JPS62242149A - Elastic suspension device - Google Patents
Elastic suspension deviceInfo
- Publication number
- JPS62242149A JPS62242149A JP8333186A JP8333186A JPS62242149A JP S62242149 A JPS62242149 A JP S62242149A JP 8333186 A JP8333186 A JP 8333186A JP 8333186 A JP8333186 A JP 8333186A JP S62242149 A JPS62242149 A JP S62242149A
- Authority
- JP
- Japan
- Prior art keywords
- elastic body
- vibration
- fluid chamber
- deformation
- great
- 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
- 239000000725 suspension Substances 0.000 title abstract 2
- 239000012530 fluid Substances 0.000 claims abstract description 31
- 238000006073 displacement reaction Methods 0.000 claims abstract description 12
- 230000001105 regulatory effect Effects 0.000 claims description 17
- 238000013016 damping Methods 0.000 abstract description 13
- 230000001276 controlling effect Effects 0.000 abstract description 5
- 230000002093 peripheral effect Effects 0.000 description 6
- 230000010349 pulsation Effects 0.000 description 5
- 230000003247 decreasing effect Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 239000013013 elastic material Substances 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
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
- F16F13/10—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 the wall being at least in part formed by a flexible membrane or the like
-
- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/003—Dampers characterised by having pressure absorbing means other than gas, e.g. sponge rubber
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)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は自動車のエンジンの支持装置等に用いられて好
適な流体封入型の防振支持装置に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a fluid-filled vibration damping support device suitable for use in a support device for an automobile engine.
（従来の技術）
自動車のエンジンを支持する流体封入型の防振支持装置
として、従来、振動体と支持体との相対変位に基いて変
形する第１弾性体で画成された第１流体室と、前記第１
流体室に連通路を介して連通し、前記第１流体室の容積
変化に基いて容積が変化する第２流体室とを備えるもの
が知られている。(Prior Art) Conventionally, a fluid-filled vibration-proof support device for supporting an automobile engine includes a first fluid chamber defined by a first elastic body that deforms based on relative displacement between a vibrating body and a support body. and the first
A device is known that includes a second fluid chamber that communicates with the fluid chamber via a communication path and whose volume changes based on a change in the volume of the first fluid chamber.
斯かる防振支持装置においては、車両の急発進、急停止
等の大変位入力時やエンジンの低周波数域の振動時には
減衰力を大きくし、高周波数域の振動時には振動伝達率
を小さくすることが要求される。In such a vibration isolating support device, the damping force should be increased when a large displacement input such as sudden start or stop of the vehicle occurs, or when vibrations occur in the low frequency range of the engine, and the vibration transmissibility should be reduced when vibrations occur in the high frequency range. is required.
（発明が解決しようとする問題点）
しかしながら従来装置では、連通路の断面積を小さくし
減衰力を大きく設定しようとすると、動的ばね定数が高
くなり、高周波数域の振動時における振動伝達率を効果
的に低減し難い不具合がある。(Problem to be solved by the invention) However, in conventional devices, when trying to reduce the cross-sectional area of the communication path and set a large damping force, the dynamic spring constant becomes high, and the vibration transmissibility during vibration in the high frequency range increases. There are some problems that make it difficult to reduce them effectively.
本発明は前記事情に鑑み案出されたものであって、本発
明の目的とする処は、大変位入力時や低周波数域の振動
時には減衰力を大きくし、且つ高周波数域の振動時には
振動伝達率を小さくできる防振支持装置を提供するにあ
る。The present invention has been devised in view of the above circumstances, and an object of the present invention is to increase the damping force during large displacement input or vibration in the low frequency range, and to reduce the vibration during vibration in the high frequency range. An object of the present invention is to provide a vibration isolating support device that can reduce the transmission rate.
（問題点を解決するための手段） 本発明は前記目的を達成するため。(Means for solving problems) The present invention aims to achieve the above object.
第１流体室（９）に前記第１弾性体（７）よりも変形容
易な第２弾性体（１９）を臨ませ、前記第２弾性体（１
９）の変形量を可変制御する規制部材（２３）を設けた
。A second elastic body (19) that is easier to deform than the first elastic body (7) faces the first fluid chamber (9);
A regulating member (23) for variably controlling the amount of deformation of 9) was provided.
