JPS60172743A - Vibro-isolating bush - Google Patents

Vibro-isolating bush

Info

Publication number
JPS60172743A
JPS60172743A JP2773584A JP2773584A JPS60172743A JP S60172743 A JPS60172743 A JP S60172743A JP 2773584 A JP2773584 A JP 2773584A JP 2773584 A JP2773584 A JP 2773584A JP S60172743 A JPS60172743 A JP S60172743A
Authority
JP
Japan
Prior art keywords
vibration
cylinder
fluid
elastic body
orifice
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
Application number
JP2773584A
Other languages
Japanese (ja)
Inventor
Yuji Kyoi
京井 裕司
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kinugawa Rubber Industrial Co Ltd
Original Assignee
Kinugawa Rubber Industrial Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kinugawa Rubber Industrial Co Ltd filed Critical Kinugawa Rubber Industrial Co Ltd
Priority to JP2773584A priority Critical patent/JPS60172743A/en
Publication of JPS60172743A publication Critical patent/JPS60172743A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04Units 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
    • F16F13/06Units 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
    • F16F13/08Units 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
    • F16F13/14Units of the bushing type, i.e. loaded predominantly radially

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)

Abstract

PURPOSE:To effectively prevent transmission of vibration in an equipment or a device suitable for engine mount by providing the equipment or the device with a function of damping low frequency vibration covering any direction in the circumferential direction of a vibro-isolating bush. CONSTITUTION:A vibro-isolating bush 1 has an intermediate sleeve 4 between an internal sleeve 2 and an external sleeve 3. Primary and secondary fluid chambers 7 and 8 communicated with each other via a primary orifice 9 are formed in a primary resilient member 5 which is disposed between the intermediate and external sleeves 4 and 3 while third and fourth chambers 10 and 11 which are communicated with each other via secondary orifice 12 are formed at right angles with the arranged direction of the primary and secondary fluid chambers 7 and 8 in a secondary resilient member 6 disposed between the internal and intermediate sleeves 2 and 4. Low frequency vibration can be attenuated in not only one direction but also other directions.

Description

【発明の詳細な説明】 産業上の利用分野 本発明d振動体を固定体に振動遮断機能をもって取付け
る際に用いられる筒状の防振ブツシュに関する。
DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a cylindrical anti-vibration bushing used when a vibrating body is attached to a fixed body with a vibration-isolating function.

従来技術 従来、自動車等の車両に搭載されるパワーユニット(エ
ンジン本体にクラッチ、トランスミッシ璽ン等が一体に
結合されたもの)はエンジンマウントを介して車体側に
取付けられるようになっている。この・エンジンマウン
トには、喰ずれか一万が前記、パワー二二ットに、他方
が車体側に装着場れる内筒、外筒間に弾性体と゛しての
ゴムが装填さ゛れるようになった筒状の防振ブツシュが
あり、前記弾性体によってエンジン振動を吸収するよう
になっている。ところが、このエンジン振動にはアイド
リンク時等に発生する低周波大振幅領域と、高回転時に
おける高周波不振幅領域とに大別され、前者の低周波大
振幅時に防振ブツシュに要求される機能は、振動吸収で
はなくむしろパワーユニットの変位規制であり、後者の
高周波小振幅時に要求される機能は本来の振動吸収であ
る。従って、前記弾性体には変位規制時に必要な高いは
ね定数と、振動吸収時に必要な低いばね定数との相反す
る要素が要求される。このため、前記弾性体はこれら相
反する要素の折中点に設定せざるを得す、低周波域のア
イドリンク振動とか走行始めのカフガク振動が車体に発
生したり、高周波域の単室内こもり音が発生したりする
。そこで、従来は特公昭48−36151とか特公昭5
8−17061.0に開示されているように、防振ブツ
シュの弾性体内に内筒を境に対向して互いにi +)フ
ィヌで連通される1対の流体室を設け、該1対の流体室
内液体が前記オリフィスを介して移動するときのダンパ
作用により、低周波大振幅領域の撮動減衰を行なうと共
に、前記弾性体自体で高周波小振幅領域の振動吸収を専
ら行なうことにより、変位規制と振動吸収の両機能を1
つの防振ブツシュで満足するようにしたものがある。
BACKGROUND ART Conventionally, a power unit (in which a clutch, a transmission, etc. are integrally coupled to an engine body) mounted on a vehicle such as an automobile is attached to the vehicle body via an engine mount. In this engine mount, one of the 10,000 parts is the power 22 parts, and the other part is loaded with rubber as an elastic body between the inner cylinder and the outer cylinder, which are installed on the vehicle body side. There is a cylindrical anti-vibration bushing that absorbs engine vibrations using the elastic body. However, this engine vibration can be roughly divided into a low-frequency large-amplitude region that occurs during idling, etc., and a high-frequency no-amplitude region that occurs during high rotation. is not vibration absorption, but rather displacement regulation of the power unit, and the latter function required at high frequency and small amplitude is original vibration absorption. Therefore, the elastic body is required to have contradictory elements: a high spring constant necessary for regulating displacement and a low spring constant necessary for absorbing vibration. For this reason, the elastic body has to be set at the midpoint between these conflicting elements, which may cause idling vibrations in the low frequency range or stiff vibrations at the beginning of running to occur in the vehicle body, and muffled noise in the single room in the high frequency range. may occur. Therefore, in the past, the special public service was designated as 48-36151 or 5
8-17061.0, a pair of fluid chambers are provided in the elastic body of the anti-vibration bushing, facing each other with an inner cylinder as a boundary, and communicating with each other through i+) fins. The damper action when the indoor liquid moves through the orifice attenuates the low-frequency, large-amplitude region, and the elastic body itself exclusively absorbs vibrations in the high-frequency, small-amplitude region, thereby regulating displacement. Both vibration absorption functions in 1
There are some models that are satisfied with just one anti-vibration bushing.

