JPS6288834A - Vibro-isolator - Google Patents
Vibro-isolatorInfo
- Publication number
- JPS6288834A JPS6288834A JP60227659A JP22765985A JPS6288834A JP S6288834 A JPS6288834 A JP S6288834A JP 60227659 A JP60227659 A JP 60227659A JP 22765985 A JP22765985 A JP 22765985A JP S6288834 A JPS6288834 A JP S6288834A
- Authority
- JP
- Japan
- Prior art keywords
- liquid
- cross
- cylinder
- passages
- throttle
- 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
- F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
- F16F13/1463—Units of the bushing type, i.e. loaded predominantly radially characterised by features of passages between working chambers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Body Structure For Vehicles (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
- Vehicle Body Suspensions (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
この発明は、たとえばエンジンマウント、ザスペンショ
ンプッシュ、キャブマウントなどとして用いることがで
きる液体入り防振装置の改良に関するものである。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an improvement in a liquid-filled vibration isolator that can be used, for example, as an engine mount, a suspension pusher, a cab mount, or the like.
（従来の技術）
従来この種の液体入り防振装置としては、たとえば、同
心配置した内筒および外筒をゴム弾性体によって相互連
結するとともに、このゴム弾性体内に、液体を封入した
二個一対の液体室を直径方向に対抗させて形成し、そし
てこれらの両液体重を一本もしくは複数本の絞り通路に
よって連通させたものがある。(Prior Art) Conventionally, this type of liquid-filled vibration isolator includes, for example, a pair of concentrically arranged inner and outer cylinders interconnected by a rubber elastic body, and a liquid sealed in the rubber elastic body. Some liquid chambers are formed diametrically opposed to each other, and these two liquid chambers are communicated through one or more restrictive passages.
かかる防振装置は、そこへ伝達されるとくに低周波大振
幅振動に対しては、液体室内の液体が絞り通路を通って
流動するに際し、その絞り通路が液体に及ぼす流動抵抗
によって、液体の運動エネルギーを熱エネルギーに変換
することにて振動の有効なる減衰をもたらすことができ
る。Such a vibration isolator prevents the motion of the liquid due to the flow resistance exerted on the liquid by the restriction passage when the liquid in the liquid chamber flows through the restriction passage. Converting energy into thermal energy can provide effective damping of vibrations.
（発明が解決しようとする問題点）
ところが、このような従来技術にあっては、両液体重の
連通をもたらす、絞り通路の種類が一種類であり、かつ
、その長さＪ５よび断面積が常に一定であるため、それ
らを、低周波帯域の振動の十分なる減衰に適合するよう
選択した場合には、高周波帯域中の比較的低い周波数の
振動によって、絞り通路内の液体の慣性力、摩擦力など
に起因する絞り通路の閉塞状態が惹起され、この結果と
して、防振装置の動的ばね定数の急激なる増加がもたら
され、それ以上の高周波振動に対しては、振動の減衰を
ほとんど行い得なくなるという問題があった。(Problems to be Solved by the Invention) However, in such prior art, there is only one type of throttle passage that brings communication between the two liquid masses, and its length J5 and cross-sectional area are Since they are always constant, relatively low frequency vibrations in the high frequency band will reduce the inertia, friction and A blockage state of the throttle passage is induced due to force, etc., resulting in a rapid increase in the dynamic spring constant of the vibration isolator, which hardly damps vibrations for higher frequency vibrations. The problem was that it could not be done.
この発明は、とくに、高周波小振幅（たとえば±０．０
５ｍｍ以下の）振動に対しては、絞り通路内の液体に、
いわゆる液柱共振が生じ、その共振周波数の直前（低周
波側）の周波数帯域では、動的ばね定数の大幅なる低下
がもたらされることに着目してなされたものであり、高
周波帯域での動ばね定数の増加を十分に抑制し得る防振
装置を提供するものである。This invention is particularly suitable for high frequency and small amplitude (for example ±0.0
For vibrations (less than 5mm), the liquid in the throttle passage
This was done by focusing on the fact that so-called liquid column resonance occurs, and in the frequency band just before the resonance frequency (low frequency side), the dynamic spring constant is significantly reduced. An object of the present invention is to provide a vibration isolating device that can sufficiently suppress an increase in constant.
