JP2592077B2 - Fluid filled type vibration damping device - Google Patents
Fluid filled type vibration damping deviceInfo
- Publication number
- JP2592077B2 JP2592077B2 JP62280447A JP28044787A JP2592077B2 JP 2592077 B2 JP2592077 B2 JP 2592077B2 JP 62280447 A JP62280447 A JP 62280447A JP 28044787 A JP28044787 A JP 28044787A JP 2592077 B2 JP2592077 B2 JP 2592077B2
- Authority
- JP
- Japan
- Prior art keywords
- liquid chamber
- orifice passage
- shaft member
- main
- rubber 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.)
- Expired - Fee Related
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
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)
Description
【発明の詳細な説明】 産業上の利用分野 この発明は、主に自動車のエンジンマウント等として
用いられる流体封入型防振装置に関する。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid filled type vibration damping device mainly used as an engine mount of an automobile.
従来の技術 エンジンマウントに好適な流体封入型防振装置とし
て、例えば特開昭56−124739号公報に記載のものが知ら
れている。これは、例えば車体側に固定される軸部材
と、これを囲んで配設され、かつ例えばエンジン側に固
定される外筒部材と、両者間に挿填されたゴム体とを有
し、上記ゴム体の内部に３個の液室が画成されていると
ともに、これらの液室を、軸部材内部のオリフィス通路
で互いに連通した構成となっている。2. Description of the Related Art As a fluid-filled type vibration damping device suitable for an engine mount, for example, a device described in Japanese Patent Application Laid-Open No. Sho 56-124739 is known. This includes, for example, a shaft member fixed to the vehicle body side, an outer cylinder member arranged around the shaft member and fixed to the engine side, for example, and a rubber body inserted therebetween. Three liquid chambers are defined inside the rubber body, and these liquid chambers are configured to communicate with each other through an orifice passage inside the shaft member.
すなわち、軸部材と外筒部材とが相対変位すると、ゴ
ム体の弾性変形に伴って各液室の溶液が変化し、これに
より各液室内に封入されたエチレングリコール等の液体
が上記オリフィス通路を通して移動する結果、単にゴム
体のみを備えた防振装置に比べて非常に大きな減衰作用
が得られるのである。That is, when the shaft member and the outer cylinder member are relatively displaced, the solution in each liquid chamber changes due to the elastic deformation of the rubber body, whereby the liquid such as ethylene glycol sealed in each liquid chamber passes through the orifice passage. As a result of the movement, an extremely large damping effect can be obtained as compared with a vibration isolator having only a rubber body.
発明が解決しようとする問題点 ところで、一般にエンジンマウントにおいては、低周
波域での振副の大きな振動に対して十分な減衰作用を果
たすべく低周波域でのロスファクタが大きいことが望ま
しく、他方、高周波の微小振動を車体側に伝達しないよ
うに、高周波域での動ばね定数が小さいことが望まし
い。すなわち、低周波域でロスファクタが大きく、かつ
高周波域で動ばね定数が小さい特性が望まれる。Problems to be Solved by the Invention By the way, in general, in an engine mount, it is desirable that the loss factor in the low frequency range is large in order to perform a sufficient damping action on large vibrations in the low frequency range. It is desirable that the dynamic spring constant in a high frequency range be small so as not to transmit high frequency minute vibrations to the vehicle body. That is, it is desired that the loss factor be large in a low frequency range and the dynamic spring constant be small in a high frequency range.
しかしながら、上記従来の流体封入型防振装置におい
ては、３個の液室が全て同一のオリフィス通路を介して
互いに連通しており、ロスファクタや動ばね定数の特性
をある一つの周波数に対してしかチューニングすること
ができない。通常は、低周波域での振動減衰特性が重視
されるため、10Hz程度の低周波数にチューニングされる
ことになり、従って、第11図に示すように、例えば100H
z以上の高周波域での動ばね定数Kdがかなり大きくなっ
てしまう。そのため、この高周波域での微小なエンジン
振動を十分に遮断できないという欠点があった。However, in the above-mentioned conventional fluid-filled type vibration damping device, all three liquid chambers communicate with each other through the same orifice passage, and the characteristics of the loss factor and the dynamic spring constant for a certain frequency. You can only tune. Usually, since the vibration damping characteristics in the low frequency range are emphasized, tuning to a low frequency of about 10 Hz is performed, and therefore, as shown in FIG.
The dynamic spring constant Kd in the high frequency range of z or more becomes considerably large. For this reason, there is a disadvantage that minute engine vibrations in the high frequency range cannot be sufficiently shut off.