しかしながら、かかる従来の防振ブツシュにあっては、
1・対の流体室は1組で一方向のみに配置されていたた
め、低周波低動の減衰は前記流体室が配置された方向の
みしか効果がない。しかし・パワーユニットの低周波振
動にはアイドル振動、発進時のガクガク撫動、更にはシ
ェイク振動等各種の振動があり、その振動方向が一方向
とは限らなく、前記流体室の配置方向に対して直角方向
にも作用してしまう。
However, in such conventional anti-vibration bushings,
Since one pair of fluid chambers is arranged in only one direction, the damping of low frequency low motion is effective only in the direction in which the fluid chambers are arranged. However, the low-frequency vibrations of the power unit include various vibrations such as idle vibration, jerky vibration when starting, and even shake vibration, and the vibration direction is not necessarily unidirectional, but relative to the arrangement direction of the fluid chamber. It also works in the right angle direction.

発明の目的 本発明はかかる従来の実状に鑑みて、低周波振動の減衰
方向が一方向の与ならず他の方向にも減衰されるように
した防振ブツシュを提供することを目的とする。
OBJECTS OF THE INVENTION In view of the conventional situation, it is an object of the present invention to provide a vibration-proof bushing in which low-frequency vibrations are attenuated not only in one direction but also in other directions.

発明の構成 かかる目的を達成する・ために本発明は、内面。Composition of the invention In order to achieve this objective, the present invention is intended to achieve this objective.

中間筒および外筒が夫々略同心状に配置され、中間筒と
外筒との間に第1弾性体を装填すると共に、内筒と中間
筒との間に第2弾性体を装填し、前記第1弾性体内に中
間筒を境に対向して1対の第1゜第2流体室を形成する
と共に、前記第2弾性体内に内筒を境に対向して前記第
1.第2流体室の配設方向に対し負角方向に1対の第3
.第4流体室を形成し、前記第1.第2流体室および前
記第3゜第4流体室を第1オリフイスおよび第2オリフ
イスを介して夫々連通することにより構成しである。
An intermediate cylinder and an outer cylinder are arranged approximately concentrically, a first elastic body is loaded between the intermediate cylinder and the outer cylinder, a second elastic body is loaded between the inner cylinder and the intermediate cylinder, and the A pair of first and second fluid chambers are formed in the first elastic body facing each other with an intermediate cylinder as a boundary, and a pair of first and second fluid chambers are formed in the second elastic body facing each other with an inner cylinder as a boundary. A pair of third fluid chambers are arranged in a negative angle direction with respect to the arrangement direction of the second fluid chamber.
.. forming a fourth fluid chamber; The second fluid chamber and the third and fourth fluid chambers are configured to communicate with each other through a first orifice and a second orifice, respectively.

