules t4' on one side of the sponge body
JRL is exposed to the working chamber so that a square of incompressible fluid within the working chamber is made to act on the sponge body.
従って、かかる構成の防振支持体によれは、作動室と平
衡室を仕切る仕切９手段に収容、保持きれたスポンジ体
が、高周波撮動の入力によって作動室内に存在する非圧
縮性流体に加わる圧力をその良好な変形作用によって効
果的に吸収１７て、以て高周波振動入力時における支持
体全体としての動バネ定数を低く維持せしめ、これによ
り良好な防振効果全発揮せしめ得るのであり、一方低周
波振動が人力したときには、スポンジ体自体の有するバ
ネの極端な非線形特性乃至はその弾性復元作用等の作用
によって、入力される低周波振動の種類の如何によらず
、大きな減衰係数が得られ、以て特定の低周波振動が入
力したときに減衰効果が達成され得ない問題も全く解消
されるに至ったのである。しかも、このような優れた高
周波域、低周波域における防振性能は、単に仕切り手段
に対して所定厚さのスポンジ体を収容、保持せしめれば
足りるため、その設計、製作が極めて容易となり、ひい
ては防振支持体の組付は作業を容易と為し、以てその製
作コストヲ低下せしめ得る利点も生じるのである。Therefore, with the vibration-proof support having such a structure, the sponge body housed and held in the partition 9 means for partitioning the working chamber and the equilibrium chamber is applied to the incompressible fluid existing in the working chamber by the input of high-frequency imaging. By effectively absorbing pressure 17 through its good deformation action, the dynamic spring constant of the support as a whole can be maintained low when high-frequency vibrations are input, thereby making it possible to fully exhibit a good vibration-proofing effect. When low-frequency vibrations are applied manually, a large damping coefficient can be obtained due to the extreme nonlinear characteristics of the spring of the sponge body itself or its elastic restoring action, regardless of the type of low-frequency vibration input. Thus, the problem of not being able to achieve a damping effect when a specific low-frequency vibration is input has been completely resolved. Moreover, such excellent vibration isolation performance in the high frequency range and low frequency range can be achieved by simply housing and holding a sponge body of a predetermined thickness in the partition means, making it extremely easy to design and manufacture. As a result, the work of assembling the vibration isolating support is facilitated, which has the advantage of reducing manufacturing costs.
以下、本発明を更に具体的に明らかにするために、図面
に示す本発明の幾つかの実施例について詳細に説明する
こととする。Hereinafter, in order to clarify the present invention more specifically, some embodiments of the present invention shown in the drawings will be described in detail.
先ず、本発明の一部施形態であるエンジンマウントの一
例を示す第１図及び第２図において、２は支持部材とし
ての支持金具であって、リング状に形成された円錐筒状
形の弾性都拐（筒状体）たるゴム４の一端側の頭部に一
体的に設けられてお９、またかかるゴム４の他端側の底
部には底部金具６が一体的に取り付けられている。なお
、これら支持金具２．底部金具６は、ゴム４の加硫成形
時に同時に加硫接着せしめられることにより、一体重な
部材として容易に製造することのできるものである。そ
して、かかる底部金具６の円筒状樹５分の下端には保護
キャンプ８がカシメ付けられており、該支持金具２及び
保護キャップ８を介してエンジンが車体に取！けられる
こととなる。なお、８ａは保護キャップ８の内外の空気
を流通せしめるための通孔である。First, in FIGS. 1 and 2 showing an example of an engine mount which is a partial embodiment of the present invention, reference numeral 2 denotes a support metal fitting as a support member, which is a conical cylindrical elastic member formed in a ring shape. A ring 9 is integrally provided on the head of one end of the rubber 4, which is a cylindrical body, and a bottom metal fitting 6 is integrally attached to the bottom of the other end of the rubber 4. In addition, these supporting metal fittings 2. The bottom metal fitting 6 is vulcanized and bonded at the same time as the rubber 4 is vulcanized and molded, so that it can be easily manufactured as an integral member. A protective camp 8 is caulked to the lower end of the cylindrical tree 5 of the bottom metal fitting 6, and the engine is attached to the vehicle body via the support metal fitting 2 and the protective cap 8. This results in him being kicked. Note that 8a is a through hole for allowing air to circulate inside and outside the protective cap 8.
１だ、かかるエンジンマウント内には、振動の入力方向
に対して直角な方向に位置する仕切９プレート１０が設
けられていて、該円錐筒状形のゴム４内に作動室１２を
形成している。更に、かかる仕切りプレート１０の下側
の空間が、底部金具６と保護キャップ８とのカシメ都に
周縁が把持された可撓性薄膜としてのダイヤフラムＩ４
によつて、部活に仕切られでおり、該仕切りプレート１
０との間に容積可変の平衡室１６を形成（７て１纏る。1. Inside this engine mount, a partition 9 plate 10 is provided which is located in a direction perpendicular to the vibration input direction, and an operating chamber 12 is formed within the conical cylindrical rubber 4. There is. Furthermore, the space below the partition plate 10 is filled with a diaphragm I4 as a flexible thin film whose peripheral edge is held by the caulking of the bottom metal fitting 6 and the protective cap 8.
The club activities are divided by the partition plate 1.
An equilibrium chamber 16 with a variable volume is formed between the 7 and 1.
そして、かかる作動室１２並びに平衡室１６内に体１８
が封入されている。なお、２ｏはカシメ伝達リングであ
って、保護キャップ８０力シメ作用によって仕切りプレ
ー）１０が底音ＩＳ金具６の係合ｆｌＳに係合して固定
せ１．められるようになっている。A body 18 is placed in the working chamber 12 and the equilibrium chamber 16.
is included. 2o is a caulking transmission ring, and the protective cap 80 (partition play) 10 engages with the engagement flS of the bottom sound IS metal fitting 6 and is fixed by the force caulking action of the protective cap 80. It is becoming more and more popular.
