JPH0587182A - Fluid-filled vibration control device - Google Patents
Fluid-filled vibration control deviceInfo
- Publication number
- JPH0587182A JPH0587182A JP27712491A JP27712491A JPH0587182A JP H0587182 A JPH0587182 A JP H0587182A JP 27712491 A JP27712491 A JP 27712491A JP 27712491 A JP27712491 A JP 27712491A JP H0587182 A JPH0587182 A JP H0587182A
- Authority
- JP
- Japan
- Prior art keywords
- side walls
- fluid
- rubber elastic
- fluid chamber
- connecting band
- 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.)
- Granted
Links
Landscapes
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、自動車のエンジンマウ
ント等に使用する流体封入型防振装置に関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid filled type vibration damping device used for an engine mount of an automobile.
【０００２】[0002]
【従来の技術】この種の流体封入型防振装置に要望され
る特性は低周波振動での高い減衰性と高周波振動での低
い振動伝達率である。このうち、減衰性に関しては、流
体室の側壁を構成するゴム弾性体は弾性率等の関係で薄
弱なものにせざるを得ないから、振動時の特に圧縮しな
ければならないときにも側壁が単に外方に膨らむのみで
容積変化が十分起こらないといった傾向がある。このた
め、特開平１−１６４８３１号公報には剛性のある拘束
部材を両側壁間に掛け渡し、この拘束部材で両側壁を拘
束して圧縮時の外方の膨らみを抑制しようとするものが
見られる。これはこれでその目的を達しているのである
が、このような拘束部材を側壁間に掛け渡すと、側壁の
弾性率が高まり、高周波域での振動伝達率が悪くなって
しまう。2. Description of the Related Art The characteristics required for a fluid filled type vibration damping device of this type are high damping at low frequency vibrations and low vibration transmissibility at high frequency vibrations. Among them, regarding damping property, the rubber elastic body forming the side wall of the fluid chamber has to be made thin due to the relationship of elastic modulus, etc., so that the side wall is simply broken even when it must be compressed especially during vibration. There is a tendency that the volume does not change sufficiently only by bulging outward. For this reason, Japanese Unexamined Patent Application Publication No. 1-164831 discloses a method in which a rigid restraint member is hung between both side walls, and the restraint members restrain both side walls to suppress outward bulging during compression. Be done. This has achieved its purpose, but if such a restraint member is hung between the side walls, the elastic modulus of the side walls is increased, and the vibration transmissibility in the high frequency range is deteriorated.
【０００３】一方で、この種の流体封入型防振装置にか
かる振動荷重は単に主振動荷重方向である上下方向（支
持物の重量がかかる方向）だけと捉えるのは不十分で、
左右方向、前後方向（軸方向）にも同じようにかかる。
図１３はこの種の流体封入型防振装置Ａで自動車のエン
ジンＢをフレームＣに支持した平面図であるが、通常、
この流体封入型防振装置Ａを左右に二個用い、フレーム
Ｃには外筒側を、エンジンＢには内筒側を固定する。こ
れを見てもわかるように、エンジンＢは車輛の加減速や
制動あるいは道路の凹凸等によってあらゆる方向に振動
することは容易に理解できる。更に、エンジン形式等に
よっては上下方向以外の方向の荷重がかかる割合が一層
増すことも予想される。従って、減衰性及び振動伝達率
とも、この３方向からの振動荷重に対して満足するもの
でなければならない。On the other hand, it is not sufficient to grasp the vibration load applied to this type of fluid filled type vibration damping device only in the vertical direction (direction in which the weight of the support is applied) which is the main vibration load direction.
The same applies to the left-right direction and the front-back direction (axial direction).
FIG. 13 is a plan view in which an automobile engine B is supported on a frame C by a fluid filled type vibration damping device A of this type.
Two fluid-filled type vibration damping devices A are used on the left and right, and the outer cylinder side is fixed to the frame C and the inner cylinder side is fixed to the engine B. As can be seen from this, it can be easily understood that the engine B vibrates in all directions due to vehicle acceleration / deceleration, braking, road irregularities, and the like. Further, depending on the engine type and the like, it is expected that the load applied in a direction other than the vertical direction will further increase. Therefore, both the damping property and the vibration transmissibility must be satisfied with respect to the vibration load from these three directions.