実施例 以1本発明の一実施例を図に基づいて詳細に説明する。Example Hereinafter, one embodiment of the present invention will be described in detail based on the drawings.

即ち、第1図、第2図は本発明の一実施例を示す防振ブ
ツシュ1で、内筒2と外筒6との間に中間筒4が設けら
れ、これら内筒2.中間筒4.外筒6が取付状態におい
て夫々同心状に配置されるようになっている。前記外筒
・6および中間筒4は゛夫々圧入嵌合される第1.第2
外筒3a、3bおよび第1.第2中間筒4a、4bによ
って構成されている。そして、中間筒4と外筒6との間
にはゴム成形された第1弾性体5および内筒2と中間筒
4との間には同様にゴム成形された第2弾性体6が夫々
装填され、前記第1弾性体5は第2外筒66と第1中間
筒4aに加硫接着されると共に、前記第2弾性体6は第
2中間筒4bと内筒2に加硫接着されている。前記第1
弾性体6内には中間筒4を境にして対向する第1流体室
7.第2流体室8が形成されている。これら第1.第2
流体室7.8内には水等の液体(非圧縮性流体ンが注入
され、そして、前記第1弾性体6の外4周部に埋設され
た管状の第1オリフイス9を介して前記第1゜第2流体
呈7.8が連通されている。−万、前記第2弾性体6内
には内筒2を境に対向して、前記第1.第2流体寛7.
8の配設方向に対し直角方向に1対の第3.第4流体室
10.11を形成しである。これら第3.第4流体室1
0.11内に祉第1.第2流体呈7,8と同様に水等の
液体が注入され、そして、第2弾性体6の内周部に埋設
された管状の第2オリアイス12を介して前記第3、第
4流体箪10,11が連通されている。
That is, FIGS. 1 and 2 show a vibration-proof bushing 1 showing one embodiment of the present invention, in which an intermediate cylinder 4 is provided between an inner cylinder 2 and an outer cylinder 6, and these inner cylinders 2. Intermediate cylinder 4. The outer cylinders 6 are arranged concentrically in the attached state. The outer cylinder 6 and the intermediate cylinder 4 each have a first cylinder which is press-fitted. Second
The outer cylinders 3a, 3b and the first. It is composed of second intermediate cylinders 4a and 4b. A first elastic body 5 molded from rubber is loaded between the intermediate cylinder 4 and the outer cylinder 6, and a second elastic body 6 similarly molded from rubber is loaded between the inner cylinder 2 and the intermediate cylinder 4. The first elastic body 5 is vulcanized and bonded to the second outer cylinder 66 and the first intermediate cylinder 4a, and the second elastic body 6 is vulcanized and bonded to the second intermediate cylinder 4b and the inner cylinder 2. There is. Said first
Inside the elastic body 6 are first fluid chambers 7 facing each other with the intermediate cylinder 4 as a boundary. A second fluid chamber 8 is formed. These first. Second
A liquid such as water (incompressible fluid) is injected into the fluid chamber 7.8, and the fluid is injected into the fluid chamber 7.8 through a tubular first orifice 9 buried in the outer four circumferences of the first elastic body 6. 1. A second fluid hole 7.8 is in communication with the second fluid hole 7.8.
A pair of third. A fourth fluid chamber 10.11 is formed. These third. Fourth fluid chamber 1
Welfare first within 0.11. Similarly to the second fluid reservoirs 7 and 8, a liquid such as water is injected into the third and fourth fluid reservoirs via a tubular second oriice 12 embedded in the inner circumference of the second elastic body 6. 10 and 11 are connected.

そして、かかる構成になる防振ブツシュ1は、内筒2が
この内筒2内に挿通される図外のボルトを介して固定体
としての単体側に装着され、外筒6が振動体としてのパ
ワーユニット側に装着されるようにな・っている。
In the anti-vibration bushing 1 having such a structure, the inner cylinder 2 is attached to a single unit as a fixed body via a bolt (not shown) inserted into the inner cylinder 2, and the outer cylinder 6 is attached as a vibrating body. It is designed to be installed on the power unit side.

