JP2860701B2 - Liquid filled vibration isolator - Google Patents
Liquid filled vibration isolatorInfo
- Publication number
- JP2860701B2 JP2860701B2 JP25791490A JP25791490A JP2860701B2 JP 2860701 B2 JP2860701 B2 JP 2860701B2 JP 25791490 A JP25791490 A JP 25791490A JP 25791490 A JP25791490 A JP 25791490A JP 2860701 B2 JP2860701 B2 JP 2860701B2
- Authority
- JP
- Japan
- Prior art keywords
- liquid
- vibration
- vibration isolator
- antifreeze
- liquid chamber
- 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
Landscapes
- Combined Devices Of Dampers And Springs (AREA)
Description
【発明の詳細な説明】 ［産業上の利用分野］ 本発明は液封入防振装置に関し、特に入力振動の振幅
に応じて特性を変更して広い範囲の振動伝達を効果的に
防止する液封入防振装置に関する。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a liquid-filled vibration isolator, and more particularly to a liquid-filled vibration-proof device whose characteristics are changed according to the amplitude of input vibration to effectively prevent a wide range of vibration transmission. It relates to a vibration isolator.
［従来の技術］ 液封入防振装置は振動体を支持する防振ゴム体内に一
対の液室を形成し、絞り流路を介して両液室間に密封液
を流通せしめることにより効果的な振動減衰をなすもの
である。かかる液封入防振装置を車両のエンジマウント
に使用する場合、エンジンからは車両の運転状態に応じ
て種々の振動が入力し、これら入力振動を効果的に低減
するためには振動の種類に応じて装置の動バネ定数や減
衰係数を最適に選択する必要がある。[Prior Art] A liquid-filled vibration isolator is effective by forming a pair of liquid chambers in a vibration-isolating rubber body that supports a vibrating body and allowing a sealed liquid to flow between the two liquid chambers through a throttle channel. Vibration damping is performed. When such a liquid-filled vibration isolator is used for an engine mount of a vehicle, various vibrations are input from the engine according to the driving state of the vehicle. Therefore, it is necessary to optimally select the dynamic spring constant and the damping coefficient of the device.
［発明が解決しようとする課題］ 入力振動に応じて装置特性を変更する方法として、従
来、液室を区画する仕切壁の一部を可動壁とするもの、
異なる長さの絞り流路を選択開閉するもの等があるが、
いずれも機械的差動部を必要とするため装置構造が複雑
化するという問題がある。[Problems to be Solved by the Invention] As a method of changing the device characteristics according to the input vibration, a method in which a part of a partition wall that partitions a liquid chamber is a movable wall,
There are ones that selectively open and close throttle paths of different lengths,
All of them require a mechanical differential section, and thus have a problem that the device structure is complicated.
本発明はかかる課題を解決するもので、装置構造を複
雑化することなく装置特性の変更が可能で、種々の入力
振動を効果的に低減せしめる液封入防振装置を提供する
ことを目的とする。An object of the present invention is to provide a liquid filled vibration isolator that can change device characteristics without complicating the device structure and effectively reduce various input vibrations. .
［課題を解決するための手段］ 本発明の構成を説明すると、液封入防振装置は、振動
体を支持する防振ゴム体１内に密閉空間を形成して液L
1、L2を封入するとともに、該密閉空間内を、絞り流路2
1を形成した仕切壁２で一対の液室Ａ、Ｂに区画し、か
つ上記封入液L1、L2を、比重が異なり互いに相液性のな
い二種以上の液L1、L2で構成したものである。[Means for Solving the Problems] The configuration of the present invention will be described. The liquid-filled vibration isolator forms a closed space in a vibration-isolating rubber body 1 that supports a vibrating body.
1, while enclosing L2, the inside of the closed space is
The partition walls 2 forming 1 form a pair of liquid chambers A and B, and the sealed liquids L1 and L2 are composed of two or more liquids L1 and L2 having different specific gravities and incompatible with each other. is there.