そして、かかるエンジンマウント内において作動室１２
と平衡室１６とを仕切る仕りノリプレート１ （ｌは、
第１図に示されるように、金属またはプラスチック等の
拐料九らなる剛性のある上部プレート２２と下部プレー
ト２４とがらなシ、それらプレートの重ね合せによって
その周縁の合わせ面に沿って所定長さの周溝、即ちオリ
フィス２６が形成され、そして第２図に示される如く、
そのオリフィス２６の一方の端部側では、上部プレート
２２を貫通して作動室１２側に開口する開口部２８が設
けられておシ、また該オリフィス２６の他方の側の端部
が下部プレート２４ケ貫通して平衡室１６側に開口する
開口部３０が形成でれているのである。また、かかる上
部プレート２２並ひに下部プレート２４の中央部の対向
する部分に円形の凹所３２．３４がそれぞれ設けられ、
それらプレート２２．２４の重ね合わせによって円形の
ポケット部３６が形成きれ、そこに独立気泡から構成さ
れる所定厚さのスポンジ板３８が隙間なく充満せしめら
れているのである。更に、上部プレート２２及び下部プ
レート２４に設けられた四部３２．３４の対向する部分
には、第２図に示される如き円形の通孔４０．４２が複
数設けられ、ポケット部３６に充満されたスポンジ板３
８のそれぞれの側の面がそれら通孔４０．４２ｅ介して
作動室１２．平衡室１６内の非圧縮性流体にそれぞれ接
触せしめられ得るようｄ構成されている。In this engine mount, a working chamber 12 is provided.
and the equilibrium chamber 16 are separated by a partition plate 1 (l is
As shown in FIG. 1, a rigid upper plate 22 and a lower plate 24 made of a material such as metal or plastic are separated, and by overlapping these plates, a predetermined length is formed along the mating surfaces of their peripheries. A circumferential groove or orifice 26 is formed, and as shown in FIG.
One end of the orifice 26 is provided with an opening 28 that passes through the upper plate 22 and opens toward the working chamber 12. An opening 30 is formed therethrough and opens to the equilibrium chamber 16 side. Further, circular recesses 32 and 34 are provided in opposing central portions of the upper plate 22 and the lower plate 24, respectively,
A circular pocket 36 is formed by overlapping these plates 22 and 24, and the pocket 36 is filled with a sponge plate 38 of a predetermined thickness made of closed cells without any gaps. Furthermore, a plurality of circular through holes 40,42 as shown in FIG. sponge board 3
8 are connected to the working chamber 12.8 through the through holes 40.42e. They are each configured to be able to come into contact with the incompressible fluid within the balance chamber 16.
従って、かかる構成のエンジンマウン）Ｋあっては、高
周波振動の入力時において作動室１２内の非圧縮性流体
に加わる圧力は、仕切りプレート１０のポケット部３６
内に保持されたスポンジ板３８の一方の面に通孔４０を
介して作用することとなり、そしてかかる流体圧の作用
するスポンジ板３８０面は該スポンジ板自体の変形の容
易性によって効果的に吸収されることとなり、以てゴム
４のバネ特性を有効に利用することができ、これによシ
全体としての動バネ定数を低く為し得て、目的とする高
周波域の振動騒音を有効に低減せしめ得るのである。一
方、低周波振動が入力された場合には、理論的には未だ
充分に解明されていないものの、かかるスポンジ体３８
自体の弾性作用等により、オリフィス２６を介しての作
動室１２と平衡室１８との間における非圧縮性流体の効
果的な流動が惹起され、そこに流動抵抗等によるエネル
ギーロスが形成されることにより、入力される低周波振
動のタイプの如何にかかわらず有効な大きな損失係数を
得ることができ、以て各種の低周波振動に対して高い減
衰作用を発揮することかできることとなったのである。Therefore, with the engine mount) K having such a configuration, the pressure applied to the incompressible fluid in the working chamber 12 at the time of input of high frequency vibration is reduced by the pocket portion 36 of the partition plate 10.
The fluid pressure acts on one surface of the sponge plate 38 held in the interior through the through hole 40, and the surface of the sponge plate 380 on which such fluid pressure acts is effectively absorbed by the ease of deformation of the sponge plate itself. As a result, the spring characteristics of the rubber 4 can be effectively utilized, thereby lowering the dynamic spring constant as a whole and effectively reducing vibration noise in the targeted high frequency range. It can be forced. On the other hand, when low-frequency vibrations are input, the sponge body 38
Due to its own elastic action, an effective flow of incompressible fluid is induced between the working chamber 12 and the equilibrium chamber 18 via the orifice 26, and energy loss is formed there due to flow resistance, etc. As a result, it is possible to obtain a large loss coefficient that is effective regardless of the type of low-frequency vibration that is input, and it has become possible to exhibit a high damping effect against various types of low-frequency vibration. .
因みに、このような効果は、本発明者等が汀々検ｔｊシ
て得られた実験結果の一部を示す以下の事実を比較する
ことによっても容易に理解されるところである。なお、
用いられた各種のタイプのエンジンマウントは次の通り
である。Incidentally, such an effect can be easily understood by comparing the following facts, which are some of the experimental results obtained by the inventors of the present invention. In addition,
The various types of engine mounts used are as follows.
Ａタイプ：ポケット部３６の高さを５ ｍｍとして、そ
こに略同じ高さのスポンジ
板３８を充填したもの（本発明）。Type A: The height of the pocket portion 36 is 5 mm, and the pocket portion 36 is filled with sponge plates 38 of approximately the same height (this invention).
Ｂタイプ：Ａタイプと同様なボケツ１一部に１間の厚さ
の可動盤を、その周縁を
上部プレート２２と下部プレート
２４にて挾持すると共に、その中
央部を弛ませ上下方向に移動可能
としたもの（従来例）。B type: Similar to A type, a movable plate with a thickness of 1 part is held by the upper plate 22 and lower plate 24 at the periphery, and the center part is loosened so that it can be moved in the vertical direction. (conventional example).
Ｃタイプ二作動室１２内に空電を注入したもの（比較例
）。Type C with static electricity injected into the second working chamber 12 (comparative example).