以上の構成により、パワーユニットにアイドル振動、ガ
クガク振動、シェイ゛り振動等の低周波太゛振幅領域の
振動が発生した場合は、第1.第2流体呈7,8内の液
体が第1オリフイス9を介して移動するときのダンパ作
用、若しくは第3.第4流体INO,11内の液体が第
2オリフィス12を介して移動するときのダンパ作用、
又はこれら2つのダンパ作用が相俟ってnil記低周波
振動を効率よく減衰する。即ち、第1.第2流体峯7,
8の配置方向の振kJJK対しては、該第1.第2流体
室7,8内の容積変化(一方が膨出、他方が収iPl旬
が生じて、このときのタンパ作用により壁動減哀を行な
う。このとき、第3.第4流体室?0.11内の容積変
化は行なわれず、この、第3.第4流体呈10.11間
でのダンパ作用はなく、また、ダンパ作用を行なう必装
はない。一方、第3.第4流体室10.11の配置方向
の振動に対しては、これら第3.第4流体室10.11
間のダンパ作用により振動減衰が行なわれる。このとき
、第1゜第2流体室7,8間にはダンパ作用が行なわれ
ない。史にこのように、第1.第2流体室7,8方向お
よびこの方向と直角方向の第3.第4流体室10.11
方向の撮動方向に対して効率良く振動減衰が行なわする
ことは勿論のこと、前記両方向に対して斜め方向の振動
入力に対しても、この振動入力の前記両方向に対する分
力成分が作用し、第1.第2流体室7,8および第3.
第4流体室10.11の相方に前記分力成分に対応する
減衰力が働き、前記斜め方向の低周波振動入力に対して
も減衰力が作用する。このように1、本夾施例の防振ブ
ツシュ1にあってはあらゆる方向(周方向)の低周波振
動入力に対して減′衰慎能が働き、車体側へ低周波振動
が伝達されるのを効率よく防止することができる。
With the above configuration, when vibrations in the low frequency, wide amplitude range, such as idle vibrations, jerky vibrations, and shear vibrations, occur in the power unit, the first problem occurs. A damping effect when the liquid in the second fluid chamber 7, 8 moves through the first orifice 9, or a third. a damping effect when the liquid in the fourth fluid INO, 11 moves through the second orifice 12;
Alternatively, these two damper actions work together to efficiently damp nil low frequency vibrations. That is, 1st. 2nd fluid mine 7,
For the swing kJJK in the arrangement direction of No. 8, the first. Volume changes in the second fluid chambers 7 and 8 (one bulges and the other contracts, and the tamper action at this time reduces wall movement. At this time, the third and fourth fluid chambers? There is no volume change within 0.11, there is no damping action between the third and fourth fluids, and there is no necessity to perform a damping action. For vibrations in the arrangement direction of the chambers 10.11, these third and fourth fluid chambers 10.11
Vibration damping is achieved by the damper action between the two. At this time, no damper action is performed between the first and second fluid chambers 7 and 8. Like this in history, the first. The second fluid chamber 7, 8 direction and the third fluid chamber in the direction perpendicular to this direction. Fourth fluid chamber 10.11
Not only is vibration damping performed efficiently in the photographing direction, but also component force components of the vibration input in the two directions act on vibration input in an oblique direction with respect to the two directions. 1st. The second fluid chambers 7, 8 and the third.
A damping force corresponding to the component force component acts on the other side of the fourth fluid chamber 10.11, and a damping force also acts on the low-frequency vibration input in the diagonal direction. In this way, 1. In the anti-vibration bushing 1 of this embodiment, the attenuation function works against low-frequency vibration input in all directions (circumferential direction), and the low-frequency vibration is transmitted to the vehicle body. can be efficiently prevented.