（問題点を解決するための手段）
この発明の防振装置は、内筒と外筒との間に、ゴム、ゴ
ム状弾性材料などを主体とするたとえば、筒状をなす肉
厚の弾性体を配設することにより、この弾性体による内
外筒の相互連結をもたらし、そしてこの弾性体の軸線方
向内側位置に、その軸線を含む一の面内にて直径方向に
対抗するとともに、液体を包含する複数対の液体室を、
軸線方向もしくは半径方向へ離間させて形成し、さらに
、それぞれの対の液体室を、長さおよび断面積の少なく
とも一方、たとえば断面積が相違するそれぞれの絞り通
路によって連通させてなる。(Means for Solving the Problems) The vibration isolating device of the present invention has a thick elastic body mainly made of rubber, rubber-like elastic material, etc., in the shape of a cylinder, between the inner cylinder and the outer cylinder. By arranging the elastic body, the inner and outer cylinders are interconnected by the elastic body, and at the axially inner position of the elastic body, the elastic body is diametrically opposed in a plane including the axis, and contains a liquid. multiple pairs of liquid chambers,
The liquid chambers are formed to be spaced apart from each other in the axial direction or the radial direction, and each pair of liquid chambers is communicated by respective throttle passages having different at least one of length and cross-sectional area, for example, cross-sectional area.
（作 用）
この防振装置において、たとえば、軸線方向へ離間する
二対の液体室を、長さが等しく断面積が相違するそれぞ
れの液体室によって連通させた場合には、とくに、高周
波小振幅振動のそこへの伝達に際し、断面積が小さい絞
り通路内の液体には比較的低い周波数にて、また、断面
積が大きい絞り通路内の液体には、それより高い周波数
にてそれぞれ液柱共振が生じ、そしてかかる液柱共振が
生じるときには、共振点を境にしてその直前の周波数帯
域では、振動振幅が小さいほど動的ばね定数の大幅なる
低減がもたらされ、逆に、その直後の周波数帯域では動
的ばね定数の急激なる増加がもたらされるので、ここで
は、周波数の増加に対し、好ましくは、断面積が小さい
絞り通路内の液体による動的ばね定数の低減がもたらさ
れた後、引き続いて、断面積が大きい通路内の液体によ
る動的ばね定数の低減がもたらされるよう、それぞれの
断面積を選択することにより、小さい通路内の液体によ
る液柱共振後における動的ばね定数の増加傾向を、大き
い通路内の液体による動的ばね定数の減少をもって十分
有効に相殺することができ、この故に、高周波小振幅の
各種の振動に対して動的はね定数の増加を十分有効に抑
制することができる。(Function) In this vibration isolator, for example, when two pairs of liquid chambers separated in the axial direction are communicated with each other by means of liquid chambers having equal lengths and different cross-sectional areas, high frequency and small amplitude When vibrations are transmitted there, liquid column resonance occurs at a relatively low frequency for the liquid in the throttle passage with a small cross-sectional area, and at a higher frequency for the liquid in the throttle passage with a large cross-sectional area. occurs, and when such liquid column resonance occurs, the smaller the vibration amplitude in the frequency band just before the resonance point, the greater the reduction in the dynamic spring constant; Since the band results in a sharp increase in the dynamic spring constant, here, for an increase in frequency, preferably after a reduction in the dynamic spring constant due to the liquid in the throttle channel with a small cross-sectional area, Subsequently, by choosing the respective cross-sectional areas such that the liquid in the passages with a large cross-sectional area results in a reduction in the dynamic spring constant, the liquid in the passages with a small cross-section increases the dynamic spring constant after liquid column resonance. This tendency can be sufficiently effectively offset by a decrease in the dynamic spring constant caused by the liquid in the large passage, and therefore, the increase in the dynamic spring constant can be sufficiently effectively suppressed against various types of high-frequency, small-amplitude vibrations. can do.