（作用）
大変位入力時や低周波数域の振動時には第２弾性体（１
９）を変形させず、或いは第２弾性体（１９）の変形量
を小さくして、連通路（１１）を通過する流体によって
減衰力を大きくする。(Function) During large displacement input or vibration in the low frequency range, the second elastic body (1
9) is not deformed or the amount of deformation of the second elastic body (19) is reduced, and the damping force is increased by the fluid passing through the communication path (11).
高周波数域の振動時には第２弾性体（１３）の変形量を
大きくし、振動により生ずる第１流体室（９）内の脈動
を緩和させ、動的ばね定数を小さくし振動伝達率を小さ
くする。During vibrations in a high frequency range, the amount of deformation of the second elastic body (13) is increased, the pulsations in the first fluid chamber (9) caused by the vibrations are alleviated, the dynamic spring constant is decreased, and the vibration transmissibility is decreased. .
（実施例）
以下、本発明の好適一実施例を添付図面に従って説明す
る。(Embodiment) A preferred embodiment of the present invention will be described below with reference to the accompanying drawings.
第１図は防振支持装置の断面側面図、第２図は同要部の
断面平面図を示す。FIG. 1 is a cross-sectional side view of the vibration isolation support device, and FIG. 2 is a cross-sectional plan view of the main parts thereof.
（１）は防振支持装置、（３）は振動体であるエンジン
に取付けられる取付部材、（５）は支持体である車体に
取付けられる取付部材で、再取付部材（３） 、 （５
）間を截頭円錐形を呈する中空状の弾性体（７）で接続
し、エンジンと車体との相対変位に基いて変形する弾性
体（７）で第１流体室（９）を画成する。(1) is a vibration isolating support device, (3) is a mounting member that is attached to the engine that is a vibrating body, and (5) is a mounting member that is attached to the vehicle body that is a support body, and the reinstallation members (3), (5) are
) are connected by a hollow elastic body (7) in the shape of a truncated cone, and a first fluid chamber (9) is defined by the elastic body (7) that deforms based on relative displacement between the engine and the vehicle body. .
前記車体側の取付部材（５）は円形の基板部（５Ａ）と
、基板部（５Ａ）の外周に肉厚に形成した外周部（５Ｂ
）とで構成し、基板部（５Ａ）の中央にはオリフィス（
１１）を形成する。The mounting member (5) on the vehicle body side includes a circular base plate part (5A) and an outer peripheral part (5B) formed thickly on the outer periphery of the base plate part (5A).
), and an orifice (
11).
前記取付部材（５）の第１流体室（９）に臨む面とは反
対の面には弾性材からなるダイヤフラム（１３）を取着
し、取付部材（５）とダイヤプラム（１３）とで、前記
第１流体室（９）の容積変化に基いて容積が変化する第
２流体室（１５）を形成し、ダイヤフラム（１３）はカ
バー（１７）で覆う。A diaphragm (13) made of an elastic material is attached to the surface of the mounting member (5) opposite to the surface facing the first fluid chamber (9), and the mounting member (5) and the diaphragm (13) A second fluid chamber (15) whose volume changes based on a change in the volume of the first fluid chamber (9) is formed, and the diaphragm (13) is covered with a cover (17).
そして前記第１流体室（９）に臨ませて第２弾性体（１
９）を設ける。A second elastic body (1) faces the first fluid chamber (9).
9).
前記第２弾性体（１９）は取付部材（５）の外周部（５
Ｂ）内に配設し、第２弾性体（１θ）は外周部（５Ｂ）
に形成した架部（２１）を介して半部を流体室（９）に
臨ませる。The second elastic body (19) is attached to the outer peripheral portion (5) of the mounting member (5).
B), and the second elastic body (1θ) is located in the outer peripheral part (5B).
The half part faces the fluid chamber (9) through a frame part (21) formed in the.
前記第２弾性体（１８）は前記第１弾性体（７）よりも
容易に変形し得るように形成し、実施例では弾性材によ
り断面を環状に形成した。The second elastic body (18) is formed to be more easily deformable than the first elastic body (7), and in the embodiment, it is made of an elastic material and has an annular cross section.
前記第２弾性体（１８）の内部には該第２弾性体（１９
）の変形を規制する規制部材（２３）を挿入する。The second elastic body (19) is provided inside the second elastic body (18).
) is inserted into the regulating member (23).