同、前記防振プツシ:=−1はノくワーユニットの支持
マウントとして用いたものを示し、内筒2が車体側に、
外筒3がパワーユニット側に装別されるものを示したが
、これを逆にして内筒2がパワーユニット側に、外筒6
が車体側に装N芒れるようにしたものでもよく、更に、
本発明の防振プツシ:Lはパワーユニットの支持ブラン
トに1沢ることなく一般の振動体を固定体に取付ける際
にLYjいることができる。
Same, the above-mentioned anti-vibration pusher: =-1 indicates the one used as a support mount for the knocker unit, and the inner cylinder 2 is on the vehicle body side.
Although the outer cylinder 3 is shown attached to the power unit side, this is reversed so that the inner cylinder 2 is attached to the power unit side and the outer cylinder 6 is attached to the power unit side.
may be mounted on the vehicle body side, and furthermore,
The anti-vibration pushbutton of the present invention: L can be used when attaching a general vibrating body to a fixed body without having to use the support blunt of the power unit.

発明の詳細 な説明したように本発明の防振フッシュは、中間筒と外
筒との間に装填はれた第1弾性体に、第1オリフイスを
介して4281される第l、第2流体室を形成する一万
、内筒と中間間との間に装填された第2弾性体に、前記
第1.第2流体案の配置方向と直角方向に第2オリフイ
7を介して連通される第3.第4流体室を形成したので
、hU記第1、第2流体室方向のみならず第3.第4流
体室方向の低周波振動を減衰でき、史に、かかる第1゜
第2流体室方向、第3.第4流体尾方向に対して斜め方
向の振動入力に対しても減衰機能が発揮婆れる。従って
、防振ブツシュの周方向におけるあらゆる方向の低周波
振動に対して減衰機能を鳴し、振動体側の低周波振動が
固定体側に伝達されるのを効率良く防止することができ
るという優れた効果を肩する。。
As described in detail, the vibration isolating fish of the present invention has the first elastic body loaded between the intermediate cylinder and the outer cylinder, and the first and second fluids 4281 applied through the first orifice. The second elastic body, which forms a chamber, is loaded between the inner cylinder and the intermediate space. The third fluid is communicated through the second orifice 7 in a direction perpendicular to the arrangement direction of the second fluid. Since the fourth fluid chamber is formed, not only the direction of the first and second fluid chambers but also the direction of the third fluid chamber. Low frequency vibrations in the direction of the fourth fluid chamber can be damped. The damping function can also be achieved against vibration input in a diagonal direction with respect to the fourth fluid tail direction. Therefore, the damping function is activated against low-frequency vibrations in all directions in the circumferential direction of the anti-vibration bushing, and the excellent effect is that low-frequency vibrations on the vibrating body side can be efficiently prevented from being transmitted to the fixed body side. shoulder. .

【図面の簡単な説明】[Brief explanation of the drawing]

第1図り本発明の防振ブッ・シュの一実施例を示す中央
横断面図、第2図は第1凶の川−B線からの断面図でお
る。 1・・・防振ブツシュ、2・・・内筒、6・・・外筒、
4・・・中間筒、5・・・第1弾性体、6・・・第2弾
性体、7・・・第1流体呈、8・・・第2流体呈、9・
・・第1オリフイス、10・・・第3流体室、11・・
・第4流体室、12・・・第2オリフイヌ。 第1図
The first figure is a central cross-sectional view showing one embodiment of the anti-vibration bushing of the present invention, and the second figure is a cross-sectional view taken along line B of the first line. 1... Anti-vibration bushing, 2... Inner cylinder, 6... Outer cylinder,
4... Intermediate cylinder, 5... First elastic body, 6... Second elastic body, 7... First fluid presentation, 8... Second fluid presentation, 9.
...First orifice, 10...Third fluid chamber, 11...
- Fourth fluid chamber, 12... second orifice dog. Figure 1

Claims (1)

【特許請求の範囲】[Claims] (1) 内筒、中間筒および外筒が夫々略同心状に配置
され、中間筒と外筒との間に第1弾性体を装填すると共
に、内筒と中間筒との間に第2弾性体を装填し、前記第
1弾性体内に中間筒を境に対向して1対の第1.第2流
体室を形成すると共に、前記第2弾硅体内に円筒を境に
対向して前記第1゜第2流体室の配設方向に対し直角方
向に1対の第3、第4流体室を形成し、前記第1.第2
流体室および前記第3.第4流体室を第1オリフイスお
よび第2オリフイスを介して夫々連通した仁とを特徴と
する防振ブツシュ◎
(1) An inner cylinder, an intermediate cylinder, and an outer cylinder are arranged approximately concentrically, and a first elastic body is loaded between the intermediate cylinder and the outer cylinder, and a second elastic body is loaded between the inner cylinder and the intermediate cylinder. The first elastic body is loaded with a pair of first elastic bodies facing each other with an intermediate cylinder as a boundary. A second fluid chamber is formed, and a pair of third and fourth fluid chambers are formed in the second bullet body, facing each other with a cylinder as a boundary, and extending in a direction perpendicular to the arrangement direction of the first and second fluid chambers. forming the first. Second
the fluid chamber and the third. A vibration-proof bushing characterized by a joint that communicates the fourth fluid chamber through the first orifice and the second orifice, respectively.
JP2773584A 1984-02-16 1984-02-16 Vibro-isolating bush Pending JPS60172743A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2773584A JPS60172743A (en) 1984-02-16 1984-02-16 Vibro-isolating bush