問題点を解決するための手段 上記の問題点を解決するために、この発明に係る流体
封入型防振装置は、軸部材とこれを囲む外筒部材との間
に挿填されたゴム体の内部に、少なくとも３個の液室を
画成するとともに、これらの液室を個々にオリフィス通
路を介して連通させて少なくとも２つの振動系を構成
し、かつ各振動系を構成するオリフィス通路の通路断面
積および通路長で定まる等価質量を各振動系で異なる値
に設定したものである。Means for Solving the Problems In order to solve the above problems, a fluid-filled type vibration damping device according to the present invention includes a rubber member inserted between a shaft member and an outer cylinder member surrounding the shaft member. Inside, at least three liquid chambers are defined, and these liquid chambers are individually communicated via orifice passages to form at least two vibration systems, and passages of the orifice passages constituting each vibration system The equivalent mass determined by the cross-sectional area and the passage length is set to a different value for each vibration system.
すなわち、第１の発明は、軸部材とこれを囲む外筒部
材との間にゴム体が挿填されてなる液体封入型防振装置
であって、上記ゴム体の一部をなし、かつ上記軸部材と
上記外筒部材とを互いに支持するように、上記軸部材か
ら放射状に延びた一対の主弾性部と、上記ゴム体の内部
で上記主弾性部の挟角側に形成された主液室と、上記軸
部材を挟んで上記主液室と対称となる位置に設けられ、
かつゴム体を軸方向に貫通した空隙部と、上記ゴム体の
内部で上記空隙部に隣接する位置に形成された複数の副
液室と、上記主液室と一つの副液室とを連通する第１の
オリフィス通路と、主液室と他の一つの副液室とを連通
し、かつ上記第１のオリフィス通路よりも通路長が短く
通路断面積が大きい第２のオリフィス通路と、を備えて
いる。That is, a first invention is a liquid-enclosed type vibration damping device in which a rubber member is inserted between a shaft member and an outer cylindrical member surrounding the shaft member, and forms a part of the rubber member. A pair of main elastic portions radially extending from the shaft member so as to support the shaft member and the outer cylindrical member with each other; and a main liquid formed inside the rubber body on a narrow angle side of the main elastic portion. Chamber, provided at a position symmetrical with the main liquid chamber across the shaft member,
A gap that penetrates the rubber body in the axial direction, a plurality of sub liquid chambers formed at positions inside the rubber body adjacent to the gap, and the main liquid chamber and one sub liquid chamber communicate with each other. A first orifice passage, and a second orifice passage which communicates the main liquid chamber with another sub liquid chamber and has a shorter passage length and a larger passage cross-sectional area than the first orifice passage. Have.
また第２の発明は、軸部材とこれを囲む外筒部材との
間にゴム体が挿填されてなる液体封入型防振装置であっ
て、上記ゴム体の一部をなし、かつ上記軸部材と上記外
筒部材とを互いに支持するように、上記軸部材から放射
状に延びた一対の主弾性部と、同じく上記ゴム体の一部
をなし、かつ上記一対の主弾性部に挟まれた挟角側の部
分に形成された隔壁と、上記ゴム体の内部で上記主弾性
部と上記隔壁との間にそれぞれ形成された一対の主液室
と、上記軸部材を挟んで上記主液室と対称となる位置に
設けられ、かつゴム体を軸方向に貫通した空隙部と、上
記ゴム体の内部で上記隙部に隣接する位置に形成された
一対の副液室と、一つの主液室と一つの副液室とを連通
する第１のオリフィス通路と、他の主液室と他の副液室
とを連通し、かつ上記第１のオリフィス通路よりも通路
長が短く通路断面積が大きい第２のオリフィス通路と、
を備えている。Further, a second invention is a liquid-filled type vibration damping device in which a rubber member is inserted between a shaft member and an outer cylindrical member surrounding the shaft member, wherein the rubber member is a part of the rubber member, and A pair of main elastic portions radially extending from the shaft member and also form a part of the rubber body, and are sandwiched between the pair of main elastic portions so as to support the member and the outer cylinder member with each other. A partition wall formed at the included angle side, a pair of main liquid chambers respectively formed between the main elastic portion and the partition wall inside the rubber body, and the main liquid chamber sandwiching the shaft member And a pair of sub-liquid chambers formed at positions adjacent to the gap inside the rubber body, and one main liquid. A first orifice passage communicating the chamber with one sub-liquid chamber, and another main liquid chamber communicating with another sub-liquid chamber; A second orifice passage is larger cross-sectional area short passage length than the first orifice passage,
It has.
作用 一般に流体封入型防振装置は、液体の共振現象を利用
したものであり、その共振周波数はオリフィス通路の等
価質量と液室の拡張ばね定数によって定まるので、上記
のようにオリフィス通路の等価質量を異ならせることに
より、各振動系の共振周波数は異なるものとなる。In general, a fluid-filled type vibration damping device utilizes the resonance phenomenon of liquid, and its resonance frequency is determined by the equivalent mass of the orifice passage and the expansion spring constant of the liquid chamber. Are different, the resonance frequency of each vibration system is different.