Ｄタイプ：作動室１２内にスポンジ体を存在させたもの
（比較例）。D type: A sponge body is present in the working chamber 12 (comparative example).
１弓タイプ：仕切り手段として単にオリフィス２６を有
する仕切りプレートを設
けたもの（通孔４０．４２．スポ
ンジ板３８等は存在しない）（比
較例）。1 bow type: one in which a partition plate having an orifice 26 is simply provided as a partition means (through holes 40, 42, sponge plate 38, etc. are not present) (comparative example).
とれらのタイプのエンジンマウントを用いて得られた結
果は、下記第１表の通りである。なお、静的バネ定数（
Ｋｓ）は１５ ｋｇ ／ｙｔｔｙｙｔであった。The results obtained using these types of engine mounts are shown in Table 1 below. In addition, the static spring constant (
Ks) was 15 kg/yttyyt.
上記第１表によれば本発明に従うスポンジ板３８を仕切
シブレート１０に保持せしめたＡタイプのエンジンマウ
ントにあっては、高周波域の振動に対して効果的な低動
バネ定数を具ａ１ｊするものであシ、しかも低周波域の
振動に対しても、そのＪ辰幅の如何にかかわらず犬ぎな
損失係数（Ｏを具備し、以て高周波域並びに低周波域に
おける有効な振動減衰作用を発揮することができるもの
であるのに対し、Ｂタイプの従来の可動盤を備えたエン
ジンマウントでは、低周波域において、損失係数（Ｏが
小さくなる場合があり、入力される振動のタイプによっ
て充分な減衰効果を発揮し得ないことを明らかにしてい
る。また、作動室内に空気を存在せしめたＣタイプの場
合には低周波域での損失係数を高めることが困難であシ
、さらにスポンジ体を作動室内に存在せしめたＤタイプ
のエンジンマウントでは高周波域での動的バネ定数が画
く、それ放置周波域での防振特性が良くないことを示し
ている。なお、単にオリフィスのみを設けた剛体からな
る仕切りプレートを用いたＥタイプのマウントでは、低
周波域の損失係数は良好であるが、高周波域の動的バネ
定数が著しく大きく、それ放置周波域での防振には全く
不適当であることが明らかにされている。According to Table 1 above, the A type engine mount in which the sponge plate 38 according to the present invention is held on the partition plate 10 has a low dynamic spring constant a1j that is effective against vibrations in the high frequency range. Moreover, even in the case of vibrations in the low frequency range, it has a large loss coefficient (O) regardless of its J width, and exhibits an effective vibration damping effect in the high frequency range as well as the low frequency range. On the other hand, with the conventional B-type engine mount with a movable platen, the loss coefficient (O) may be small in the low frequency range, and depending on the type of input vibration, the loss coefficient (O) may be small. In addition, in the case of type C, which has air in the working chamber, it is difficult to increase the loss coefficient in the low frequency range, and it is also difficult to increase the loss coefficient in the low frequency range. The dynamic spring constant of the D-type engine mount placed in the working chamber is large in the high frequency range, which indicates that the vibration isolation characteristics are not good in the idle frequency range. The E-type mount, which uses a partition plate made of Something has been revealed.
このように、本発明に従ってスポンジ板３８を支持ブレ
ー１−１０に収容、保持せしめたエンジンマウントは、
高周波振動に対して優れた防振効果を有することは勿論
、低周波振動の各種のタイプのものに対しても優れた減
衰特性（損失係数を大ぎく為し得る故に）を発揮し得る
ものであるが、その低周波域における優れた減衰作用に
ついては未だ充分に解明されておらず、それ故あくまで
も推測の域を出るものではないが、恐らく、スポンジ板
３８内に存在する多数の気泡によるスポンジ板の圧縮性
乃至はかかるスポンジ板３８の弾性変形復元作用によっ
て、低周波振動の入力に基づく非圧縮性流体の圧力変動
と該圧力変動による該スポンジ板３８表面の変形との間
に位相差が生じないため、これが従来の可動盤の如き流
体移動とは異なるものとなって、オリフィス２０を介し
て一層効果的な流体移動が惹起されるようになシ、そし
てこれによってエネルギーロスが惹起され、以て上記Ｂ
タイプの如ｒ可動盤を用いたマウン１−に比べてより大
きな損失係数を具現すると共に、低周波振動の各種のタ
イプのものに対しても有効な減衰特性をもつものではな
いかと、考えられている。As described above, the engine mount in which the sponge plate 38 is accommodated and held in the support brake 1-10 according to the present invention is as follows.
It not only has an excellent vibration damping effect against high frequency vibrations, but also exhibits excellent damping characteristics (because the loss coefficient can be greatly reduced) against various types of low frequency vibrations. However, its excellent damping effect in the low frequency range has not yet been fully elucidated, and therefore it is only a matter of speculation, but it is probably due to the large number of bubbles present in the sponge plate 38. Due to the compressibility of the plate or the elastic deformation recovery action of the sponge plate 38, there is a phase difference between the pressure fluctuation of the incompressible fluid based on the input of low frequency vibration and the deformation of the surface of the sponge plate 38 due to the pressure fluctuation. Since this does not occur, this is different from the fluid movement as in the conventional movable platen, and more effective fluid movement is caused through the orifice 20, and this causes energy loss. Therefore, the above B
It is thought that this type of mount realizes a larger loss coefficient than the mount 1- which uses a movable plate, and also has effective damping characteristics against various types of low frequency vibrations. ing.