なおこれらのことは、長さだけが相違する絞り通路を設
けた場合、長さおよび断面積の両方が相違する絞り通路
を設けた場合も同様であり、長さが短いほど、また断面
積が、大きいほど、液柱共振の発生周波数が高くなる。Note that these things are the same when providing throttle passages that differ only in length, or when providing throttle passages that differ in both length and cross-sectional area; the shorter the length, the larger the cross-sectional area. , the higher the frequency at which liquid column resonance occurs.
（実施例） 以下にこの発明を図示例に基づいて説明する。(Example) The present invention will be explained below based on illustrated examples.
第１図はこの発明の一実施例を示す断面図であり、図中
１は内筒を、２はこの内筒１の外周に、たとえば同心配
置した外筒をそれぞれ示し、ここではこれらの内外筒１
，２を、それらの間に配設した弾性体３によって相互連
結する。FIG. 1 is a cross-sectional view showing one embodiment of the present invention. In the figure, 1 indicates an inner cylinder, and 2 indicates an outer cylinder arranged concentrically around the outer circumference of the inner cylinder 1. Here, these inner and outer cylinders are shown. Cylinder 1
, 2 are interconnected by an elastic body 3 disposed between them.
たとえばゴム、ゴム状弾性材料などを主体とするこの弾
性体３は、その外周面に筒状部材４を有しており、この
弾性体３の内外筒１，２への連結は、これもたとえば、
弾性体３の内周面を内筒１に加硫接着させ、そしてその
外周面に、０リングを介して外ｆ？Ｉ２をかしめ固定す
ることにて行うことができる。For example, this elastic body 3 mainly made of rubber, rubber-like elastic material, etc. has a cylindrical member 4 on its outer peripheral surface, and the connection of this elastic body 3 to the inner and outer cylinders 1 and 2 is also, for example. ,
The inner peripheral surface of the elastic body 3 is vulcanized and adhered to the inner cylinder 1, and an outer f? This can be done by caulking and fixing I2.
またここでは、弾性体３の軸線方向内側位置で、その軸
線を含む一の面内に、直径方向に対抗するとともに、液
体を包含する二対の液体室５．５および６．６を軸線方
向へ離間させて形成する。ここにおけるこれらの液体室
５，６はいずれも、弾性体３に形成した窪み３ａと、外
筒２と、筒状部材４とによって区画されてそれらへ充填
された所要粘度の液体を十分液密に維持する。Here, at an axially inner position of the elastic body 3, two pairs of liquid chambers 5.5 and 6.6 that diametrically oppose each other and contain liquid are axially arranged in a plane that includes the axis of the elastic body 3. Formed in a spaced manner. Both of these liquid chambers 5 and 6 here are partitioned by a recess 3a formed in the elastic body 3, the outer cylinder 2, and the cylindrical member 4, and are sufficiently liquid-tight for the liquid of a desired viscosity filled therein. to be maintained.
そして図示例では、このように構成した二対の液体室の
うち、一方の対をなす液体室５．５を、筒状部材４の外
周面に形成した溝と、外筒内周面とで形成した断面積の
小さい二本の絞り通路７によって相互に連通させ、他方
の対をなす液体室６゜６を、同様にして形成した断面積
の大きい二本の絞り通路８によって相互に連通させる。In the illustrated example, one of the two pairs of liquid chambers configured in this way, the liquid chamber 5.5, is formed by a groove formed on the outer circumferential surface of the cylindrical member 4 and an inner circumferential surface of the outer cylinder. They are made to communicate with each other by two formed throttle passages 7 with a small cross-sectional area, and the other pair of liquid chambers 6゜6 are communicated with each other by two similarly formed throttle passages 8 with a large cross-sectional area. .
第２図はこの発明の他の実施例を示す断面図であり、こ
の例は、それぞれの絞り通路を弾性体３の内周側に形成
することにより、各絞り通路の長さを短くしたものであ
る。FIG. 2 is a sectional view showing another embodiment of the present invention, in which the length of each throttle passage is shortened by forming each throttle passage on the inner peripheral side of the elastic body 3. It is.