すなわち、ある１つのオリフィス通路の通路断面積を
比較的小さく、かつ通路長を比較的長く設定すれば、等
価質量は大となり、その振動系は低周波域で共振する。
従って、低周波域でのロスファクタが大きく得られる。That is, if the cross-sectional area of one orifice passage is set relatively small and the passage length is set relatively long, the equivalent mass becomes large and the vibration system resonates in a low frequency range.
Therefore, a large loss factor in a low frequency range can be obtained.
また、他の１つのオリフィス通路の通路断面積を比較
的大きく、かつ通路長を比較的短く設定すれば、等価質
量は小となり、その振動系は高周波域で共振する。従っ
て、高周波域での動ばね定数が非常に小さなものとな
る。If the cross-sectional area of the other orifice passage is set relatively large and the passage length is set relatively short, the equivalent mass becomes small, and the vibration system resonates in a high frequency range. Therefore, the dynamic spring constant in a high frequency range becomes very small.
ここで、上記構成では、軸部材と外筒部材とが相対的
に変位すると、略Ｖ字形をなす主弾性部の内側に形成さ
れた主液室の容積が変化し、副液室との間で各オリフィ
ス通路を介して液体が確実に移動する。Here, in the above configuration, when the shaft member and the outer cylinder member are relatively displaced, the volume of the main liquid chamber formed inside the substantially elastic V-shaped main elastic portion changes, and the volume between the main liquid chamber and the sub liquid chamber changes. As a result, the liquid reliably moves through each orifice passage.
実施例 第１図〜第５図は、例えばエンジンマウントとして用
いられる本発明の流体封入型防振装置の一実施例を示し
ている。Embodiment FIGS. 1 to 5 show an embodiment of a fluid filled type vibration damping device of the present invention used as, for example, an engine mount.
図において、１は例えば車体側に固定される金属製の
軸部材、２はこの軸部材１を囲むように配設され、かつ
例えばエンジン側に固定される円筒状をなす金属製の外
筒部材、３は両者間に挿填されたゴム体である。In the drawing, reference numeral 1 denotes a metal shaft member fixed to, for example, a vehicle body side, and 2 denotes a cylindrical metal outer cylinder member disposed around the shaft member 1 and fixed to, for example, an engine side. Reference numeral 3 denotes a rubber body inserted between the two.
この実施例では、上記外筒部材２は、インナカラー４
とアウタカラー５と両者間に介在する中間カラー６との
三重構造となっている。そして、上記インナカラー４と
中間カラー６は互いに密に圧入固定されており、またア
ウタカラー５は、中間カラー６の外周に圧入された上
で、両端縁5aをかしめて固定してある（第２図参照）。In this embodiment, the outer cylinder member 2 is
And an outer collar 5 and an intermediate collar 6 interposed therebetween. The inner collar 4 and the intermediate collar 6 are press-fitted and fixed to each other densely, and the outer collar 5 is press-fitted to the outer periphery of the intermediate collar 6 and then caulked and fixed at both end edges 5a (the second color). 2).
上記ゴム体３は、その内周側が上記軸部材１に加硫接
着されており、かつ外周側が上記外筒部材２、詳しくは
インナカラー４に加硫接着されている。そして、このゴ
ム体３の内部に、３個の液室、つまり主液室となる第１
液室７と、副液室となる第２液室８および第３液室９が
画成されている。詳しくは、第１液室７は、ゴム体３の
下部中央に比較的大きく形成されており、また第2,第３
液室8,9は、上記第１液室７よりも容積が小さく、それ
ぞれ軸部材１の両側に対称形状に形成されていて、第１
液室７と第2,第３液室8,9との間に、逆Ｖ字形の主弾性
部3aが残るようにしてある。つまり、上記軸部材１は主
に上記主弾性部3aを介して外筒部材２に支持されるので
あり、エンジンの荷重が作用した状態で軸部材１と外筒
部材２とがちょうど同心状となるように構成されてい
る。また、上記ゴム体３の上部には、円弧状に空隙部10
が貫通形成されている。なお、11は上記ゴム体３の中心
部分を補強するとともに、過大な変位を阻止すべくゴム
体３内に埋設された金属製のストッパである。The rubber body 3 has an inner peripheral side vulcanized and bonded to the shaft member 1 and an outer peripheral side vulcanized and bonded to the outer cylindrical member 2, specifically, the inner collar 4. Then, inside the rubber body 3, three liquid chambers, that is, a first liquid chamber serving as a main liquid chamber is provided.
A liquid chamber 7 and a second liquid chamber 8 and a third liquid chamber 9 serving as sub liquid chambers are defined. More specifically, the first liquid chamber 7 is formed relatively large in the center of the lower part of the rubber body 3 and the second and third liquid chambers 7 are formed.
The liquid chambers 8 and 9 have a smaller volume than the first liquid chamber 7 and are formed symmetrically on both sides of the shaft member 1, respectively.