【０００４】[0004]
【発明が解決しようとする課題】こういったことから、
本出願人は、主流体室（受圧側の流体室）内を貫通して
側壁間を一体的に連結し、且つ、内外筒間を荷重方向に
架橋する質量体を取り付けたゴム弾性支柱を設けた案件
を先に特願平２−１３３５７８号として提案している。
この弾性支柱によって圧縮時の側壁の外方膨らみが抑え
られるとともに、へたり防止が図られ、且つ、これらは
３方向からの振動荷重に対しても充足するものになっ
て、この種の流体封入型防振装置としてはほぼ理想のも
のが具現できたのである。[Problems to be Solved by the Invention]
The applicant has provided a rubber elastic column which penetrates the inside of the main fluid chamber (the fluid chamber on the pressure receiving side) and integrally connects the side walls with each other, and which has a mass body attached to bridge the inner and outer cylinders in the load direction. I have previously proposed this case as Japanese Patent Application No. 2-133578.
The elastic struts suppress outward bulging of the side wall during compression and prevent settling, and they also satisfy vibration loads from three directions. It was possible to realize a nearly ideal type vibration damping device.
【０００５】ところが、最近では、この種の流体封入型
防振装置は小型車種にも適用されるようになり、これに
応える小型のものになってくると、このような弾性支柱
は質量体で上下に分断されて振動荷重に対する歪率が大
きくなり、耐久性が確保できなくなってくる。又、耐久
性を確保しようとすれば、剛性の高いものにせざるを得
ず、その結果、所望の振動伝達率が得られないといった
ことが起こる。本発明は、このような課題を解決するも
のであって、要するに、小型の流体封入型防振装置であ
っても、減衰性、振動伝達率に不満のない流体封入型防
振支持装置を提案するものである。Recently, however, this type of fluid-filled type vibration damping device has come to be applied to small-sized vehicle types, and when it becomes a small size corresponding to this, such elastic support column is a mass body. As it is divided into upper and lower parts, the strain rate against vibration load becomes large, and durability cannot be secured. Further, in order to ensure durability, it is unavoidable that the rigidity be high, and as a result, a desired vibration transmissibility cannot be obtained. The present invention solves such a problem and, in short, proposes a fluid-filled type vibration-damping support device that is satisfactory in damping properties and vibration transmissibility even in a small-sized fluid-filled type vibration-damping device. To do.
【０００６】[0006]
【課題を解決するための手段】以上の課題を解決するた
め、本発明は、互いに同心若しくは上下方向に偏心して
配される内筒と外筒との間に、間隔をあけて筒軸に直角
に介装される二つのゴム弾性体の側壁と、この側壁間に
筒軸に平行に一体的に架橋される同じくゴム弾性体の隔
壁とで非圧縮性流体を封入する主流体室と従流体室とを
前記隔壁の下方と上方とに隔設し、これら主従流体室を
オリフィス構造で連通した流体封入型防振装置におい
て、前記主流体室内に、筒軸に平行に前記両側壁間を一
体的に架橋するゴム弾性体の連結帯を設け、この連結帯
の一部を質量体で置換してなる流体封入型防振装置を提
供する。SUMMARY OF THE INVENTION In order to solve the above problems, the present invention has a space between an inner cylinder and an outer cylinder, which are concentric with each other or eccentric in the vertical direction, and are perpendicular to the cylinder axis. A main fluid chamber and a sub-fluid that enclose an incompressible fluid between two side walls of a rubber elastic body interposed between the side walls and a partition wall of the same rubber elastic body that is integrally bridged between the side walls in parallel with the cylinder axis. In a fluid filled type vibration damping device in which a chamber is provided above and below the partition wall, and these main and sub fluid chambers are communicated by an orifice structure, the both side walls are integrated into the main fluid chamber in parallel with the cylinder axis. Provided is a fluid filled type vibration damping device in which a connecting band of a rubber elastic body that is cross-linked is provided and a part of the connecting band is replaced with a mass body.