［作用］ 上記構成の防振装置において、二種以上の密封液L1、
L2は比重の小さいものL1が上方へ、比重の大きいものL2
が下方へそれぞれ移動する。これら密封液のうち一種L2
が絞り流路21付近にあるように液量を設定すれば、小振
幅振動の入力時には液室Ａの変形による液の移動量は少
ないため、絞り流路21には上記一種の液L2のみが流通
し、この液の特性により装置特性が決定される。[Operation] In the vibration isolator of the above configuration, two or more sealing liquids L1,
L2 with low specific gravity L1 goes up, L2 with high specific gravity
Move downward respectively. One of these sealing liquids L2
If the amount of liquid is set so that the liquid is in the vicinity of the throttle channel 21, the amount of movement of the liquid due to the deformation of the liquid chamber A is small at the time of inputting the small amplitude vibration. It circulates, and the characteristics of the liquid determine the device characteristics.
大振幅振動の入力時には液室Ａは大きく変形し、液の
移動量が増加して、絞り流路21には上記一種の液L2に続
いて他の種類の液L1も流通し、この液L1の特性が異なる
ことにより装置特性が変更される。When a large amplitude vibration is input, the liquid chamber A is greatly deformed, and the amount of movement of the liquid increases, so that another liquid L1 flows through the throttle channel 21 in addition to the above-described liquid L2. Are different, the device characteristics are changed.
かくして、何等機械的作動部を有することなく、振動
振幅に応じた最適な装置特性に切り替えられて効果的な
振動低減作用がなされる。Thus, without any mechanical operating portion, the device characteristics are switched to the optimum device characteristics according to the vibration amplitude, and an effective vibration reduction action is performed.
［第１実施例］ 第１図において、防振ゴム体１は下方へ拡径する厚肉
の筒状をなし、その上方開口は下方へ山形に突出する頂
板４により閉鎖されている。防振ゴム体１の下方開口縁
には筒状側板５の上端部が接合され、該側板５内には仕
切壁２が挿入嵌着された防振ゴム体１の下方開口を閉鎖
し、その上方に主液室Ａが形成されている。仕切壁２の
下方にはこれに沿って薄肉のゴムシート３が配設され、
その外周縁は上記仕切壁２の外周下面に密接してその下
方に副液室Ｂを形成している。First Embodiment In FIG. 1, a vibration-proof rubber body 1 has a thick cylindrical shape whose diameter increases downward, and its upper opening is closed by a top plate 4 projecting downward in a mountain shape. The upper end of the cylindrical side plate 5 is joined to the lower opening edge of the vibration-proof rubber body 1, and the lower opening of the vibration-proof rubber body 1 in which the partition wall 2 is inserted and fitted in the side plate 5 is closed. A main liquid chamber A is formed above. A thin rubber sheet 3 is disposed below the partition wall 2 along the partition wall 2,
The outer peripheral edge is in close contact with the outer peripheral lower surface of the partition wall 2 to form a sub-liquid chamber B therebelow.
上記仕切壁２には外周に絞り流路21が形成されて上下
の主液室Ａと副液室Ｂとを連通しており、連通する両液
室Ａ、Ｂ内には二種の液体L1、L2が封入されている。す
なわち、封入液L1、L2の一方はシリコーン油であり、他
方はエチレングリコールを主体とする不凍液である。不
凍液L2の比重が1.1であるのに対して、シリコーン油L1
のそれは0.98であり、これらを混入するとシリコーン油
L1は不凍液L2の上方へ移動する。しかして、両者の割合
いを調節すると、図示の如く、仕切壁２の上方の主液室
Ａ内まで不凍液L2が入り込んで、主液室Ａ内に液の境界
R1ができる。ここで、上記シリコーン油L1の動粘度は不
凍液L2よりも大きい200cst程のものを使用する。A throttle channel 21 is formed on the outer periphery of the partition wall 2 to communicate the upper and lower main liquid chambers A and the sub liquid chambers B, and two liquid chambers A and B communicate with each other. , L2 are enclosed. That is, one of the sealed liquids L1 and L2 is a silicone oil, and the other is an antifreeze mainly composed of ethylene glycol. While the specific gravity of antifreeze L2 is 1.1, silicone oil L1
It is 0.98.
L1 moves above the antifreeze L2. When the ratio of the two is adjusted, the antifreeze L2 enters the main liquid chamber A above the partition wall 2 as shown in the figure, and the boundary of the liquid enters the main liquid chamber A.
R1 is possible. Here, the kinematic viscosity of the silicone oil L1 is about 200 cst larger than that of the antifreeze L2.