また、かくの如きマウント構造によれば、仕切シブレー
ト１（ＨＣ対して単に所定厚さのスポンジ板３８を収容
、保持して、その一方の面に作動室１２内の非圧縮性流
体が受ける圧力を作用せしめるようにすればよいもので
あるために、該仕切りプレート１００２枚のプレート２
２．２４の間に可動盤を挾持せしめる従来のエンジンマ
ウントに較べて、その設計が非常に簡単且つ容易となる
のであり、また当然のことながら、その組付けも殴めて
簡単で、製作も容易であって、その製作コストを著しく
低減せしめ得る等の利点も存するのである。Moreover, according to such a mounting structure, a sponge plate 38 of a predetermined thickness is simply accommodated and held in the partition sib plate 1 (HC), and the pressure applied to the incompressible fluid in the working chamber 12 is applied to one surface of the sponge plate 38. Since the plate 2 of the 1002 partition plates
Compared to the conventional engine mount that clamps the movable plate between 2.24 and 24, the design is much simpler and easier, and as a matter of course, the assembly is also much easier and the manufacturing process is also easier. It also has the advantage of being easy and significantly reducing manufacturing costs.
さらに、上側の構造にあっては、上部プレート２２の凹
部３２の底部に通孔４０か設けられると共に、下部プレ
ート２４の凹部３４の底部にも通孔４２が設けられてお
シ、このため作動室１２側から作用する力によって該ス
ポンジ体３８が変形されやすくなっている。なお、ここ
で８−マ、通孔、１２は上部プレート２２の通孔４０に
対応する位置に設けられており、これによって前記した
スポンジ板３８の変形がよシ一層効果的に行なわれ得る
ようになっている。Further, in the upper structure, a through hole 40 is provided at the bottom of the recess 32 of the upper plate 22, and a through hole 42 is also provided at the bottom of the recess 34 of the lower plate 24. The sponge body 38 is easily deformed by the force acting from the chamber 12 side. Note that the holes 8 and 12 are provided at positions corresponding to the holes 40 of the upper plate 22, so that the above-described deformation of the sponge plate 38 can be carried out more effectively. It has become.
甘た、第３図、第４図には、本発明の他の実施例が明ら
かにされているが、前実施例と同様な機能を有する同様
な部分には同一の符号をイ」シて説明を省略することと
し、異なる点についてのみ述べると、先ずこの実施例で
は、エンジンマウントは支持金具２を介してエンジン側
に取υ付けられ不一方、車体側には２部品６ａ、６ｂで
構成された底部金具６の数例フランジに設けられたボル
ト４４を介して取り付けられるようになっている。Another embodiment of the present invention is disclosed in FIGS. 3 and 4, and similar parts having similar functions to those of the previous embodiment are designated by the same reference numerals. The explanation will be omitted, and only the different points will be described. First, in this embodiment, the engine mount is attached to the engine side via the support fitting 2, and on the other hand, it is composed of two parts 6a and 6b on the vehicle body side. Some examples of the bottom metal fitting 6 can be attached via bolts 44 provided on the flange.
従って、保護ギャップ８は前例とは異なり、ボルト部を
有しておらず、単に内側に配置、取り付けられるダイヤ
フラム１４を保護する機能を有するのみである。Therefore, unlike the previous example, the protective gap 8 does not have a bolt part, and merely has the function of protecting the diaphragm 14 disposed and attached inside.
また、かかるマウント内において、作動室１２と平衡室
１６を仕切る仕切）手段４６は、ポット状の凹所を有す
る剛性部４２からなるものであって該ボッ１−形状の（
＋ｉ１１壁部分にスポンジ体４８が収容保持されている
。よシ具体的には第３図に示されるように、ポット形状
を為す下側部利５０のポット内に上側部利５２の円筒部
が圧入、固定せしめられることによって、ポット側壁部
の囲シに複数個のポケット部３６が形成され、そしてか
かるポケット部３６内に所定厚さのスポンジ体４８がそ
れぞれ充満されているのである。なお、スポンジ体４８
のそれぞれの面に対応する上側部材５２゜下側部材５０
には通孔４０，４２が前例と同様に設けられておシ、そ
れぞれ作動室１２内の非圧縮性流体１８．平衡室１６内
の非圧縮性流体１８に接触せしめられるようになってい
る。寸だ、仕切９手段４６を構成する上側部材５２には
、その周方向に延びる所定長さの連通孔５８が設けられ
ており、また下側部組５０の周縁部にもその周方向に所
定長さの連通孔５８が設けられており、該」二側部材５
２と下側部材５０が重ね合わせられたとぎに二つの連通
孔５６と５８が接続され、所定長さのオリフィスを形成
するようになっている。なお、」二側部材５２に設けら
れた連通孔５６は作動る。Further, in such a mount, a partitioning means 46 for partitioning the working chamber 12 and the equilibrium chamber 16 is composed of a rigid portion 42 having a pot-shaped recess.
A sponge body 48 is housed and held in the +i11 wall portion. More specifically, as shown in FIG. 3, the cylindrical part of the upper part 52 is press-fitted and fixed into the pot-shaped lower part 50, so that the enclosure of the pot side wall part is closed. A plurality of pocket portions 36 are formed in the pocket portion 36, and each of the pocket portions 36 is filled with a sponge body 48 having a predetermined thickness. In addition, the sponge body 48
Upper member 52° and lower member 50 corresponding to each surface of
Through holes 40, 42 are provided in the same way as in the previous example, and the incompressible fluid 18. in the working chamber 12, respectively. It is adapted to be brought into contact with an incompressible fluid 18 within an equilibrium chamber 16. The upper member 52 constituting the partition 9 means 46 is provided with a communication hole 58 of a predetermined length extending in the circumferential direction, and the peripheral edge of the lower part assembly 50 is also provided with a communication hole 58 of a predetermined length extending in the circumferential direction. A long communication hole 58 is provided, and the second side member 5
2 and the lower member 50 are overlapped, the two communicating holes 56 and 58 are connected to form an orifice of a predetermined length. Note that the communication hole 56 provided in the second side member 52 operates.