この例の弾性体３は、その軸線方向の中央部分で、その
内周面に、通路画成筒９を有しており、ここでは、この
通路画成筒９の内周面と、内筒１の外周面とで断面積の
異なる環状の絞り通路１０゜１１をそれぞれ形成し、こ
れらの絞り通路１０．１１を、通路画成筒９に設けた貫
通孔を介してそれぞれの対の液体室５，５および６，６
に同口させることにより、多対の液体室の相互の連通を
もたらす。The elastic body 3 in this example has a passage-defining cylinder 9 on its inner circumferential surface at its central portion in the axial direction. Annular throttle passages 10 and 11 having different cross-sectional areas are formed on the outer peripheral surface of the tube 1, and these throttle passages 10 and 11 are connected to each pair of liquid chambers through through holes provided in the passage defining cylinder 9. 5,5 and 6,6
By having the same opening, multiple pairs of liquid chambers are brought into communication with each other.
このように構成してなる防振装置において、高周波帯域
（たとえば４５〜５００Ｈｚ）の小振幅振動（たとえば
±ｏ、ｏｓｎ＋ｍ ＞が、たとえば外筒２に伝達された
場合には、断面積の小さい絞り通路７゜１０内の液体に
、比較的低い周波数での液柱共振が生じその共振周波数
の直前の周波数帯域にては、動的ばね定数ひいては絶対
ばねの顕著なる減少が、また、共振周波数の直後の周波
数帯域にては、絶対ばねの急激なる増加がもたらされる
。なおここで、振動周波数が一層高くなった場合には、
絶対ばねの低下がもたらされ、このとき絶対ばねは、絞
り通路７．１０の閉塞時のそれと同一となる。In the vibration isolating device configured in this way, when small amplitude vibrations (for example, ±o, osn+m) in a high frequency band (for example, 45 to 500 Hz) are transmitted to, for example, the outer cylinder 2, an aperture with a small cross-sectional area is used. Liquid column resonance occurs in the liquid in the passage 7.10 at a relatively low frequency, and in the frequency band just before the resonance frequency, there is a significant decrease in the dynamic spring constant and thus in the absolute spring, and also at the resonance frequency. In the immediately following frequency band, a sharp increase in the absolute spring is brought about.If the vibration frequency becomes even higher here,
A lowering of the absolute spring is effected, which is now the same as that when the throttle channel 7.10 is closed.
この一方において、通路７，１０の液体の液柱共振周波
数にては、断面積の大きい絞り通路８，１１内の液体は
いまだに液柱共振を生じな（へので、通常は、その周波
数およびその周波数の前後の周波数帯域の撮動に対して
は、絞り通路８．１１を通る液体流動が可能である。On the other hand, at the liquid column resonance frequency of the liquid in the passages 7 and 10, the liquid in the throttle passages 8 and 11, which have large cross-sectional areas, still does not cause liquid column resonance. For imaging of frequency bands around the frequency, a liquid flow through the restriction passage 8.11 is possible.
またここで、絞り通路８．７１内の液体は、通路７．１
０内の液体の液柱共振周波数より高い振動周波数にて液
柱共振を生じ、このことによってもまた、その共振周波
数を境にして絶対ばねの大幅なる減少および急激なる増
加がそれぞれもたらされる。Also here, the liquid in the throttle passage 8.71 is transferred to the passage 7.1.
A liquid column resonance occurs at a vibration frequency higher than the liquid column resonance frequency of the liquid in zero, which also results in a large decrease and a sharp increase, respectively, in the absolute spring past that resonance frequency.
従って、絞り通路７と８または１０と１１を設けた防振
装置において、通路７，１０内の液体に起因する絶対ば
ねの急激なる増加が生じる周波数帯域で、通路８．１１
内の液体に起因する絶対ばねの大なる低下がもたらされ
るよう、両絞り通路７．８および１０．１１の長さおよ
び断面積を選択した場合には、絶対ばねの一方の増加を
他方の低下によって相殺することができ、防振装置の絶
対ばねを各種の周波数に対して十分低く押えることがで
き、内筒１もしくは外筒２に伝達された振動を、その他
方側に対して有効に絶縁することができる。Therefore, in a vibration isolator provided with throttle passages 7 and 8 or 10 and 11, in a frequency band where a sudden increase in the absolute spring due to the liquid in passages 7 and 10 occurs, passages 8 and 11
If the lengths and cross-sectional areas of both throttle passages 7.8 and 10.11 are chosen so that a large reduction in the absolute spring due to the liquid in the The absolute spring of the vibration isolator can be held down sufficiently low for various frequencies, and the vibration transmitted to the inner cylinder 1 or outer cylinder 2 can be effectively isolated from the other side. can do.