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2773584A JPS60172743A (en) 1984-02-16 1984-02-16 Vibro-isolating bush

Publications (1)

Publication Number Publication Date
JPS60172743A true JPS60172743A (en) 1985-09-06

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ID=12229283

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2773584A Pending JPS60172743A (en) 1984-02-16 1984-02-16 Vibro-isolating bush

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Country Link
JP (1) JPS60172743A (en)

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2593255A1 (en) * 1986-01-22 1987-07-24 Peugeot Hydro-elastic articulation
FR2601098A1 (en) * 1986-07-04 1988-01-08 Tokai Rubber Ind Ltd ELASTIC CUFFING STRUCTURE WITH FLUID FILLING
US4767107A (en) * 1986-01-30 1988-08-30 Automobiles Peugeot Central suspension hydroelastic mount, in particular for the suspension of a motor-vehicle motor-drive unit
US4771990A (en) * 1986-03-19 1988-09-20 Hutchinson Hydraulic antivibration support sleeves
US4790520A (en) * 1985-11-25 1988-12-13 Nissan Motor Co., Ltd. Vibration insulating device with flexible diaphragm between radially outer gas chamber and radially inner liquid chamber
DE3722132A1 (en) * 1987-07-04 1989-01-12 Daimler Benz Ag HYDRAULIC DAMPING BEARING
US4817926A (en) * 1987-04-04 1989-04-04 Firma Carl Freudenberg Hydraulically damped tubular rubber spring
FR2622268A1 (en) * 1987-10-22 1989-04-28 Freudenberg Carl RUBBER BUSHING SPRING
US4871150A (en) * 1987-01-20 1989-10-03 Automobiles Peugeot Elastically yieldable support in particular for the suspension of a vehicle engine
US4971456A (en) * 1988-10-08 1990-11-20 Tokai Rubber Industries, Ltd. Fluid-filled elastic center bearing mount
JPH039137A (en) * 1989-06-06 1991-01-17 Tokai Rubber Ind Ltd Liquid enclosing type cylindrical mount device
US5024425A (en) * 1989-02-24 1991-06-18 Firma Carl Freudenberg Elastomeric sleeve spring
US5044813A (en) * 1988-01-26 1991-09-03 The Goodyear Tire & Rubber Company Bush type hydraulically damped engine or transmission mount
US5172894A (en) * 1991-12-05 1992-12-22 Gencorp Inc. Dual elastomeric/fluid engine mount
US5178376A (en) * 1989-10-05 1993-01-12 Firma Carl Freudenberg Hydraulically damped rubber cartridge spring
US5299788A (en) * 1990-12-13 1994-04-05 Tokai Rubber Industries, Ltd. Fluid-filled cylindrical elastic mount having orifice passages and voids formed in elastic body
US5489193A (en) * 1993-07-29 1996-02-06 Hutchinson Antivibration supports for helicopter blades, and a helicopter rotor including such supports
FR2784152A1 (en) * 1998-10-06 2000-04-07 Mannesmann Boge Gmbh A hydraulically damped rubber mounting for a motor vehicle that incorporates rigid cylindrical inner member and a spaced rigid cylindrical outer member
WO2001073315A1 (en) * 2000-03-27 2001-10-04 ZF Lemförder Metallwaren AG Rubber bearing with graduated damping behavior
DE10118229A1 (en) * 2001-04-11 2002-11-07 Zf Lemfoerder Metallwaren Ag Hydraulically damping bush bearing
WO2010108490A1 (en) * 2009-03-23 2010-09-30 Zf Friedrichshafen Ag Elastomeric plain bearing having switchable rigidity
US7866639B2 (en) 2008-12-09 2011-01-11 Tokai Rubber Industries, Ltd. Fluid-filled cylindrical vibration-damping device