このように、仕切り手段をポット形状とし、その側壁部
にスポンジ体を収容保持せしめるようにしても、かかる
スポンジ体４８の一方の面が、通孔４０を介して作動室
１２内の非圧縮性流体１８に接触せしめられている限り
において、高周波振動の入力時において流体に加わる圧
力は、該スポンジ体４８の変形によって効果的に吸収せ
しめられるようになり、また低、周波振動の入力時にお
いては、該スポンジ体４８のバネの極端な非線形特性乃
至は弾性復元特性によって損失係数を大ならしめ、以て
優れた減衰性能を発揮させ得るのである。In this way, even if the partition means is pot-shaped and the sponge body is housed and held on the side wall thereof, one surface of the sponge body 48 can be inserted into the non-compressible part of the working chamber 12 through the through hole 40. As long as the sponge body 48 is in contact with the fluid 18, the pressure applied to the fluid when high-frequency vibrations are input is effectively absorbed by the deformation of the sponge body 48, and when low-frequency vibrations are input, The loss coefficient is increased by the extreme nonlinear characteristics or elastic restoring characteristics of the spring of the sponge body 48, thereby making it possible to exhibit excellent damping performance.
また、」二記二つの実施例においては、所定のスポンジ
体を収容、保持するために、仕切り手段として二つの部
材が用いられているが、第５図及び第６図に示されるよ
うに、単に一枚の仕切シ板６０で仕切シ手段を構成し、
該仕切り板６０の作動室１２側の面に凹部６２を設けて
、そこに所定のスポンジ板６４を充填せしめると共に、
該凹部６２の内周面に沿って止めリング６６を圧入する
ことによって、かかる充填されたスポンジ板６４を外れ
ないように押えることにより、該仕切υ板６０にスポン
ジ板６４を収容、保持させるようにすることも可能であ
る。この構成によれば、非圧縮性流体に対するスポンジ
板６４の接触面を大きくすることが可能である。なお、
６８はかかる仕切）板６０の端面に沿って所定長さに亘
って設けられたオリフィスを形成するための周溝であっ
て、さらに、第７図に示す仕切シ手段は、第５図及び第
６図に示される如ぎものと同様に一枚の仕切り板７４１
でて構成され、且つ第５図及び第６図のものと同様に所
定のスポンジ板６４が収容、保持されているが、前例と
異なるところは、該スポンジ板６４が収容された四部６
２の底部に複数の通孔７６ど・；設けら壮て：レシ、こ
れによってスポンジ板６４の作動室側から加わる圧力に
よって、該スポンジ板６４が変形しやすくなるように構
成されている。In addition, in the two embodiments described in Section 2, two members are used as partition means to accommodate and hold a prescribed sponge body, but as shown in FIGS. 5 and 6, The partitioning means is simply constituted by one partitioning plate 60,
A recess 62 is provided on the surface of the partition plate 60 on the working chamber 12 side, and a predetermined sponge plate 64 is filled therein.
By press-fitting a retaining ring 66 along the inner peripheral surface of the recess 62, the filled sponge plate 64 is held so that it does not come off, so that the sponge plate 64 is accommodated and held in the partition υ plate 60. It is also possible to According to this configuration, it is possible to increase the contact surface of the sponge plate 64 with the incompressible fluid. In addition,
Reference numeral 68 denotes a circumferential groove for forming an orifice extending over a predetermined length along the end face of the partition plate 60, and the partition means shown in FIG. A single partition plate 741 similar to the one shown in Figure 6.
5 and 6, and a predetermined sponge plate 64 is housed and held therein, but the difference from the previous example is that the four parts 6 in which the sponge plate 64 is housed are
A plurality of through holes 76 are provided at the bottom of the sponge plate 64 so that the sponge plate 64 is easily deformed by pressure applied from the working chamber side of the sponge plate 64.
ところで、以」二の具体例においても成る程度は説明し
たが、作動室１２と平衡室１６とを連通せしめるべく、
仕切シ手段に具備せしめられるオリフィスとしては、公
知の種々なる形態のものが適宜に採用され得るものであ
り、またオリフィスの形成にあっても単に１枚の板状の
部材に孔をあけたものから２枚の部利の重ね合せによっ
てオリフィスとなる流体流路が形成されるようにしても
よく、更にはかかるオリフィスが仕切シ手段内に設けら
れる場合の他、かかる仕切シ手段の周縁に設けられた溝
と該仕切シ手段の取シ付けられる部材の壁面との間でオ
リフィスを形成する周溝形態のものであっても何等差し
支えないのである。なおオリフィスの径としては、３〜
１０ ｙｕｎ程度（矩形の場合には面積換算）、そして
オリフィスの長さくＬ）と直径（Ｄ）の比としては、Ｔ
、 ／ Ｊ） −８〜３０程度の値が一般に採用される
ものである。By the way, although the degree of implementation has been explained in the second specific example, in order to make the working chamber 12 and the equilibrium chamber 16 communicate with each other,
As the orifice provided in the partitioning means, various known forms may be adopted as appropriate, and the orifice may be formed by simply drilling a hole in a single plate-shaped member. A fluid flow path serving as an orifice may be formed by superimposing two parts from each other, and furthermore, such an orifice may be provided in the partition means or at the periphery of the partition means. A circumferential groove may be used to form an orifice between the groove and the wall surface of the member to which the partition means is attached. The diameter of the orifice is 3~
10 yun (in the case of a rectangle, the area is converted), and the ratio of the orifice length (L) to the diameter (D) is T.
, /J) A value of about -8 to 30 is generally adopted.
また、７５−かる仕切シ手段に収容、保持されるスポン
ジ体としては、公知の各種のスポンジ体、例エバゴム、
ウレタン、ｐｖｃ、或いはオレフィン系等のスポンジ体
（発泡体）であり、独立気泡からなるものである。なお
、このようなスポンジ体は、一般に発泡倍率５〜５０倍
、見用は比重０．５〜００１のものとして製造されたも
のが好適に用いられることとなる。Further, as the sponge body accommodated and held in the partition means 75, various known sponge bodies may be used, such as evaporated rubber,
It is a sponge body (foam) made of urethane, PVC, or olefin, and is composed of closed cells. In addition, such a sponge body is generally preferably manufactured with an expansion ratio of 5 to 50 times and a specific gravity of 0.5 to 0.001.