【０００７】[0007]
【作用】上記の手段をとることにより、即ち、主流体室
内には両側壁間と一体的に架橋される連結帯が設けられ
ることにより、主流体室の収縮時、その側壁が外方へ膨
らもうとするのを抑える。更に、このとき、連結帯の一
部は質量体で置換されているから、その分、残りのゴム
弾性部の剛性は相対的に上がって側壁の膨らみ抑制効果
は一層高くなる。従って、振動時における流体室の容積
変化は促進されて高い減衰性を発揮する。一方、連結帯
の架橋方向は上下方向ではなく、これと直角な左右方向
であり、且つ、これの一部は質量体で置換されているか
ら、そのダンパー効果と相まって振動伝達率は低く抑え
られ、振動吸収性も高い。このように、減衰性、振動伝
達率とも、より好ましい方向に作用する。By the above-mentioned means, that is, by providing the main fluid chamber with the connecting band integrally bridging the both side walls, the side wall of the main fluid chamber expands outward when the main fluid chamber contracts. Suppress frowning. Further, at this time, since a part of the connecting band is replaced by the mass body, the rigidity of the remaining rubber elastic portion is relatively increased, and the effect of suppressing the bulging of the side wall is further enhanced. Therefore, the volume change of the fluid chamber at the time of vibration is promoted and a high damping property is exhibited. On the other hand, the bridging direction of the connecting band is not the up-down direction but the left-right direction perpendicular to this, and part of this is replaced by the mass body, so the vibration transmissibility is kept low in combination with the damper effect. It also has high vibration absorption. Thus, both damping and vibration transmissibility act in a more favorable direction.
【０００８】[0008]
【実施例】以下、本発明の実施例を図面を参照して説明
する。図１は本発明に係る流体封入型防振装置の一部横
断面図、図２は縦断面図、図３は正面図であるが、この
流体封入型防振装置は内筒１０の外周に、間隔をあけて
設けられる二つのゴム弾性体の側壁１２と、この側壁１
２間に内筒１０の両側から左右方向に翼状に張出して一
体的に架橋される同じくゴム弾性体の隔壁１４とでこの
隔壁１４を挟んだ上下位置に外周に開口した二つの空間
１６、１８を隔成する筒体２０を上方（荷重がかかって
くる方向）に偏心させて張装する。そして、この空間１
６、１８に非圧縮性流体を封入して筒体２０の外周に外
筒２２を嵌着し、この流体封入空間１６、１８の下側の
ものを主流体室１６、上側のものを従流体室１８とする
ものである。尚、主流体室１６の下端、即ち、筒体２０
の下端には隔壁１４と同様に両側壁１２間を一体的に架
橋するゴム弾性体の架橋帯１５を残しておく。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a partial cross-sectional view of a fluid filled type vibration damping device according to the present invention, FIG. 2 is a vertical sectional view, and FIG. 3 is a front view. , Two side walls 12 of a rubber elastic body provided at intervals, and the side wall 1
Two spaces 16 and 18 opened to the upper and lower sides sandwiching this partition wall 14 with a partition wall 14 which is also made of a rubber elastic material and is integrally bridged between both sides of the inner cylinder 10 in the left-right direction. The tubular body 20 that separates is eccentric upward (in the direction in which the load is applied) and is stretched. And this space 1
An incompressible fluid is enclosed in 6 and 18 and an outer cylinder 22 is fitted around the outer periphery of a cylinder body 20, the lower one of the fluid-filled spaces 16 and 18 is the main fluid chamber 16, and the upper one is the secondary fluid. It is to be the chamber 18. The lower end of the main fluid chamber 16, that is, the cylindrical body 20
Like the partition wall 14, a cross-linking band 15 made of a rubber elastic body that integrally cross-links the side walls 12 is left at the lower end of the.