An inverted V-shaped main elastic portion 3a remains between the liquid chamber 7 and the second and third liquid chambers 8,9. That is, the shaft member 1 is mainly supported by the outer cylinder member 2 via the main elastic portion 3a. When the load of the engine is applied, the shaft member 1 and the outer cylinder member 2 are exactly concentric. It is configured to be. In the upper part of the rubber body 3, a gap 10 is formed in an arc shape.
Are formed through. Reference numeral 11 denotes a metal stopper embedded in the rubber body 3 to reinforce the center portion of the rubber body 3 and prevent excessive displacement.
一方、上記インナカラー４においては、第５図に示す
ように、各液室7,8,9に対応する部分が矩形の窓状に開
口形成されている。つまり、この各液室7,8,9の部分で
は、側端部4aのみが帯状に残されている（第２図参
照）。そして、上記インナカラー４の外周に嵌合する中
間カラー６の外周面に、第１オリフィス通路12と第２オ
リフィス通路13とが凹設されている。On the other hand, in the inner collar 4, as shown in FIG. 5, portions corresponding to the respective liquid chambers 7, 8, and 9 are formed as rectangular windows. That is, in the liquid chambers 7, 8, and 9, only the side end 4a is left in a band shape (see FIG. 2). A first orifice passage 12 and a second orifice passage 13 are recessed on the outer peripheral surface of the intermediate collar 6 fitted on the outer periphery of the inner collar 4.
上記第１オリフィス通路12は、第１図に示すように、
中間カラー６の略全周近くに亘って形成され、つまり通
路長が十分に長く形成されており、一端が開口部14を介
して第１液室７に連通し、かつ他端が開口部15を介して
第２液室８に連通している。そして、この第１液室７と
第２液室８とを連通した第１オリフィス通路12は、第２
図に示すように、その通路断面積が比較的小さく設定さ
れている。なお、上記開口部14,15は、上記第１オリフ
ィス通路12の通路長が最も長くなるように、それぞれ第
１液室7,第２液室８の端部に開口している。従って、上
記第１オリフィス通路12の等価質量は非常に大きなもの
となる。The first orifice passage 12, as shown in FIG.
The intermediate collar 6 is formed substantially all around the circumference, that is, the passage length is formed sufficiently long. One end communicates with the first liquid chamber 7 through the opening 14, and the other end has the opening 15. Through the second liquid chamber 8. The first orifice passage 12 communicating the first liquid chamber 7 and the second liquid chamber 8 is
As shown in the figure, the cross-sectional area of the passage is set relatively small. The openings 14 and 15 are opened at the ends of the first liquid chamber 7 and the second liquid chamber 8, respectively, so that the path length of the first orifice path 12 is the longest. Therefore, the equivalent mass of the first orifice passage 12 becomes very large.
また上記第２オリフィス通路13は、第３図に示すよう
に、第１液室７と第３液室９とを直接につなぐ形に、つ
まり通路長が短く形成されており、一端が開口部16を介
して第１液室７に連通し、かつ他端が開口部17を介して
第３液室９に連通している。そして、第４図に示すよう
に、この第２オリフィス通路13は広い幅に形成されてお
り、つまりその通路断面積が比較的大きく設定されてい
る。なお、上記開口部16,17は、上記第２オリフィス通
路13が最も短くなるような位置に開口している。従っ
て、上記第２オリフィス通路13の等価質量は非常に小さ
なものとなる。As shown in FIG. 3, the second orifice passage 13 is formed so as to directly connect the first liquid chamber 7 and the third liquid chamber 9, that is, has a short passage length. The other end communicates with the third liquid chamber 9 through the opening 17. As shown in FIG. 4, the second orifice passage 13 is formed to have a wide width, that is, the passage cross-sectional area is set to be relatively large. The openings 16 and 17 are opened at positions where the second orifice passage 13 is the shortest. Therefore, the equivalent mass of the second orifice passage 13 is very small.
上記のように第１オリフィス通路12,第２オリフィス1
3によって連通された各液室7,8,9の内部には、適宜な粘
度、例えば200CP程度のエチレングリコール等が密に充
填されている。As described above, the first orifice passage 12 and the second orifice 1
The interior of each of the liquid chambers 7, 8, and 9 communicated by 3 is densely filled with an appropriate viscosity, for example, about 200 CP of ethylene glycol or the like.