上記防振装置は、ゴムシート３の下方に配設されて側
板５の下端部に結合された底板６のボルトにより車両フ
レームに固定され、エンジンは防振ゴム体１の頂部に接
合された上板７にボルト固定される。The vibration isolator is fixed to a vehicle frame by a bolt of a bottom plate 6 disposed below the rubber sheet 3 and connected to a lower end of the side plate 5, and the engine is joined to the top of the rubber vibration insulator 1. It is bolted to the plate 7.
防振装置にエンジン振動が入力すると、防振ゴム体１
の変形に伴い主液室Ａの容積が変化し、密封液が絞り流
路21を経て流通して振動減衰力を生じるとともに、主液
室Ａの内圧が増大して大きなバネ力を生じる。この場合
の装置の動バネ定数は、絞り流路21を通過する液の粘
性、比重等の特性により第２図に示す如き周波数特性を
示す。図中線ｗ、ｘ、ｙ、ｚはこの順に粘度が大きくな
っており、粘度が小さい場合には動バネ定数に低周波側
で小、高周波側で大となる極値が現れ、粘度が小さくな
るにつれて極値の絶対値は小さくなる。When the engine vibration is input to the vibration isolator, the vibration isolating rubber body 1
With the deformation, the volume of the main liquid chamber A changes, and the sealing liquid flows through the throttle channel 21 to generate a vibration damping force, and the internal pressure of the main liquid chamber A increases to generate a large spring force. In this case, the dynamic spring constant of the device exhibits frequency characteristics as shown in FIG. 2 due to characteristics such as viscosity and specific gravity of the liquid passing through the throttle channel 21. The lines w, x, y, and z in the figure show that the viscosity increases in this order. When the viscosity is small, the dynamic spring constant has an extreme value that is small on the low frequency side and large on the high frequency side, and the viscosity is small. The absolute value of the extremum becomes smaller as it becomes.
さて、比較的振幅の小さいシェイク振動が入力する場
合には、防振ゴム体１の変形量は小さく、したがって主
液室Ａの容積変化は小さいから、粘度の小さい不凍液L2
のみが絞り流路21を経て流通する。この場合の装置特性
は、第３図に示す如きものであり、10Hz付近のシェイク
振動は装置減衰係数（図中破線）が極大を示すことによ
り効果的に減衰低減される。なお、図中、実線は装置の
動バネ定数の特性を示す。By the way, when the shake vibration having a relatively small amplitude is inputted, the deformation amount of the vibration isolating rubber body 1 is small and therefore the volume change of the main liquid chamber A is small, so that the antifreeze liquid L2 having a small viscosity is used.
Only the gas flows through the throttle channel 21. The device characteristics in this case are as shown in FIG. 3, and the shake vibration around 10 Hz is effectively reduced by the device damping coefficient (broken line in the figure) showing a maximum. In the drawing, the solid line indicates the characteristic of the dynamic spring constant of the device.
比較的振幅の大きいしゃくり振動の入力時には、防振
ゴム体１は大きく変形し、これに伴い主液室Ａの容積が
大きく変化して、絞り流路21には不凍液L2に続いて粘度
の大きいシリコーン油L1が流通し、これにより装置特性
は第４図に示す如きものとなる。この状態では図より知
られる如く、10Hz付近で装置動バネ定数（図中実線）は
十分大きな値となり、しゃくり振動が効果的に抑制低減
される。At the time of the input of a relatively large amplitude shock vibration, the vibration-isolating rubber body 1 is greatly deformed, and the volume of the main liquid chamber A is greatly changed accordingly, so that the throttle passage 21 has a large viscosity following the antifreeze liquid L2. The silicone oil L1 circulates, whereby the device characteristics are as shown in FIG. In this state, as is known from the drawing, the device dynamic spring constant (solid line in the drawing) becomes a sufficiently large value around 10 Hz, and the hiccup vibration is effectively suppressed and reduced.
［第２実施例］ 上記シリコーン油に代えて不凍液よりも比重が大きく
（比重1.7〜2.0）かつ粘度も大きいフッ素油（例えばデ
ュポン社製 商品名クライトックス143）を使用しても
良く、この場合には、第５図に示す如く、フッ素油L3が
不凍液L2の下方へ移動し、液の境界R2は副液室Ｂ内に生
じる。[Second embodiment] Instead of the above silicone oil, a fluorine oil having a higher specific gravity (specific gravity of 1.7 to 2.0) and a higher viscosity than antifreeze (for example, Krytox 143 manufactured by DuPont) may be used. Then, as shown in FIG. 5, the fluorine oil L3 moves below the antifreeze liquid L2, and a boundary R2 of the liquid is generated in the sub liquid chamber B.