さらに仕切り手段に収容、保持されて作動室側に露出せ
しめられるスポンジ体の面債ば、かかる仕切り手段の表
面積の１０〜８０％程度であり、このような露出比率に
おいて所定のスポンジ体が一般にかかる仕切う手段に形
成される凹所に隙間なく、場合によってはその高さの倍
程度までのものが適当な押え部材乃至は通孔乃至は格子
を有する部利によって押えられ、圧縮されて充填せしめ
られるようになっている。なお、かかるスポンジ体の厚
さは、高周波域の振動によって加わる流体圧力を吸収す
るべく適宜に決定されることとなるが、一般に数ｍｍ程
度、通常３〜１０ｇｍの範囲内のものである。Further, the surface area of the sponge body accommodated and held in the partition means and exposed to the working chamber side is about 10 to 80% of the surface area of the partition means, and at such an exposure ratio, a predetermined sponge body is generally There is no gap in the recess formed in the partitioning means, and in some cases, objects up to twice the height of the recess are held down by a suitable holding member or a part having a through hole or a grid, and are compressed and filled. It is now possible to The thickness of the sponge body is appropriately determined in order to absorb the fluid pressure applied by vibrations in the high frequency range, and is generally about several mm, usually within the range of 3 to 10 gm.
なお、本発明は、以上例示のもののみに限定されるもの
では決してなく、その趣旨を逸脱しない限シにおいて、
当業者の知識に基づいて種々なる変更、修正等を加える
ことができるものであって、本発明はそのような変形例
、修正例等を全て含むものと解釈されなければならない
。It should be noted that the present invention is by no means limited to the above-mentioned examples, and may include the following without departing from the spirit thereof:
Various changes, modifications, etc. can be made based on the knowledge of those skilled in the art, and the present invention should be construed as including all such modifications, modifications, etc.
また、上側にあっては、エンジンマウントに本発明を適
用した例について説明したが、本発明はその他ボデイマ
ウン１−等の防振支持体についても適用することが可能
である。Moreover, although an example in which the present invention is applied to an engine mount has been described above, the present invention can also be applied to other anti-vibration supports such as the body mount 1-.
第１図は、本発明の防振支持体に係るエンジンマウン１
−の一例を示す断面図であシ、第２図は、その仕切り手
段としての仕切シブレートの平面図である。第３図は、
本発明を適用したエンジンマウントの他の一例を示す断
面図であ如、第４図はそこで用いられたボッｌ−形状を
有する仕Ｕ／、Ｊ Ｄ手段の斜視図である。第５図は、
本発明に従う仕切シ手段の他の例を示す断面図であり、
第６図は、その斜視図である。第７図は、本発明に従う
仕切り手段の更に他の実施例を示す第５図に相当する図
である。
２：支持金具 ４：ゴム
６：底部金具 ８：保護キャップ８ａ：通孔
ｌＯ＝仕切シブレート１２：作動室
１４：ダイヤフラム１６：平衡室 １８：
非圧縮性流体２２：上部プレー１− ２４：下部プレ
ー１−２６．５４ニオリフイス ２８．．３０：開［１
部３６：ポケット部 ３８．６４：スポンジ板４０
．４２．７６：通孔 ４６：仕切り手段４８：スポンジ
体 ５０：下側部利５２：上側部材 ５６．
５８：連通孔６０．７４：仕切り板 ６２：凹部
６６：止めリング ６８：周溝FIG. 1 shows an engine mount 1 according to the vibration isolating support of the present invention.
Fig. 2 is a sectional view showing an example of - and Fig. 2 is a plan view of a partition plate serving as the partitioning means. Figure 3 shows
FIG. 4 is a sectional view showing another example of an engine mount to which the present invention is applied, and FIG. 4 is a perspective view of the bolt-shaped fittings U/JD means used therein. Figure 5 shows
It is a sectional view showing another example of the partition means according to the present invention,
FIG. 6 is a perspective view thereof. FIG. 7 is a diagram corresponding to FIG. 5 showing still another embodiment of the partitioning means according to the present invention. 2: Support metal fitting 4: Rubber 6: Bottom metal fitting 8: Protective cap 8a: Through hole
lO = partition sibrate 12: working chamber
14: Diaphragm 16: Equilibrium chamber 18:
Incompressible fluid 22: Upper play 1-24: Lower play 1-26.54 Niorifice 28. ．． 30: Open [1
Part 36: Pocket part 38.64: Sponge board 40
．． 42.76: Through hole 46: Partition means 48: Sponge body 50: Lower part 52: Upper member 56.