【０００９】本発明は、以上の主流体室１６内に、筒軸
に平行に両側壁１２間に一体的に架橋するゴム弾性体の
連結帯２４を設けるとともに、この連結帯２４の一部を
質量体２６で置換するのである。このような連結帯２４
を設けることにより、側壁１２に圧縮荷重がかかったと
きに、単に外方へ膨らんでへたったような状態になるの
を抑制する。又、連結帯２４の一部を質量体２６で置換
するのは、残りの連結帯２４の剛性を相対的に上げて膨
らみ抑制効果を大きくするためと、この質量体２６にダ
ンパー効果を出させるためである。従って、質量体２６
の比重やその置換量は振動数合わせのチューニング要素
として利用できる。更に、連結帯２４は主流体室１６内
に独立させて（隔壁１４や架橋帯１５と連結しなこと）
架橋するのがダンパー効果の点からも好ましい。尚、こ
の連結帯２４は内筒１０と外筒２２とが一定以上に変位
するのを規制するストッパーも兼用するから、従来のよ
うに主流体室１６内や外部にわざわざ別物体のストッパ
ーを設けるようなことをしなくてもよく、この面からの
コストダウンも可能である。According to the present invention, in the above main fluid chamber 16, a rubber elastic coupling band 24 integrally bridging between both side walls 12 is provided parallel to the cylinder axis, and a part of this coupling band 24 is provided. It is replaced by the mass body 26. Such a connecting belt 24
By providing the side wall, when a compressive load is applied to the side wall 12, it is possible to prevent the side wall 12 from bulging outward and becoming a sagging state. Further, a part of the connecting band 24 is replaced with the mass body 26 in order to relatively increase the rigidity of the remaining connecting band 24 to increase the swelling suppressing effect, and to make the mass body 26 exert a damper effect. This is because. Therefore, the mass 26
The specific gravity of and its substitution amount can be used as a tuning element for frequency matching. Further, the connecting band 24 is independent in the main fluid chamber 16 (do not connect to the partition wall 14 or the bridge band 15).
It is preferable to crosslink from the viewpoint of the damper effect. Since the connecting band 24 also serves as a stopper that restricts the inner cylinder 10 and the outer cylinder 22 from displacing beyond a certain amount, a stopper for another object is provided inside or outside the main fluid chamber 16 as in the conventional case. It is not necessary to do such a thing, and the cost can be reduced from this aspect.
【００１０】この他、隔壁１４の従流体室１８側は耐久
性を高めるために側壁１２間に亘って貫通する貫通孔２
８が設けられており、残部の中央外周部には筒体２０の
外周まで至る主塊部３０が、その両側には流体の移動を
容易にするための主流体室１６側に薄く湾曲するダイア
フラム部３２がそれぞれ形成されている。従って、従流
体室１８の底部はダイアフラム部３２で形成されている
とともに、この主塊部３０によって左右に分割されるこ
とになる。更に、筒体２０の外周側には両側壁１２の部
分で連続し、各流体室１６、１８の部分を窓状に切欠い
た補強リング３４が埋設されて補強されている。In addition to the above, the sub-fluid chamber 18 side of the partition wall 14 has a through hole 2 penetrating between the side walls 12 in order to improve durability.
8 is provided, and a main lump portion 30 reaching the outer periphery of the cylindrical body 20 is provided in the center outer peripheral portion of the remaining portion, and on both sides thereof, a diaphragm that is thinly curved toward the main fluid chamber 16 for facilitating the movement of fluid. Each part 32 is formed. Therefore, the bottom portion of the sub-fluid chamber 18 is formed by the diaphragm portion 32, and is divided into the left and right by the main mass portion 30. Further, on the outer peripheral side of the tubular body 20, a reinforcing ring 34, which is continuous with the portions of the both side walls 12 and has a window-shaped notch in the portions of the fluid chambers 16 and 18, is embedded and reinforced.
【００１１】次に、以上の主流体室１６と従流体室１８
間はオリフィス構造３６で連通され、振動によって両流
体室１６、１８の容積が変動すれば、それに伴って流体
の移動が起こるようになっている。このオリフィス構造
３６は、従流体室１８側の筒体２０の外周に主流体室１
６と二つの従流体室１８とにそれぞれ通ずるオリフィス
通路３８を外周に形成した半円状のオリフィスリング４
０を嵌着することによって行う。尚、オリフィスリング
４０は補強リング３４の中央に凹陥部４２を形成してこ
の中に嵌合するようにすれば、強固に固定されて位置ず
れ等を起こし難いし、補強リング３４、ひいては筒体２
０全体の剛性を高める。図４はオリフィスリング４０の
平面図であるが、これに形成されるオリフィス通路３８
をジグザクにしてその通路長を長くして減衰性をより高
めるとともに、主塊部３０で分割された二つの従流体室
１８相互へも通ずるようオリフィス孔４４が設けられて
いる。Next, the main fluid chamber 16 and the sub-fluid chamber 18 described above
The spaces are communicated with each other by an orifice structure 36, and when the volumes of the fluid chambers 16 and 18 are changed by vibration, the fluid is moved accordingly. The orifice structure 36 is provided on the outer periphery of the cylindrical body 20 on the side of the sub-fluid chamber 18 and the main fluid chamber 1
6 and the two sub-fluid chambers 18, respectively, a semi-circular orifice ring 4 having an orifice passage 38 formed on the outer periphery and communicating with each other.