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4790520A (en) * 1985-11-25 1988-12-13 Nissan Motor Co., Ltd. Vibration insulating device with flexible diaphragm between radially outer gas chamber and radially inner liquid chamber
FR2593255A1 (en) * 1986-01-22 1987-07-24 Peugeot Hydro-elastic articulation
US4767107A (en) * 1986-01-30 1988-08-30 Automobiles Peugeot Central suspension hydroelastic mount, in particular for the suspension of a motor-vehicle motor-drive unit
US4771990A (en) * 1986-03-19 1988-09-20 Hutchinson Hydraulic antivibration support sleeves
US4871152A (en) * 1986-07-04 1989-10-03 Takai Rubber Industries, Ltd. Fluid-filled resilient bushing structure with radial vanes
FR2601098A1 (en) * 1986-07-04 1988-01-08 Tokai Rubber Ind Ltd ELASTIC CUFFING STRUCTURE WITH FLUID FILLING
US4871150A (en) * 1987-01-20 1989-10-03 Automobiles Peugeot Elastically yieldable support in particular for the suspension of a vehicle engine
US4817926A (en) * 1987-04-04 1989-04-04 Firma Carl Freudenberg Hydraulically damped tubular rubber spring
DE3722132A1 (en) * 1987-07-04 1989-01-12 Daimler Benz Ag HYDRAULIC DAMPING BEARING
FR2622268A1 (en) * 1987-10-22 1989-04-28 Freudenberg Carl RUBBER BUSHING SPRING
DE3735698A1 (en) * 1987-10-22 1989-05-03 Freudenberg Carl Fa SLEEVE RUBBER SPRING
US5044813A (en) * 1988-01-26 1991-09-03 The Goodyear Tire & Rubber Company Bush type hydraulically damped engine or transmission mount
US4971456A (en) * 1988-10-08 1990-11-20 Tokai Rubber Industries, Ltd. Fluid-filled elastic center bearing mount
US5024425A (en) * 1989-02-24 1991-06-18 Firma Carl Freudenberg Elastomeric sleeve spring
JPH039137A (en) * 1989-06-06 1991-01-17 Tokai Rubber Ind Ltd Liquid enclosing type cylindrical mount device
US5178376A (en) * 1989-10-05 1993-01-12 Firma Carl Freudenberg Hydraulically damped rubber cartridge spring
US5299788A (en) * 1990-12-13 1994-04-05 Tokai Rubber Industries, Ltd. Fluid-filled cylindrical elastic mount having orifice passages and voids formed in elastic body
US5172894A (en) * 1991-12-05 1992-12-22 Gencorp Inc. Dual elastomeric/fluid engine mount
US5489193A (en) * 1993-07-29 1996-02-06 Hutchinson Antivibration supports for helicopter blades, and a helicopter rotor including such supports
FR2784152A1 (en) * 1998-10-06 2000-04-07 Mannesmann Boge Gmbh A hydraulically damped rubber mounting for a motor vehicle that incorporates rigid cylindrical inner member and a spaced rigid cylindrical outer member
WO2001073315A1 (en) * 2000-03-27 2001-10-04 ZF Lemförder Metallwaren AG Rubber bearing with graduated damping behavior
DE10118229A1 (en) * 2001-04-11 2002-11-07 Zf Lemfoerder Metallwaren Ag Hydraulically damping bush bearing
DE10118229B4 (en) * 2001-04-11 2007-03-29 ZF Lemförder Metallwaren AG Hydraulically damping bush bearing
US7866639B2 (en) 2008-12-09 2011-01-11 Tokai Rubber Industries, Ltd. Fluid-filled cylindrical vibration-damping device
WO2010108490A1 (en) * 2009-03-23 2010-09-30 Zf Friedrichshafen Ag Elastomeric plain bearing having switchable rigidity
US8807543B2 (en) 2009-03-23 2014-08-19 Audi Ag Elastomeric plain bearing having switchable rigidity

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