58: Communication hole 60. 74: Partition plate 62: Recess 66: Stop ring 68: Circumferential groove
Claims (1)
持部拐を一体的に設け、且つ他端側にオリフィスを有す
る仕切シ手段を設けて該筒状体内に作動室を形成すると
共に、該仕切り手段の外側に少なくとも一部が可撓性薄
膜からなる囲いにて平衡室を形成して、該平衡室と前記
作動室とを前記オリフィスを介して連通せしめる一方、
該作動室及び該平衡室内に所定の非圧縮性流体を封入し
た防振支持体において、 前記仕切９手段に、所定厚さのスポンジ体ケ収容、保持
せしめると共に、該スポンジ体の一方の面の少なくとも
一部分を０１■記作動室に対して露出せしめ、該作動室
内の非圧縮性流体の圧力が該スポンジ体に作用せしめら
れるようにしたことを特徴とする防振支持体。 （２）前記仕切り手段の前記スポンジ体が収容、保持さ
れる部位に複数の通孔部が設けられ、該通孔Ｓを介して
該スポンジ体の他方の面の少々くとも一部分がｎｉｌ記
平衡室側の流体に接触せしめられ得るようにした特許請
求の範囲第１項記載の防振支持体。 （３）前記仕切シ手段全第一の仕切り部材と第二の仕切
シ部材にて構成し、且つそれら二つの仕切９部材の間に
形成づれたポケット部に前記スポンジ体を充満せしめる
と共に、該スポンジ体の位置する第−及び第二の仕切す
部材のうちの少なくとも作動室側の音Ｉｓ位に複数の通
孔部Ｓを設け、該通孔部を介して該スポンジ体に前記非
圧縮性流体が接触せしめられるようにした特許請求の範
囲第１項記載の防振支持体。 （４）前記仕切９手段が、ｌ！’Ｊ記作動室に向って開
口する凹所を有し、且つ該凹所の少なくとも■（１］壁
部分が第一の仕切シ部拐及び第二の仕切り音ＩＳ利にて
構成されるようにすると共に、該側壁汗１）分に前記ス
ポンジ体が配置せしめられるようにした特許請求の範囲
第１項記載の防振支持体。 Ｇ５）、、 ｎｉｊ記ポケット部を形成する前記第一の
仕切９部材並びに第二の仕切、！ｌ） ｆ！Ｉｌｓ拐の
部位に、それぞれ前記複数の通孔部を設けると共に、そ
れら通孔部が対向して該第−の仕切９部材と該第二の仕
切り部材に配置せしめられる特許請求の範囲第３項また
け第４項記載の防振支持体。 （６） ＝記オリフィスが、前記仕切り手段全構成す
る二つの仕切り部材の重合によってその周方向に所定長
さに亘って形成され、且つ一方の仕切り邪拐を貫通して
該オリフィスの一方の端部が前記作動室側に開口せしめ
られる一方、他方の仕切り都拐ヲ貫通して該オリフィス
の他方の端部が前記平衡室側に開口せしめられる特許請
求の範囲第３項乃至第５項の何れかに記載の防振支持体
。[Scope of Claims] (1) A support part is integrally provided at one end of a thick cylindrical body made of a rubber elastic body, and a partition means having an orifice is provided at the other end to form a wall inside the cylindrical body. A working chamber is formed in the partition means, and an equilibrium chamber is formed outside the partition means, at least a portion of which is made of a flexible thin film, and the equilibrium chamber and the working chamber are communicated through the orifice. on the other hand,
In the vibration damping support in which a predetermined incompressible fluid is sealed in the working chamber and the equilibrium chamber, the partition 9 means accommodates and holds a sponge body of a predetermined thickness, and one surface of the sponge body is 01. A vibration-isolating support, characterized in that at least a portion thereof is exposed to the working chamber, so that the pressure of the incompressible fluid in the working chamber is applied to the sponge body. (2) A plurality of through holes are provided in a portion of the partition means in which the sponge body is accommodated and held, and at least a portion of the other surface of the sponge body is brought into equilibrium through the through holes S. The vibration isolation support according to claim 1, which is capable of being brought into contact with a fluid on the chamber side. (3) The partition means is composed of a first partition member and a second partition member, and fills the pocket portion formed between the two partition members with the sponge body, and A plurality of through holes S are provided at least on the working chamber side of the first and second partitioning members where the sponge body is located, and the incompressible material is inserted into the sponge body through the through holes. The vibration isolation support according to claim 1, which is adapted to be brought into contact with a fluid. (4) The partition 9 means l! It has a recess that opens toward the working chamber, and at least (1) a wall portion of the recess is configured with a first partition part and a second partition part. 2. The vibration damping support according to claim 1, wherein the sponge body is disposed in the side wall sweat area. G5), the first partition 9 member and the second partition forming the pocket portion! l) f! Claim 3, wherein the plurality of through-holes are provided in the respective portions of the Ils, and the through-holes are arranged facing each other in the first partition 9 member and the second partition member. The vibration-proof support according to item 4. (6) The orifice is formed over a predetermined length in the circumferential direction by overlapping two partition members constituting the partition means, and extends through one of the partitions to one end of the orifice. One end of the orifice is opened to the working chamber side, and the other end of the orifice is opened to the equilibrium chamber side by penetrating the other partition wall. Anti-vibration support described in Crab.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15845882A JPS5947541A (en) | 1982-09-11 | 1982-09-11 | Vibro-isolating supporting body |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15845882A JPS5947541A (en) | 1982-09-11 | 1982-09-11 | Vibro-isolating supporting body |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5947541A true JPS5947541A (en) | 1984-03-17 |
Family
ID=15672179
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15845882A Pending JPS5947541A (en) | 1982-09-11 | 1982-09-11 | Vibro-isolating supporting body |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5947541A (en) |
Cited By (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0115417A2 (en) * | 1983-01-25 | 1984-08-08 | Avon Industrial Polymers Limited | Hydraulically damped mounting device |
| EP0133588A2 (en) * | 1983-08-15 | 1985-02-27 | Bridgestone Corporation | Vibration isolating device and system |
| FR2563880A1 (en) * | 1984-05-03 | 1985-11-08 | Toyoda Gosei Kk | HYDRAULIC SHOCK ABSORBER DEVICE |
| EP0174184A2 (en) * | 1984-09-07 | 1986-03-12 | Bridgestone Corporation | Vibration isolating apparatus |
| JPS61189341A (en) * | 1985-02-18 | 1986-08-23 | Bridgestone Corp | Vibration isolating device |