This is done by fitting 0. If the orifice ring 40 has a concave portion 42 formed at the center of the reinforcing ring 34 and is fitted into the concave portion 42, the orifice ring 40 is firmly fixed and is unlikely to be displaced, and the reinforcing ring 34, and thus the tubular body. Two
0 Increase overall rigidity. Although FIG. 4 is a plan view of the orifice ring 40, the orifice passage 38 formed therein is shown.
An orifice hole 44 is provided so that the passage length is made longer by zigzag to further enhance the damping property and also communicates with the two sub-fluid chambers 18 divided by the main mass portion 30.
【００１２】図５、図６は本発明の他の実施例を示す横
断面図、縦断面図であるが、この例のものは、連結帯２
４を主流体室１６内で独立させるのではなく、内筒１０
側と連結させるのである。即ち、連結帯２４と隔壁１４
とを連結柱４６で上下方向に連結するのである。このよ
うにすることにより、質量体２６のダンパー効果を減殺
することなく、３方向の共振振動数のチューニング設計
の自由度を増すことができる。又、連結柱４６が存在し
ていると、連結帯２４は側壁１２の拘束効果のみを考慮
すればよいことなるから、これが存在する方向、即ち、
上下方向の耐久性を大幅にアップすることができる。FIG. 5 and FIG. 6 are a horizontal sectional view and a vertical sectional view showing another embodiment of the present invention.
4 is not independent in the main fluid chamber 16 but is instead the inner cylinder 10
Connect with the side. That is, the connecting band 24 and the partition wall 14
And are connected in the up-down direction by the connecting column 46. By doing so, it is possible to increase the degree of freedom in tuning design of the resonance frequencies in the three directions without reducing the damper effect of the mass body 26. Further, when the connecting column 46 exists, the connecting band 24 only needs to consider the restraining effect of the side wall 12, and therefore, the direction in which the connecting column 24 exists, that is,
The durability in the vertical direction can be greatly improved.
【００１３】図７、図８も本発明の他の実施例を示す横
断面図、縦断面図であるが、この例のものは連結帯２４
を外筒２２側、即ち、架橋帯１５と連結柱４８で上下方
向に連結するのである。この効果も前記した実施例の連
結柱４６を設けたものと同じである。7 and 8 are horizontal and vertical sectional views showing another embodiment of the present invention. In this example, the connecting band 24 is used.
Is connected to the outer cylinder 22 side, that is, in the vertical direction by the bridge strip 15 and the connecting column 48. This effect is also the same as that of the connection column 46 of the above-described embodiment.
【００１４】以上の構成の防振装置で自動車のエンジン
を支持するのであるが、このとき、外筒をフレームに固
定し、エンジンを内筒に対してその重量が反偏心方向か
らかかるような方向で取り付ける。これにより、エンジ
ンから発する振動がシャーシに伝達されるのを遮断し、
且つ、発生した振動を減衰できるのであるが、この場
合、次のような効果が期待できる。The engine of the automobile is supported by the vibration isolator having the above-described structure. At this time, the outer cylinder is fixed to the frame, and the weight of the engine is applied to the inner cylinder from the anti-eccentric direction. Install with. This blocks the vibrations from the engine from being transmitted to the chassis,
Moreover, the generated vibration can be damped, but in this case, the following effects can be expected.