さて上記のように構成された流体封入型防振装置にお
いては、軸部材１が外筒部材２に対し相対変位すると、
各液室7,8,9内の容積が変化し、第１液室７と第２液室
８との間、および第１液室７と第３液室９との間で液体
が移動する。このとき、第１液室７と第２液室８とは、
等価質量が大きいオリフィス通路つまり通路断面積が小
さく、かつ通路長が長い第１オリフィス通路12で連通さ
れているため、低周波域で共振して第１オリフィス通路
12内を多量の液体が通過する。従って、第12図の破線に
示すように、10Hz前後の低周波域で非常に大きなロスフ
ァクタｌが得られ、エンジンの大振幅の振動を効果的に
抑制できる。Now, in the fluid filled type vibration damping device configured as described above, when the shaft member 1 is relatively displaced with respect to the outer cylinder member 2,
The volume in each of the liquid chambers 7, 8, 9 changes, and the liquid moves between the first liquid chamber 7 and the second liquid chamber 8, and between the first liquid chamber 7 and the third liquid chamber 9. . At this time, the first liquid chamber 7 and the second liquid chamber 8
Since the orifice passage having a large equivalent mass, that is, the first orifice passage 12 having a small passage cross-sectional area and a long passage length communicates with each other, the first orifice passage resonates in a low frequency range.
A large amount of liquid passes through 12. Accordingly, as shown by the broken line in FIG. 12, a very large loss factor 1 is obtained in a low frequency range of about 10 Hz, and large-amplitude vibration of the engine can be effectively suppressed.
一方、第１液室７と第３液室９とは、等価質量が小さ
なオリフィス通路つまり通路断面積が大きく、かつ通路
長が短い第２オリフィス通路13で連通されているため、
高周波域で共振して第２オリフィス通路13内を多量の液
体が通過する。従って、第12図の実線に示すように、高
周波域での動ばね定数Kdを小さなものとすることがで
き、車体への微小振動の伝達を効果的に阻止できる。な
お、第12図の例では、高周波側のピークが200Hz前後に
チューニングされているが、これは第２オリフィス通路
13の通路断面積や通路長によって適宜変更し得るのは勿
論である。On the other hand, the first liquid chamber 7 and the third liquid chamber 9 communicate with each other through the orifice passage having a small equivalent mass, that is, the second orifice passage 13 having a large passage cross-sectional area and a short passage length.
A large amount of liquid passes through the second orifice passage 13 while resonating in a high frequency range. Therefore, as shown by the solid line in FIG. 12, the dynamic spring constant Kd in the high frequency range can be reduced, and the transmission of minute vibration to the vehicle body can be effectively prevented. In the example of FIG. 12, the peak on the high frequency side is tuned to around 200 Hz.
Needless to say, it can be appropriately changed according to the passage sectional area and the passage length of the thirteenth passage.
因みに、上記実施例においては、第１オリフィス通路
12の断面積は7mm2、長さは150mm程度に設定されてお
り、また第２オリフィス通路13の断面積は50mm2、長さ
は15mm程度に設定されている。Incidentally, in the above embodiment, the first orifice passage
The sectional area of 12 is set to about 7 mm 2 and the length is set to about 150 mm, and the sectional area of the second orifice passage 13 is set to about 50 mm 2 and the length is set to about 15 mm.
第10図は、上述した作用の理解を助けるために、上記
流入封入型防振装置の振動系をモデル化して示したもの
である。ここで、ｋはゴム体３のばね定数、k1は第１液
室７の拡張ばね定数、k2は第２液室８および第３液室９
の拡張ばね定数を示している。FIG. 10 shows a model of a vibration system of the inflow-enclosed type vibration damping device in order to facilitate understanding of the above-mentioned operation. Here, k is the spring constant of the rubber body 3, k 1 extended spring constant of the first fluid chamber 7, k 2 is the second liquid chamber 8 and the third liquid chamber 9
2 shows the extended spring constant of the.
次に、第６図〜第９図は、この発明に係る流体封入型
防振装置の異なる実施例を示している。この実施例は、
外筒部材２がインナカラー４とアウタカラー18との二重
構造となっており、両者は密に圧入されて互いに固定さ
れている。そして、上記アウタカラー18の内周面に第１
オリフィス通路19および第２オリフィス通路20が凹設さ
れている。6 to 9 show different embodiments of the fluid filled type vibration damping device according to the present invention. This example is
The outer cylinder member 2 has a double structure of an inner collar 4 and an outer collar 18, both of which are pressed tightly and fixed to each other. Then, the first inner surface of the outer collar 18 is
An orifice passage 19 and a second orifice passage 20 are recessed.
第１液室７と第２液室８とを連通する第１オリフィス
通路19は、やはり通路断面積が比較的小さく設定され
（第７図参照）、かつ通路長を長く確保すべくアウタカ
ラー18を略一周するように形成されているもので、特に
第７図に示すように、インナカラー４の帯状の側端部4a
によって覆われ得る位置に形成されている。そして、そ
の両端部に、アウタカラー18の軸方向に折曲した折曲部
21,22が設けられており、該折曲部21,22を介して第１液
室７および第２液室８にそれぞれ連通している。The first orifice passage 19 communicating the first liquid chamber 7 and the second liquid chamber 8 also has a relatively small passage cross-sectional area (see FIG. 7), and has an outer collar 18 for ensuring a long passage length. Is formed so as to make substantially one round. Particularly, as shown in FIG. 7, the band-shaped side end 4a of the inner collar 4 is formed.