すなわち、このように構成した防振装置によれば、周波
数変化に対するその絶対ばねの変化は、第３図でグラフ
に実線で示すようになる。なおここで、図に破線で示す
曲線は、絞り通路７，１０内の液体に基づく絶対ばねの
変化を示し、この曲線によれば、絶対ばねは、通路７，
１０内の液体の共振周波数Ａの直前の周波数帯域では大
きく低下し、その直後の周波数帯域では急激に増加する
に対し、図に一点鎖線で示す絞り通路８．１１内の液体
に基づく絶対ばねの変化によれば、そこの液体の共振周
波数Ｂの直前の周波数帯域、いいかえれば共振周波数Ａ
の直後の帯域において大幅に低下するので、この周波数
帯域では、これらの両組対ばね曲線の平均曲線となる防
振装置の絶対ばねを十分小さく抑えることができ、この
結果として、防振装置は、この周波数帯域においても撮
動絶縁機能を有効に発揮することができる。That is, according to the vibration isolating device configured in this way, the change in the absolute spring with respect to the frequency change is as shown by the solid line in the graph in FIG. Here, the curve shown by a broken line in the figure shows the change in the absolute spring based on the liquid in the throttle passages 7, 10, and according to this curve, the absolute spring is
In the frequency band immediately before the resonant frequency A of the liquid in 10, it decreases greatly, and in the frequency band immediately after that, it increases sharply, whereas the absolute spring based on the liquid in the throttle passage 8.11 shown by the dashed line in the figure According to the change, the frequency band immediately before the resonant frequency B of the liquid, in other words, the resonant frequency A
In this frequency band, the absolute spring of the vibration isolator, which is the average curve of both sets of pair spring curves, can be kept sufficiently small, and as a result, the vibration isolator , it is possible to effectively exhibit the imaging insulation function even in this frequency band.
また図の一点鎖線によれば、共振周波数Ａより低い周波
数帯域では、絶対ばねが十分低い値となるので、この部
分の絶対ばねが、防振装置の絶対ばねの大幅なる増加を
もたらすおそれは全くない。Furthermore, according to the dashed line in the figure, in the frequency band lower than the resonance frequency A, the absolute spring has a sufficiently low value, so there is no possibility that the absolute spring in this part will cause a significant increase in the absolute spring of the vibration isolator. do not have.
第４図はこの発明の他の実施例を示す断面図であり、対
をなすそれぞれの液体室５，５および６゜６を、弾性体
３の軸線を含む一の面内にて半径方向へ離間させて形成
したものである。FIG. 4 is a cross-sectional view showing another embodiment of the present invention, in which the paired liquid chambers 5, 5 and 6°6 are arranged in a radial direction within a plane including the axis of the elastic body 3. They are formed at a distance.
内周面を内筒１に、これもたとえば加硫接着されるこの
例の弾性体３は、その半径方向内側から順次に、窪み３
ａと、筒状部材４ａ上にかしめ固定されて液体室５．５
の区画に寄与する区画筒１２と、この区画筒１２に摩擦
掛合させた取付筒１３と、取付筒１３の外周面に接着さ
れて通路画成筒１４とともに、液体室６，６用の窪み３
ｂを形成する弾性体部分３Ｃとを具える。The elastic body 3 of this example, whose inner circumferential surface is also vulcanized and bonded to the inner cylinder 1, has depressions 3 sequentially formed from the inside in the radial direction.
a, and a liquid chamber 5.5 which is caulked and fixed onto the cylindrical member 4a.