【００１５】[0015]
【発明の効果】主流体室内に、筒軸に平行に両側壁間に
架橋する連結帯を設け、この連結帯の一部を質量体で置
換したことにより、荷重がかかったときに側壁の変形が
抑えられ、主従流体室間の流体移動量が増す。このよう
に流体移動が十分起こることによって振動エネルギーは
消費され、減衰効果が増大する。図９は筒軸に直角な上
下方向のロスファクタ（ｔａｎδ）−周波数特性である
が、これから、一部が質量体で置換された連結帯を設け
たもの（以下、本発明品という）はこのようなものがな
い従来品に比べてロスファクタが大きいことがわかる。EFFECTS OF THE INVENTION In the main fluid chamber, a connecting band that bridges between both side walls is provided in parallel with the cylinder axis, and a part of this connecting band is replaced with a mass body so that the side wall is deformed when a load is applied. Is suppressed, and the amount of fluid movement between the master and slave fluid chambers increases. Such sufficient fluid movement consumes vibrational energy and increases the damping effect. FIG. 9 shows the loss factor (tan δ) -frequency characteristic in the vertical direction perpendicular to the cylinder axis. From this, the one provided with a connecting band partially replaced with a mass body (hereinafter referred to as the product of the present invention) It can be seen that the loss factor is larger than that of the conventional product without such a thing.
【００１６】連結帯中における質量体の置換量を調整す
ることで、上下方向と左右方向及び前後方向との剛性比
を変えることができるため、従来から問題となっていた
耐久性を犠牲にすることなく、３方向の振動伝達効果を
同時に満足することが可能になる。又、剛性の変更によ
り、共振点を移動させることも可能となる。更に、この
質量体の存在は上下方向１Ｗ（エンジン分担荷重）付近
においてバネ定数を合わせたときに静的特性も向上させ
る。図１０は荷重−たわみ特性を表すものであるが、本
発明品は上下方向の荷重に対してのたわみが少なくなる
ことがわかる。このことは、耐久性を高めることにつな
がる。By adjusting the replacement amount of the mass body in the connecting band, the rigidity ratio in the up-down direction, the left-right direction, and the front-back direction can be changed, so that the durability, which has been a problem in the past, is sacrificed. It is possible to simultaneously satisfy the vibration transmission effect in the three directions. Further, it is possible to move the resonance point by changing the rigidity. Furthermore, the presence of this mass body also improves the static characteristics when the spring constants are adjusted in the vicinity of 1 W (engine shared load) in the vertical direction. FIG. 10 shows the load-deflection characteristics, but it can be seen that the product of the present invention has less deflection with respect to the vertical load. This leads to increased durability.
【００１７】本出願人が先に提案した主流体室内にゴム
弾性支柱を設けるものでは、共振点が車輛の通常走行時
の振動数である高周波数域の４００〜５００Ｈｚに出て
来るが、両側壁間に一部を質量体で置換したゴム弾性連
結帯を架橋し、この質量体を側壁から離すことにより、
これを回避することができる。図１１は上下方向の絶対
バネ定数−周波数特性を示すものであるが、本発明品の
共振点は４００〜５００Ｈｚ付近には存在しない。即
ち、振動伝達率が小さくなり、乗り心地の向上に貢献す
る。In the case where the rubber elastic column is provided in the main fluid chamber previously proposed by the applicant, the resonance point appears in the high frequency range of 400 to 500 Hz which is the frequency of the vehicle during normal running, but both sides By cross-linking the rubber elastic connecting band partly replaced with a mass between the walls and separating this mass from the side wall,
This can be avoided. FIG. 11 shows the absolute spring constant-frequency characteristics in the vertical direction, but the resonance point of the product of the present invention does not exist near 400 to 500 Hz. That is, the vibration transmissibility is reduced, which contributes to improving the riding comfort.
【００１８】更に、本発明品は、前後方向の絶対バネ定
数、即ち、振動伝達率を高周波数域で下げる。図１２は
前後方向の絶対バネ定数−周波数特性を示すものである
が、本発明品の共振点は３００〜５００Ｈｚを外れる低
周波数域に移動し、この点からも乗り心地の向上に貢献
する。以上のとおり、この流体封入型防振装置は従来に
はない小型のものであっても、本来の減衰効果をより高
め、且つ、全方向の振動伝達特性を広い周波数域に亘っ
てチューニング可能にしたものであり、ほぼ理想とする
ものを具現できたのである。Further, the product of the present invention lowers the absolute spring constant in the front-rear direction, that is, the vibration transmissibility in a high frequency range. FIG. 12 shows the absolute spring constant-frequency characteristics in the front-rear direction, but the resonance point of the product of the present invention moves to a low frequency range outside 300 to 500 Hz, which also contributes to improvement of riding comfort. As described above, even if this fluid-filled type vibration damping device is smaller than ever before, it is possible to further enhance the original damping effect and to tune the vibration transfer characteristics in all directions over a wide frequency range. I was able to realize what was almost ideal.