It is formed in a position that can be covered by And, at both ends, a bent portion bent in the axial direction of the outer collar 18
21 and 22 are provided, and communicate with the first liquid chamber 7 and the second liquid chamber 8 via the bent portions 21 and 22, respectively.
また、第１液室７と第３液室９とを連通する第２オリ
フィス通路20は、インナカラー４の第１液室7,第３液室
９に対応した窓状開口部と両端が一部ラップするように
形成されており、この結果、液室7,9内に露出した端部2
0a,20bを介して第１液室７および第３液室９にそれぞれ
連通している。なお、上記第２オリフィス通路20は、第
９図に示すように、十分に大きな通路断面積を有してい
る。The second orifice passage 20 communicating the first liquid chamber 7 and the third liquid chamber 9 has a window-shaped opening corresponding to the first liquid chamber 7 and the third liquid chamber 9 of the inner collar 4 at one end. End portions 2 exposed in the liquid chambers 7, 9 as a result.
The first and third liquid chambers 7 and 9 communicate with each other via 0a and 20b. The second orifice passage 20 has a sufficiently large passage cross-sectional area as shown in FIG.
この実施例では、アウタカラー18に対する第１オリフ
ィス通路19,第２オリフィス20の溝加工が若干面倒にな
るものの、外筒部材２が二重構造となり、部品点数を削
減できる利点がある。In this embodiment, although the groove processing of the first orifice passage 19 and the second orifice 20 with respect to the outer collar 18 is slightly complicated, there is an advantage that the outer cylinder member 2 has a double structure and the number of parts can be reduced.
次に、第13図に示す実施例は、ゴム体３内部に４個の
液室を画成した実施例を示している。すなわち、逆Ｖ字
形をなす主弾性部3aの下部に、略垂直な隔壁23を挟んで
第１液室24と第２液室25とが対称形状に形成されている
とともに、主弾性部3aの上部に、第３液室26と第４液室
27とが対称形状に形成されている。そして、主液室とな
る第１液室24と副液室となる第３液室26とが細くかつ長
い第１オリフィス通路28を介して連通しており、かつ主
液室となる第２液室25と副液室となる第４液室27とが太
くかつ短い第２オリフィス通路29を介して連通してい
る。Next, the embodiment shown in FIG. 13 shows an embodiment in which four liquid chambers are defined inside the rubber body 3. That is, the first liquid chamber 24 and the second liquid chamber 25 are formed symmetrically with the substantially vertical partition wall 23 interposed therebetween under the inverted V-shaped main elastic part 3a. Above the third liquid chamber 26 and the fourth liquid chamber
27 are formed symmetrically. A first liquid chamber 24 serving as a main liquid chamber and a third liquid chamber 26 serving as a sub liquid chamber communicate with each other through a thin and long first orifice passage 28, and a second liquid chamber serving as a main liquid chamber is provided. The chamber 25 and a fourth liquid chamber 27 serving as a sub liquid chamber communicate with each other through a thick and short second orifice passage 29.
従って、上記実施例では、第１液室24と第３液室26と
第１オリフィス通路28とによって一方の振動系が構成さ
れ、かつ第２液室25と第４液室27と第２オリフィス通路
29とによって他方の振動系が構成される。そして、第１
オリフィス通路28の等価質量が第２オリフィス通路29の
等価質量よりも大となり、この結果、第１オリフィス通
路28側の振動系が比較的低周波域で共振し、かつ第２オ
リフィス通路29側の振動系が比較的高周波域で共振する
ことになる。Therefore, in the above embodiment, one of the vibration systems is constituted by the first liquid chamber 24, the third liquid chamber 26, and the first orifice passage 28, and the second liquid chamber 25, the fourth liquid chamber 27, and the second orifice aisle
29 constitutes the other vibration system. And the first
The equivalent mass of the orifice passage 28 becomes larger than the equivalent mass of the second orifice passage 29. As a result, the vibration system of the first orifice passage 28 resonates in a relatively low frequency range and the equivalent mass of the second orifice passage 29 The vibration system resonates in a relatively high frequency range.
なお、上記のように多数の液室を備えたものにおいて
は、各液室の連通の態様を変えることで種々の組み合わ
せが可能である。In the case where a large number of liquid chambers are provided as described above, various combinations are possible by changing the communication mode of each liquid chamber.