| US4657232A (en) * | 1983-05-12 | 1987-04-14 | Avon Industrial Polymers Limited | Hydraulically damped mounting device |
| JPS62184253A (en) * | 1986-01-30 | 1987-08-12 | ロ−ド・コ−ポレ−シヨン | Quiescent fluid-loaded vibration isolator |
| US4756515A (en) * | 1984-08-07 | 1988-07-12 | The Toyo Rubber Industry Co., Ltd. | Fluid-damping vibration-isolating support device |
| US4793600A (en) * | 1986-03-14 | 1988-12-27 | Bridgestone Corporation | Vibration isolating apparatus |
| EP0307741A2 (en) * | 1987-09-18 | 1989-03-22 | Metzeler Gimetall Ag | Hydraulically damping two-chamber engine mounting |
| US4832319A (en) * | 1986-07-08 | 1989-05-23 | Bridgestone Corporation | Vibration absorbing apparatus |
| US4861006A (en) * | 1986-09-16 | 1989-08-29 | Bridgestone Corporation | Anti-vibration apparatus |
| JPH02146330A (en) * | 1988-10-18 | 1990-06-05 | Carl Freudenberg:Fa | Rubber seat |
| US4955589A (en) * | 1987-12-23 | 1990-09-11 | Avon Industrial Polymers Limited | Hydraulically damped mounting device |
| JPH0589998U (en) * | 1992-05-08 | 1993-12-07 | 株式会社フコク | Liquid-filled mount |
| US6352248B1 (en) | 1999-07-13 | 2002-03-05 | Carl Freudenberg | Hydraulically damped bearing |
| DE10064769A1 (en) * | 2000-12-22 | 2002-08-29 | Contitech Luftfedersyst Gmbh | Hydro spring |
| KR100907383B1 (en) | 2008-04-29 | 2009-07-10 | 현대자동차주식회사 | Air damping engine mount |
| CN108006150A (en) * | 2017-01-03 | 2018-05-08 | 北京京西重工有限公司 | Vertical decoupler for hydraulic mount |
| KR20180065158A (en) * | 2016-12-07 | 2018-06-18 | 현대자동차주식회사 | Nozzle plate of engine-mount |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5751847B2 (en) * | 1977-12-13 | 1982-11-04 | ||
| JPS5761248B2 (en) * | 1975-04-28 | 1982-12-23 | Mitsui Toatsu Chemicals | |
| JPS5853934B2 (en) * | 1979-12-26 | 1983-12-02 | 株式会社東芝 | Self-purifying catalyst |
-
1982
- 1982-09-11 JP JP15845882A patent/JPS5947541A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5761248B2 (en) * | 1975-04-28 | 1982-12-23 | Mitsui Toatsu Chemicals | |
| JPS5751847B2 (en) * | 1977-12-13 | 1982-11-04 | ||
| JPS5853934B2 (en) * | 1979-12-26 | 1983-12-02 | 株式会社東芝 | Self-purifying catalyst |
Cited By (29)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0115417A2 (en) * | 1983-01-25 | 1984-08-08 | Avon Industrial Polymers Limited | Hydraulically damped mounting device |
| US4657232A (en) * | 1983-05-12 | 1987-04-14 | Avon Industrial Polymers Limited | Hydraulically damped mounting device |
| EP0133588A2 (en) * | 1983-08-15 | 1985-02-27 | Bridgestone Corporation | Vibration isolating device and system |
| FR2563880A1 (en) * | 1984-05-03 | 1985-11-08 | Toyoda Gosei Kk | HYDRAULIC SHOCK ABSORBER DEVICE |
| US4756515A (en) * | 1984-08-07 | 1988-07-12 | The Toyo Rubber Industry Co., Ltd. | Fluid-damping vibration-isolating support device |
| EP0174184A2 (en) * | 1984-09-07 | 1986-03-12 | Bridgestone Corporation | Vibration isolating apparatus |
| EP0174184A3 (en) * | 1984-09-07 | 1986-05-14 | Bridgestone Corporation | Vibration isolating apparatus |
| US4802658A (en) * | 1984-09-07 | 1989-02-07 | Bridgestone Corporation | Vibration isolating apparatus |
| JPS61189341A (en) * | 1985-02-18 | 1986-08-23 | Bridgestone Corp | Vibration isolating device |
| JPS62184253A (en) * | 1986-01-30 | 1987-08-12 | ロ−ド・コ−ポレ−シヨン | Quiescent fluid-loaded vibration isolator |
| EP0235540A2 (en) | 1986-01-30 | 1987-09-09 | Lord Corporation | Hydraulic-damping mounting |
| US4709907A (en) * | 1986-01-30 | 1987-12-01 | Thorn Richard P | Quiet fluid filled vibration isolator |
| US4793600A (en) * | 1986-03-14 | 1988-12-27 | Bridgestone Corporation | Vibration isolating apparatus |
| US4832319A (en) * | 1986-07-08 | 1989-05-23 | Bridgestone Corporation | Vibration absorbing apparatus |
| US4861006A (en) * | 1986-09-16 | 1989-08-29 | Bridgestone Corporation | Anti-vibration apparatus |
| US4973031A (en) * | 1986-09-16 | 1990-11-27 | Bridgestone Corporation | Anti-vibration apparatus |
| EP0307741A2 (en) * | 1987-09-18 | 1989-03-22 | Metzeler Gimetall Ag | Hydraulically damping two-chamber engine mounting |
| US4955589A (en) * | 1987-12-23 | 1990-09-11 | Avon Industrial Polymers Limited | Hydraulically damped mounting device |
| JPH02146330A (en) * | 1988-10-18 | 1990-06-05 | Carl Freudenberg:Fa | Rubber seat |
| US5020782A (en) * | 1988-10-18 | 1991-06-04 | Firma Carl Freudenberg | Hydraulically damped rubber bearing having a flexibly expandable waveguide |
| JPH0589998U (en) * | 1992-05-08 | 1993-12-07 | 株式会社フコク | Liquid-filled mount |
| US6352248B1 (en) | 1999-07-13 | 2002-03-05 | Carl Freudenberg | Hydraulically damped bearing |
| DE10064769A1 (en) * | 2000-12-22 | 2002-08-29 | Contitech Luftfedersyst Gmbh | Hydro spring |
| KR100907383B1 (en) | 2008-04-29 | 2009-07-10 | 현대자동차주식회사 | Air damping engine mount |
| KR20180065158A (en) * | 2016-12-07 | 2018-06-18 | 현대자동차주식회사 | Nozzle plate of engine-mount |
| CN108006150A (en) * | 2017-01-03 | 2018-05-08 | 北京京西重工有限公司 | Vertical decoupler for hydraulic mount |
| EP3343064A1 (en) * | 2017-01-03 | 2018-07-04 | BeijingWest Industries Co. Ltd. | Vertical decoupler for a hydraulic mount |
| US20180187742A1 (en) * | 2017-01-03 | 2018-07-05 | Beijingwest Industries Co., Ltd. | Vertical Decoupler For A Hydraulic Mount |
| US10584761B2 (en) * | 2017-01-03 | 2020-03-10 | Beijingwest Industries Co., Ltd. | Vertical decoupler for a hydraulic mount |
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