【図１】流体封入型防振装置の横断面図である。FIG. 1 is a cross-sectional view of a fluid filled type vibration damping device.
【図２】流体封入型防振装置の縦断面図である。FIG. 2 is a vertical cross-sectional view of a fluid filled type vibration damping device.
【図３】流体封入型防振装置の正面図である。FIG. 3 is a front view of a fluid filled type vibration damping device.
【図４】オリフィスリングの平面図である。FIG. 4 is a plan view of an orifice ring.
【図５】流体封入型防振装置の横断面図である。FIG. 5 is a cross-sectional view of the fluid filled type vibration damping device.
【図６】流体封入型防振装置の縦断面図である。FIG. 6 is a vertical sectional view of a fluid filled type vibration damping device.
【図７】流体封入型防振装置の横断面図である。FIG. 7 is a cross-sectional view of a fluid filled type vibration damping device.
【図８】流体封入型防振装置の縦断面図である。FIG. 8 is a vertical cross-sectional view of a fluid filled type vibration damping device.
【図９】上下方向のロスファクタ（ｔａｎδ）−周波数
特性である。FIG. 9 is a vertical loss factor (tan δ) -frequency characteristic.
【図１０】荷重−たわみ特性である。FIG. 10 is a load-deflection characteristic.
【図１１】上下方向の絶対バネ定数−周波数特性であ
る。FIG. 11 is an absolute spring constant-frequency characteristic in the vertical direction.
【図１２】前後方向の絶対バネ定数−周波数特性であ
る。FIG. 12 is an absolute spring constant-frequency characteristic in the front-rear direction.
【図１３】エンジンとシャーシの取付状態を示す平面図
である。FIG. 13 is a plan view showing a mounting state of the engine and the chassis.
１０ 内筒 １２ 側壁 １４ 隔壁 １６ 主流体室 １８ 従流体室 ２２ 外筒 ２４ 連結帯 ２６ 質量体 ３６ オリフィス構造 ４６ 連結柱 ４８ 連結柱 10 Inner Cylinder 12 Sidewall 14 Partition Wall 16 Main Fluid Chamber 18 Secondary Fluid Chamber 22 Outer Cylinder 24 Connection Zone 26 Mass Body 36 Orifice Structure 46 Connection Column 48 Connection Column
Claims (5)
配される内筒と外筒との間に、間隔をあけて筒軸に直角
に介装される二つのゴム弾性体の側壁と、この側壁間に
筒軸に平行に一体的に架橋される同じくゴム弾性体の隔
壁とで非圧縮性流体を封入する主流体室と従流体室とを
前記隔壁の下方と上方とに隔設し、これら主従流体室を
オリフィス構造で連通した流体封入型防振装置におい
て、前記主流体室内に、筒軸に平行に前記両側壁間を一
体的に架橋するゴム弾性体の連結帯を設け、この連結帯
の一部を質量体で置換してなる流体封入型防振装置。1. Side walls of two rubber elastic bodies interposed between an inner cylinder and an outer cylinder, which are concentric with each other or eccentric to each other in the vertical direction, and which are interposed at right angles to a cylinder axis, and the side walls. A main fluid chamber and a sub-fluid chamber for enclosing an incompressible fluid with a partition wall of a rubber elastic body integrally bridged in parallel with the cylinder axis are provided below and above the partition wall. In a fluid-filled type vibration damping device in which a main-slave fluid chamber communicates with an orifice structure, a connection band of a rubber elastic body that integrally bridges between the both side walls is provided parallel to the cylinder axis in the main fluid chamber. A fluid filled type vibration damping device in which a part of the above is replaced with a mass body.
請求項１の流体封入型防振装置。2. The fluid filled type vibration damping device according to claim 1, wherein the mass body is separated from both side walls.