A partitioning tube 12 that contributes to the partitioning, a mounting tube 13 frictionally engaged with the partitioning tube 12, a passage-defining tube 14 bonded to the outer peripheral surface of the mounting tube 13, and a recess 3 for the liquid chambers 6, 6.
and an elastic body portion 3C forming b.
このような弾性体３に対する外筒２の取り付けは、第１
．２図に示したところと同様に、弾性体３の外周に位置
するその筒状部材４ｂ上に外筒２をかしめ固定すること
により行われる。The attachment of the outer cylinder 2 to the elastic body 3 is performed in the first
．． This is done by caulking and fixing the outer cylinder 2 onto the cylindrical member 4b located on the outer periphery of the elastic body 3, in the same way as shown in FIG.
そしてまたこの例では、液体室５．５の連通をもたらす
絞り通路１５を、第１図で述べたと同様にして筒状部材
４ａと、区画筒１２とで形成し、そして液体室６．６の
連通をもたらす絞り通路１６を、第２図で述べたと同様
にして取付筒１３と、通路画成筒１４とで形成し、これ
らの絞り通路１５．１６を、断面積を等しくする一方、
通路１６の長さが通路１５のそれよも長いものとする。Also in this example, the throttle passage 15 that brings the liquid chamber 5.5 into communication is formed by the cylindrical member 4a and the partition tube 12 in the same manner as described in FIG. The throttle passage 16 that provides communication is formed by the mounting tube 13 and the passage defining tube 14 in the same manner as described in FIG.
It is assumed that the length of the passage 16 is longer than that of the passage 15.
この防振装置によれば、絞り通路１ｃＩ内の液体の液柱
共振が、絞り通路１６内の液体のそれよりも低い周波数
にて発生するので、絞り通路１５．１６の長さの比を、
絞り通路１５．１６内の液体に起因する絶対ばねのピー
ク値が、それぞれ、第５図の破線および一点鎖線と同一
もしくはそれらに近似したものとなるように選択するこ
とにより、防振装置の絶対ばねを、高周波振動に対して
より十分に低減させることができる。従ってこの防振装
置では、高周波撮動を広い周波数帯域にわたって有効に
絶縁することができる。According to this vibration isolator, since the liquid column resonance of the liquid in the throttle passage 1cI occurs at a lower frequency than that of the liquid in the throttle passage 16, the ratio of the lengths of the throttle passage 15.16 is
By selecting such that the peak values of the absolute spring due to the liquid in the throttle passages 15 and 16 are the same as or close to the dashed line and the dashed-dotted line in FIG. 5, respectively, the absolute The spring can be more effectively damped against high frequency vibrations. Therefore, with this vibration isolator, high frequency imaging can be effectively isolated over a wide frequency band.
なお、ここにおいて、それぞれの絞り通路１５゜１６内
にお【プる液柱共振は、断面積および長さの少なくとも
一方を相違させることにより、断面積が大きいものほど
、また長さが短いものほど発生周波数が高くなるので、
所要の共振周波数との間遠の下で、第４図に示す絞り通
路１６を、外筒２の内周に形成すること、絞り通路１５
を内筒１の外周に形成すること、ざらには、絞り通路１
６を外周２の内周に、そして絞り通路１５を内筒１の外
周にそれぞれ形成するとも′可能である。In this case, the liquid column resonance in each of the throttle passages 15 and 16 is caused by making at least one of the cross-sectional area and length different, so that the larger the cross-sectional area, the shorter the length. As the frequency increases,
Forming the throttle passage 16 shown in FIG. 4 on the inner circumference of the outer cylinder 2 at a distance from the required resonance frequency;
is formed on the outer periphery of the inner cylinder 1, roughly speaking, the throttle passage 1
It is also possible to form the throttle passage 6 on the inner periphery of the outer periphery 2 and the throttle passage 15 on the outer periphery of the inner cylinder 1.
以上この発明を図示例に基づいて説明したが、液体室の
対を三対以上形成すること、それぞれの絞り通路の、断
面積および長さの両方を変化させることも可能である。Although the present invention has been described above based on the illustrated examples, it is also possible to form three or more pairs of liquid chambers and to change both the cross-sectional area and length of each throttle passage.