発明の効果 以上の説明で明らかなように、この発明に係る流体封
入型防振装置によれば、低周波域でのロスファクタを十
分に大きく確保できると同時に、高周波域での動ばね定
数を小さく抑制することができる。従って、低周波域に
チューニングした従来の防振装置に比べて、高周波振動
を一層効果的に遮断でき、例えばエンジンマウントとし
てエンジン振動に起因する騒音の低減が図れる。特に、
主液室が略Ｖ字形をなす主弾性部の挟角側に配置され、
その対称位置に空隙部が位置するので、入力に対し主液
室が確実に容積変化し、液柱振動による振動抑制作用が
一層良好に得られる。As is clear from the above description, according to the fluid-filled type vibration damping device of the present invention, a sufficiently large loss factor in a low frequency range can be ensured, and a dynamic spring constant in a high frequency range can be reduced. It can be suppressed small. Therefore, compared to a conventional vibration isolator tuned to a low frequency range, high frequency vibration can be more effectively cut off, and noise caused by engine vibration can be reduced, for example, as an engine mount. Especially,
The main liquid chamber is arranged on the narrow angle side of the main elastic portion having a substantially V shape,
Since the gap is located at the symmetrical position, the volume of the main liquid chamber is reliably changed with respect to the input, and the vibration suppressing action by the liquid column vibration can be more favorably obtained.
第１図〜第４図はこの発明に係る流体封入型防振装置の
一実施例を示す断面図であって、第１図は第２図のＩ−
Ｉ線に沿った断面図、第２図は第１図のII−II線に沿っ
た断面図、第３図は第２図のIII−III線に沿った要部の
みの断面図、第４図は第３図のIV−IV線に沿った要部の
みの断面図、第５図はこの実施例の分解斜視図、第６図
〜第９図はこの発明の異なる実施例を示す断面図であっ
て、第６図は第７図のVI−VI線に沿った断面図、第７図
は第６図のVII−VII線に沿った断面図、第８図は第７図
のVIII−VIII線に沿った断面図、第９図は第６図のIX−
IX線に沿った要部のみの断面図、第10図はこの発明の流
体封入型防振装置の振動モデルを示す説明図、第11図は
従来における流体封入型防振装置の周波数特性図、第12
図はこの発明に係る流体封入型防振装置の周波数特性
図、第13図は４個の液室を備えた実施例を示す断面図で
ある。 １……軸部材、２……外筒部材、３……ゴム体、７……
第１液室、８……第２液室、９……第３液室、12……第
１オリフィス通路、13……第２オリフィス通路。1 to 4 are cross-sectional views showing one embodiment of a fluid-filled type vibration damping device according to the present invention, and FIG.
FIG. 2 is a sectional view taken along line II-II in FIG. 1, FIG. 3 is a sectional view taken along line III-III in FIG. 2, and FIG. FIG. 5 is a cross-sectional view of only essential parts taken along line IV-IV in FIG. 3, FIG. 5 is an exploded perspective view of this embodiment, and FIGS. 6 to 9 are cross-sectional views showing different embodiments of the present invention. 6 is a sectional view taken along line VI-VI of FIG. 7, FIG. 7 is a sectional view taken along line VII-VII of FIG. 6, and FIG. FIG. 9 is a cross-sectional view along the line VIII, FIG.
FIG. 10 is a cross-sectional view of only the main part along the line IX, FIG. 10 is an explanatory diagram showing a vibration model of the fluid-filled type vibration damping device of the present invention, FIG. 11 is a frequency characteristic diagram of the conventional fluid-filled type vibration damping device, Twelfth
FIG. 13 is a frequency characteristic diagram of the fluid filled type vibration damping device according to the present invention, and FIG. 13 is a sectional view showing an embodiment having four liquid chambers. 1 ... shaft member, 2 ... outer cylinder member, 3 ... rubber body, 7 ...
First liquid chamber, 8 second liquid chamber, 9 third liquid chamber, 12 first orifice passage, 13 second orifice passage.
Claims (2)
体が挿填されてなる液体封入型防振装置であって、 上記ゴム体の一部をなし、かつ上記軸部材と上記外筒部
材とを互いに支持するように、上記軸部材から放射状に
延びた一対の主弾性部と、 上記ゴム体の内部で上記主弾性部の挟角側に形成された
主液室と、 上記軸部材を挟んで上記主液室と対称となる位置に設け
られ、かつゴム体を軸方向に貫通した空隙部と、 上記ゴム体の内部で上記空隙部に隣接する位置に形成さ
れた複数の副液室と、 上記主液室と一つの副液室とを連通する第１のオリフィ
ス通路と、 主液室と他の一つの副液室とを連通し、かつ上記第１の
オリフィス通路よりも通路長が短く通路断面積が大きい
第２のオリフィス通路と、 を備えていることを特徴とする液体封入型防振装置。1. A liquid-filled type vibration damping device comprising a rubber member inserted between a shaft member and an outer cylinder member surrounding the shaft member, wherein the liquid member forms a part of the rubber member, and A pair of main elastic portions radially extending from the shaft member so as to support the outer cylindrical member with each other, and a main liquid chamber formed on the narrow side of the main elastic portion inside the rubber body. A void portion provided at a position symmetrical to the main liquid chamber with the shaft member interposed therebetween and penetrating the rubber body in the axial direction, and a plurality of voids formed at positions inside the rubber body adjacent to the void portion A first orifice passage communicating between the main liquid chamber and one sub liquid chamber; a first orifice passage communicating with the main liquid chamber and another sub liquid chamber; A second orifice passage having a shorter passage length and a larger passage cross-sectional area than the second orifice passage. Input type vibration isolator.