かかる構成によっても上記第１実施例と同様の効果が
ある。With such a configuration, the same effect as in the first embodiment can be obtained.
［第３実施例］ 第６図に示す如く、シリコーン油L1、不凍液L2、フッ
素油L3の三種を封入することもでき、この場合、仕切壁
２に近い中層に不凍液L2、上層にはシリコーン油L1、下
層にフッ素油L3が位置する。Third Embodiment As shown in FIG. 6, three types of silicone oil L1, antifreeze liquid L2, and fluorine oil L3 can be enclosed. In this case, antifreeze liquid L2 is placed in the middle layer near partition wall 2, and silicone oil is placed in the upper layer. Fluorine oil L3 is located in L1 and lower layer.
かかる構成によれば、大振動入力時の主液室Ａの収縮
時にシリコーン油L1が、主液室Ａの拡大時にはフッ素油
L3がそれぞれ不凍液L2に続いて絞り流路21を流通して、
さらに効果的な振動低減作用がなされる。According to this configuration, the silicone oil L1 is contracted when the main liquid chamber A contracts when a large vibration is input, and the fluorine oil is used when the main liquid chamber A is expanded.
L3 circulates in the throttle channel 21 following the antifreeze L2, respectively.
A more effective vibration reducing action is provided.
［発明の効果］ 以上の如く、本発明の液封入防振装置によれば、比重
が異なり互いに相溶性のない液を液室内に封入すること
により、機械的な作動部を設けて構造を複雑化すること
なく、入力振動の種類に応じて装置特性を最適に変更
し、効果的に振動低減をなすことができる。[Effects of the Invention] As described above, according to the liquid-filled vibration isolator of the present invention, liquids having different specific gravities and being incompatible with each other are sealed in the liquid chamber, thereby providing a mechanical operating portion and complicating the structure. Therefore, the device characteristics can be optimally changed according to the type of the input vibration, and the vibration can be effectively reduced.
第１図ないし第４図は本発明の第１実施例を示し、第１
図は防振装置の全体断面図、第２図は装置の動バネ定数
の周波数特性図、第３図および第４図はいずれも装置の
動バネ定数と減衰係数の周波数特性図、第５図は本発明
の第２実施例を示す防振装置の全体断面図、第６図は本
発明の第３実施例を示す防振装置の全体断面図である。 １……防振ゴム体 ２……仕切壁 21……絞り流路 ３……ゴムシート Ａ、Ｂ……液室 L1、L2、L3……封入液1 to 4 show a first embodiment of the present invention.
FIG. 2 is an overall sectional view of the vibration isolator, FIG. 2 is a frequency characteristic diagram of a dynamic spring constant of the device, FIGS. 3 and 4 are frequency characteristic diagrams of a dynamic spring constant and a damping coefficient of the device, and FIG. FIG. 6 is an overall sectional view of a vibration isolator according to a second embodiment of the present invention, and FIG. 6 is an overall sectional view of a vibration isolator according to a third embodiment of the present invention. 1 ... anti-vibration rubber body 2 ... partition wall 21 ... throttle flow path 3 ... rubber sheet A, B ... liquid chamber L1, L2, L3 ... filled liquid
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭63−308241（ＪＰ，Ａ) 特開 昭64−69837（ＪＰ，Ａ) 特開 昭62−171541（ＪＰ，Ａ) 特開 昭58−207540（ＪＰ，Ａ) 特開 昭58−221028（ＪＰ，Ａ) 実開 昭62−35133（ＪＰ，Ｕ) 実開 昭60−38955（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.6，ＤＢ名) F16F 13/00──────────────────────────────────────────────────続 き Continuation of front page (56) References JP-A-63-308241 (JP, A) JP-A-64-69837 (JP, A) JP-A-62-171541 (JP, A) JP-A-58-58 207540 (JP, A) JP-A-58-221028 (JP, A) JP-A 62-35133 (JP, U) JP-A 60-38955 (JP, U) (58) Fields investigated (Int. 6 , DB name) F16F 13/00
Claims (1)
を形成して液を封入するとともに、該密閉空間内を、絞
り流路を形成した仕切壁で一対の液室に区画し、かつ上
記封入液を、比重が異なり互いに相溶性のない二種以上