（発明の効果）
従って、この発明によれば、複数対の液体室を、長さお
よび断面積の少なくとも一方が相違するそれぞれの絞り
通路によって連通させてそれぞれの絞り通路内の液体を
、異なる周波数にて液柱共振させることにより、とくに
ＪｊＸＷｉｔ幅の高周波撮動に対し、防振装置の動的ば
ね定数、ひいては絶対ばねを、広い周波数帯域にわたっ
て十分低く抑えることができる。(Effects of the Invention) Therefore, according to the present invention, a plurality of pairs of liquid chambers are communicated by respective throttle passages having different lengths and cross-sectional areas, and the liquid in each throttle passage is controlled to flow at different frequencies. By causing the liquid column to resonate at , the dynamic spring constant of the vibration isolator, and ultimately the absolute spring, can be kept sufficiently low over a wide frequency band, especially for high frequency imaging with a JjXWit width.
第１．２図はそれぞれこの発明の実施例を示す断面図、
第３図は第１．２図に示す装置の周波数と絶対ばねとの
関係を示すグラフ、
第４図はこの発明の他の実施例を示す断面図、第５図は
第４図に示す装置の周波数と絶対ばねとの関係を示すグ
ラフである。
１・・・内筒 ２・・・外筒３・・・弾性体
５，６・・・液体室７、 ８．１０． ｉ？
、 ７５．１６・・・絞り通路第１図
第２図
周液数−
第４図
！
Ｅ−１１１厘斤面図1.2 are cross-sectional views showing embodiments of the present invention, FIG. 3 is a graph showing the relationship between the frequency and absolute spring of the device shown in FIG. 1.2, and FIG. FIG. 5, which is a sectional view showing the embodiment, is a graph showing the relationship between the frequency and the absolute spring of the device shown in FIG. 4. 1... Inner cylinder 2... Outer cylinder 3... Elastic body 5, 6... Liquid chamber 7, 8.10. i?
, 75.16... Throttle passage Figure 1 Figure 2 Circumferential liquid number - Figure 4! E-111 rack surface diagram
Claims (1)
軸線方向内側位置に、その軸線を含む一の面内にて直径
方向に対向するとともに、液体を包含する複数対の液体
室を形成し、それぞれの対の液体室を、長さおよび断面
積の少なくとも一方が相違するそれぞれの絞り通路によ
って連通させてなる防振装置。1. An elastic body is disposed between the inner cylinder and the outer cylinder, and a plurality of elastic bodies are arranged inside the elastic body in the axial direction, diametrically opposed to each other in a plane including the axis, and containing a liquid. A vibration damping device that forms a pair of liquid chambers and communicates each pair of liquid chambers through respective throttle passages that are different in at least one of length and cross-sectional area.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60227659A JPS6288834A (en) | 1985-10-15 | 1985-10-15 | Vibro-isolator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60227659A JPS6288834A (en) | 1985-10-15 | 1985-10-15 | Vibro-isolator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6288834A true JPS6288834A (en) | 1987-04-23 |
Family
ID=16864324
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60227659A Pending JPS6288834A (en) | 1985-10-15 | 1985-10-15 | Vibro-isolator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6288834A (en) |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62184250A (en) * | 1986-02-08 | 1987-08-12 | Marugo Rubber Kogyo Kk | Liquid-filled bush |
| JPH01126451A (en) * | 1987-11-06 | 1989-05-18 | Kinugawa Rubber Ind Co Ltd | Fluid sealed-in vibration isolator |
| US4893799A (en) * | 1987-01-23 | 1990-01-16 | Kleber Industrie | Vibration isolation apparatus |
| US4896868A (en) * | 1988-01-28 | 1990-01-30 | Jean Thelamon | Hydraulic antivibratory support sleeve |