体が挿填されてなる液体封入型防振装置であって、 上記ゴム体の一部をなし、かつ上記軸部材と上記外筒部
材とを互いに支持するように、上記軸部材から放射状に
延びた一対の主弾性部と、 同じく上記ゴム体の一部をなし、かつ上記一対の主弾性
部に挟まれた挟角側の部分に形成された隔壁と、 上記ゴム体の内部で上記主弾性部と上記隔壁との間にそ
れぞれ形成された一対の主液室と、 上記軸部材を挟んで上記主液室と対称となる位置に設け
られ、かつゴム体を軸方向に貫通した空隙部と、 上記ゴム体の内部で上記隙部に隣接する位置に形成され
た一対の副液室と、 一つの主液室と一つの副液室とを連通する第１のオリフ
ィス通路と、 他の主液室と他の副液室とを連通し、かつ上記第１のオ
リフィス通路よりも通路長が短く通路断面積が大きい第
２のオリフィス通路と、 を備えていることを特徴とする液体封入型防振装置。2. A liquid-filled type vibration damping device comprising a rubber member inserted between a shaft member and an outer cylindrical member surrounding the shaft member. A pair of main elastic portions extending radially from the shaft member so as to support the outer cylinder member with each other, and an included angle which also forms a part of the rubber body and is interposed between the pair of main elastic portions. A partition formed on the side portion; a pair of main liquid chambers formed between the main elastic portion and the partition inside the rubber body; and a symmetrical shape with the main liquid chamber across the shaft member. And a gap portion penetrating the rubber body in the axial direction, a pair of sub-liquid chambers formed at a position adjacent to the gap inside the rubber body, and one main liquid chamber. A first orifice passage communicating with one sub-liquid chamber, and another main liquid chamber communicating with another sub-liquid chamber; A second orifice passage having a shorter passage length than the first orifice passage and a larger passage cross-sectional area;
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62280447A JP2592077B2 (en) | 1987-11-06 | 1987-11-06 | Fluid filled type vibration damping device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62280447A JP2592077B2 (en) | 1987-11-06 | 1987-11-06 | Fluid filled type vibration damping device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01126451A JPH01126451A (en) | 1989-05-18 |
| JP2592077B2 true JP2592077B2 (en) | 1997-03-19 |
Family
ID=17625184
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62280447A Expired - Fee Related JP2592077B2 (en) | 1987-11-06 | 1987-11-06 | Fluid filled type vibration damping device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2592077B2 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2878286B2 (en) * | 1988-08-02 | 1999-04-05 | 株式会社ブリヂストン | Anti-vibration device |
| JPH02124338U (en) * | 1989-03-23 | 1990-10-12 | ||
| JPH03121327A (en) * | 1989-10-02 | 1991-05-23 | Tokai Rubber Ind Ltd | Fluid sealed type cylindrical mount apparatus |
| JP2616064B2 (en) * | 1989-11-29 | 1997-06-04 | 日産自動車株式会社 | Fluid-filled power unit mount |
| JP2583145B2 (en) * | 1990-05-22 | 1997-02-19 | 丸五ゴム工業株式会社 | Fluid filled type vibration damping device |
| DE4137977C2 (en) * | 1991-11-19 | 1995-06-14 | Freudenberg Carl Fa | Multi-chamber hydraulic bush |
| JP3662045B2 (en) * | 1995-03-15 | 2005-06-22 | 日産自動車株式会社 | Vehicle engine test pallet and test bench |
| DE102016001507B4 (en) * | 2016-02-10 | 2020-06-18 | Anvis Deutschland Gmbh | Vibration damper |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0615894B2 (en) * | 1985-02-22 | 1994-03-02 | 日産自動車株式会社 | How to set resonance frequency of liquid in orifice of liquid-filled type vibration isolator |
| JPS6256643A (en) * | 1985-09-04 | 1987-03-12 | Nissan Motor Co Ltd | Vibropreventive element with liquid encapsulated |
| JPS6288834A (en) * | 1985-10-15 | 1987-04-23 | Bridgestone Corp | Vibro-isolator |
| JPS63111335A (en) * | 1986-10-28 | 1988-05-16 | Tokai Rubber Ind Ltd | Cylindrical fluid-sealed type mounting device |
| JPS643342A (en) * | 1987-06-25 | 1989-01-09 | Tokai Rubber Ind Ltd | Fluid-sealed type cylindrical mount device |
| JPH0643555Y2 (en) * | 1987-10-27 | 1994-11-14 | 東海ゴム工業株式会社 | Fluid-filled cylindrical mount device |
-
1987
- 1987-11-06 JP JP62280447A patent/JP2592077B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH01126451A (en) | 1989-05-18 |
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