の液で構成したことを特徴とする液封入防振装置。1. A sealed space is formed in a vibration-isolating rubber body that supports a vibrating body, a liquid is sealed therein, and the sealed space is partitioned into a pair of liquid chambers by a partition wall having a throttle channel. And a liquid filling vibration isolator, wherein the filling liquid is composed of two or more liquids having different specific gravities and incompatible with each other.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25791490A JP2860701B2 (en) | 1990-09-27 | 1990-09-27 | Liquid filled vibration isolator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25791490A JP2860701B2 (en) | 1990-09-27 | 1990-09-27 | Liquid filled vibration isolator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04136534A JPH04136534A (en) | 1992-05-11 |
| JP2860701B2 true JP2860701B2 (en) | 1999-02-24 |
Family
ID=17312948
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25791490A Expired - Fee Related JP2860701B2 (en) | 1990-09-27 | 1990-09-27 | Liquid filled vibration isolator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2860701B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010050521A1 (en) | 2008-10-28 | 2010-05-06 | 株式会社ブリヂストン | Method for manufacturing anti-vibration device |
| WO2010143444A1 (en) | 2009-06-10 | 2010-12-16 | 株式会社ブリヂストン | Vibrationproof device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9249857B2 (en) | 2007-12-12 | 2016-02-02 | Bridgestone Corporation | Anti-vibration apparatus |
| CN102066803B (en) * | 2008-06-17 | 2014-05-14 | 株式会社普利司通 | Vibration damping device |
| JP5087517B2 (en) * | 2008-10-29 | 2012-12-05 | 株式会社ブリヂストン | Anti-vibration device manufacturing method |
| JP5210947B2 (en) * | 2009-04-08 | 2013-06-12 | 株式会社ブリヂストン | Anti-vibration device manufacturing method |
| JP5264601B2 (en) * | 2009-04-10 | 2013-08-14 | 株式会社ブリヂストン | Anti-vibration device manufacturing method |
| JP5286148B2 (en) * | 2009-04-21 | 2013-09-11 | 株式会社ブリヂストン | Anti-vibration device manufacturing method |
| JP5346697B2 (en) * | 2009-06-10 | 2013-11-20 | 株式会社ブリヂストン | Vibration isolator |
| JP5393273B2 (en) * | 2009-06-10 | 2014-01-22 | 株式会社ブリヂストン | Vibration isolator |
| JP5393272B2 (en) * | 2009-06-10 | 2014-01-22 | 株式会社ブリヂストン | Vibration isolator |
| JP5469926B2 (en) * | 2009-06-10 | 2014-04-16 | 株式会社ブリヂストン | Vibration isolator |
| JP5452089B2 (en) * | 2009-06-15 | 2014-03-26 | 株式会社ブリヂストン | Anti-vibration device manufacturing method |
| JP5286165B2 (en) * | 2009-06-15 | 2013-09-11 | 株式会社ブリヂストン | Anti-vibration device manufacturing method |
| JP5286167B2 (en) * | 2009-06-17 | 2013-09-11 | 株式会社ブリヂストン | Anti-vibration device manufacturing method |
-
1990
- 1990-09-27 JP JP25791490A patent/JP2860701B2/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010050521A1 (en) | 2008-10-28 | 2010-05-06 | 株式会社ブリヂストン | Method for manufacturing anti-vibration device |
| US8407897B2 (en) | 2008-10-28 | 2013-04-02 | Bridgestone Corporation | Method of manufacturing a vibration isolator |
| WO2010143444A1 (en) | 2009-06-10 | 2010-12-16 | 株式会社ブリヂストン | Vibrationproof device |
| US9188191B2 (en) | 2009-06-10 | 2015-11-17 | Bridgestone Corporation | Vibrationproof device |
| EP2441976A4 (en) * | 2009-06-10 | 2016-03-23 | Bridgestone Corp | Vibrationproof device |
| US9435396B2 (en) | 2009-06-10 | 2016-09-06 | Bridgestone Corporation | Vibrationproof device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH04136534A (en) | 1992-05-11 |
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