| EP0353700A2 (en) * | 1988-08-02 | 1990-02-07 | Bridgestone Corporation | Vibration damping device |
| JPH0246114U (en) * | 1988-09-22 | 1990-03-29 | ||
| FR2644864A1 (en) * | 1989-03-23 | 1990-09-28 | Tokai Rubber Ind Ltd | FLUID-FILLED CYLINDRICAL ELASTIC FITTING HAVING TWO ORIFICES WITH DIFFERENT PASSAGE SECTIONS |
| FR2650356A1 (en) * | 1989-07-31 | 1991-02-01 | Hutchinson | IMPROVEMENTS MADE TO MAN CHONS HYDRAULIC ANTI-VIBRATOR |
| DE3936347A1 (en) * | 1989-11-02 | 1991-05-08 | Freudenberg Carl Fa | HYDRAULICALLY DAMPING SLEEVE RUBBER SPRING |
| JPH03125046A (en) * | 1989-10-05 | 1991-05-28 | Carl Freudenberg:Fa | Hydraulic cushion type cylindrical rubber seat |
| FR2655113A1 (en) * | 1989-11-29 | 1991-05-31 | Nissan Motor | ELASTOMER DAMPING DEVICE FILLED WITH A FLUID. |
| US5221077A (en) * | 1989-05-15 | 1993-06-22 | Bridgestone Corporation | Vibration isolating apparatus |
| EP0971153A1 (en) * | 1998-06-30 | 2000-01-12 | Draftex Industries Limited | Movement-damping arrangements |
| JP2016089994A (en) * | 2014-11-07 | 2016-05-23 | トヨタ自動車株式会社 | Liquid-sealed vibration control device |
-
1985
- 1985-10-15 JP JP60227659A patent/JPS6288834A/en active Pending
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62184250A (en) * | 1986-02-08 | 1987-08-12 | Marugo Rubber Kogyo Kk | Liquid-filled bush |
| US4893799A (en) * | 1987-01-23 | 1990-01-16 | Kleber Industrie | Vibration isolation apparatus |
| JPH01126451A (en) * | 1987-11-06 | 1989-05-18 | Kinugawa Rubber Ind Co Ltd | Fluid sealed-in vibration isolator |
| US4896868A (en) * | 1988-01-28 | 1990-01-30 | Jean Thelamon | Hydraulic antivibratory support sleeve |
| EP0353700A2 (en) * | 1988-08-02 | 1990-02-07 | Bridgestone Corporation | Vibration damping device |
| JPH0246114U (en) * | 1988-09-22 | 1990-03-29 | ||
| US5060918A (en) * | 1989-03-23 | 1991-10-29 | Tokai Rubber Industries, Ltd. | Fluid-filled cylindrical elastic connector having two orifice passages with different cross sectional areas |
| FR2644864A1 (en) * | 1989-03-23 | 1990-09-28 | Tokai Rubber Ind Ltd | FLUID-FILLED CYLINDRICAL ELASTIC FITTING HAVING TWO ORIFICES WITH DIFFERENT PASSAGE SECTIONS |
| US5221077A (en) * | 1989-05-15 | 1993-06-22 | Bridgestone Corporation | Vibration isolating apparatus |
| US5088702A (en) * | 1989-07-31 | 1992-02-18 | Hutchinson | Hydraulic antivibratory sleeves |
| FR2650356A1 (en) * | 1989-07-31 | 1991-02-01 | Hutchinson | IMPROVEMENTS MADE TO MAN CHONS HYDRAULIC ANTI-VIBRATOR |
| JPH03125046A (en) * | 1989-10-05 | 1991-05-28 | Carl Freudenberg:Fa | Hydraulic cushion type cylindrical rubber seat |
| US5178376A (en) * | 1989-10-05 | 1993-01-12 | Firma Carl Freudenberg | Hydraulically damped rubber cartridge spring |
| DE3936347A1 (en) * | 1989-11-02 | 1991-05-08 | Freudenberg Carl Fa | HYDRAULICALLY DAMPING SLEEVE RUBBER SPRING |
| FR2655113A1 (en) * | 1989-11-29 | 1991-05-31 | Nissan Motor | ELASTOMER DAMPING DEVICE FILLED WITH A FLUID. |
| EP0971153A1 (en) * | 1998-06-30 | 2000-01-12 | Draftex Industries Limited | Movement-damping arrangements |
| JP2016089994A (en) * | 2014-11-07 | 2016-05-23 | トヨタ自動車株式会社 | Liquid-sealed vibration control device |
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