連結してなる請求項１又は２の流体封入型防振装置。3. The fluid filled type vibration damping device according to claim 1, wherein the coupling band and the inner cylinder side are vertically coupled by a coupling column.
連結してなる請求項１又は２の流体封入型防振装置。4. The fluid filled type vibration damping device according to claim 1, wherein the coupling band and the outer cylinder side are coupled in the vertical direction by a coupling column.
項１又は２の流体封入型防振装置。5. The fluid filled type vibration damping device according to claim 1 or 2, wherein the connecting bands are vertically independent.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3277124A JP2631590B2 (en) | 1991-09-26 | 1991-09-26 | Fluid filled type vibration damping device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3277124A JP2631590B2 (en) | 1991-09-26 | 1991-09-26 | Fluid filled type vibration damping device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0587182A true JPH0587182A (en) | 1993-04-06 |
| JP2631590B2 JP2631590B2 (en) | 1997-07-16 |
Family
ID=17579129
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3277124A Expired - Fee Related JP2631590B2 (en) | 1991-09-26 | 1991-09-26 | Fluid filled type vibration damping device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2631590B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0530585U (en) * | 1991-09-27 | 1993-04-23 | 丸五ゴム工業株式会社 | Fluid filled anti-vibration support device |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62261730A (en) * | 1986-05-08 | 1987-11-13 | Bridgestone Corp | Vibration damping device |
| JPS643341A (en) * | 1987-06-25 | 1989-01-09 | Tokai Rubber Ind Ltd | Fluid-sealed type vibro-isolating bush |
| JPH01164831A (en) * | 1987-12-18 | 1989-06-28 | Tokai Rubber Ind Ltd | Fluid-filled type cylinder type mount |
-
1991
- 1991-09-26 JP JP3277124A patent/JP2631590B2/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62261730A (en) * | 1986-05-08 | 1987-11-13 | Bridgestone Corp | Vibration damping device |
| JPS643341A (en) * | 1987-06-25 | 1989-01-09 | Tokai Rubber Ind Ltd | Fluid-sealed type vibro-isolating bush |
| JPH01164831A (en) * | 1987-12-18 | 1989-06-28 | Tokai Rubber Ind Ltd | Fluid-filled type cylinder type mount |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0530585U (en) * | 1991-09-27 | 1993-04-23 | 丸五ゴム工業株式会社 | Fluid filled anti-vibration support device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2631590B2 (en) | 1997-07-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CA1301787C (en) | Fluid filled elastomeric damping device | |
| US4407491A (en) | Rubber bearing device having air damping capacity | |
| US4895353A (en) | Fluid filled elastomeric damping device | |
| US4420060A (en) | Engine mount arrangement | |
| US5040774A (en) | Hydraulic damping bushing | |
| JP2598969B2 (en) | Fluid-filled cylindrical mounting device | |
| JPS6216335B2 (en) | ||
| JP3425429B2 (en) | Engine-gear unit mounting | |
| JPS5947171B2 (en) | Elastic support device for vehicle engine suspension | |
| JPH03121327A (en) | Fluid sealed type cylindrical mount apparatus | |
| JP2583145B2 (en) | Fluid filled type vibration damping device | |
| JPS62224746A (en) | Fluid seal type vibrationproof supporting body | |
| US5035407A (en) | Fluid-filled power unit mount | |
| JPH0143851B2 (en) | ||
| JPH09177868A (en) | Bearing of vibrator restriction device | |
| JPH0587182A (en) | Fluid-filled vibration control device | |
| JP3547478B2 (en) | Fluid-filled anti-vibration support device | |
| JPH0226337A (en) | Inner-outer cylinder type fluid sealed vibration isolator | |
| JPH11278294A (en) | Shimmy reduction device | |
| JPS5845135Y2 (en) | engine support device | |
| JPH06207637A (en) | Liquid sealing-up type vibration proof mount | |
| JPH09273586A (en) | Vibration control device | |
| JP3599509B2 (en) | Liquid-filled anti-vibration mount | |
| JP3474249B2 (en) | Liquid-filled engine mount | |
| JPH032089B2 (en) |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090425 Year of fee payment: 12 |
|
| LAPS | Cancellation because of no payment of annual fees |