前記規制部材（２３）は軸状を呈しスリーブ（２４Ａ）
。The regulating member (23) has a shaft shape and has a sleeve (24A).
.
（２４Ｂ）により回転自在に支持し、規制部材（２３）
の外周面（２３Ａ）には架部（２１）に臨ませて四部（
２５）を周方向半部にわたって延出形成し、四部（２５
）と第２弾性体（１９）とで空気室（２７）を画成する
。(24B) and is rotatably supported by the regulating member (23).
There are four parts (23A) facing the frame (21) on the outer peripheral surface (23A) of the
25) is formed to extend over a half part in the circumferential direction, and four parts (25
) and the second elastic body (19) define an air chamber (27).
実施例１は第２５１性体（１９）の耐久性を高めるため
、第２ｑａ性体（１８）と規制部材（２３）を固着し、
外周部（５Ｂ）の支持孔（２８）で第２弾性体（１９）
と規制部材（２３）を回転自在に支持した。In Example 1, in order to increase the durability of the 251st element (19), the 2nd qa element (18) and the regulating member (23) were fixed,
The second elastic body (19) is inserted into the support hole (28) of the outer peripheral part (5B).
and the regulating member (23) were rotatably supported.
前記規制部材（２３）の端部にはパルスモータ等の適宜
駆動手段（３１）を連結する。An appropriate drive means (31) such as a pulse motor is connected to the end of the regulating member (23).
前記駆動手段（３１）は加速度や、エンジン回転数、エ
ンジン振動数、アクセル開度等の各種運転パラメータに
基いて作動させ、大変位入力時には第３図（ａ）に示す
ように規制部材（２３）の外周面（２３Ａ）を架部（２
１）側に臨ませ、アイドル回転時を含んだ低周波数振動
域では第３図（ｂ）に示すように凹部（２５）の半部を
架部（２１）側に臨ませ、且つ周波数が高くなるにつれ
て軸部材（２３）を次第に回転させ、第３図（Ｃ）に示
すように高周波数振動域では凹部（２５）全体を架部（
２１）側に臨ませるように構成する。The driving means (31) is operated based on various operating parameters such as acceleration, engine rotation speed, engine vibration frequency, and accelerator opening, and when a large displacement is input, the regulating member (23) is activated as shown in FIG. 3(a). ) of the outer peripheral surface (23A) of the frame (2
1) side, and in the low frequency vibration range including idling, half of the recess (25) faces the frame (21) side as shown in Figure 3 (b), and the frequency is high. As the temperature increases, the shaft member (23) is gradually rotated, and as shown in FIG.
21) Configure it so that it faces the side.
本実施例は前記のように構成したので、大変位入力時に
は第２弾性体（１８）は規制部材（２３）の外周面（２
３Ａ）により変形が阻とされ、従って第１流体室（８）
の容積変化時にオリフィス（１１）を通過する流体によ
って大きな減衰力を得ることができる。Since this embodiment is configured as described above, when a large displacement is input, the second elastic body (18) is
3A) prevents deformation and therefore the first fluid chamber (8)
A large damping force can be obtained by the fluid passing through the orifice (11) when the volume changes.
また低周波数域の振動時には、第１流体室（９）内の脈
動により第２ｊｊｌ性体（１９）は凹部（２５）の半部
を介して変形可能であり、第１流体室（８）内の脈動を
前記大変位入力時の場合よりも弱め、オリフィス（１１
）を通過する流体によって所望の減衰力を発生させるこ
とができる。Furthermore, during vibrations in a low frequency range, the second jjl elastic body (19) can be deformed through the half of the recess (25) due to pulsations in the first fluid chamber (9), and The pulsation of the orifice (11
) can generate the desired damping force.
更に、振動周波数が高くなるにつれて矢部（２１）に臨
む四部（２５）の容積を増大させ、第２弾性体（１８）
の変形し得る容積を増大して第１流体室（８）内の脈動
を漸次緩和し、動的ばね定数を小さくする。そして高周
波数域の振動時には凹部（２５）全体によって第１流体
室（３）内の脈動を緩和し、振動伝達率を極めて小さく
することができる。Furthermore, as the vibration frequency increases, the volume of the fourth part (25) facing the arrow part (21) is increased, and the second elastic body (18)
The deformable volume of the first fluid chamber (8) is increased to gradually alleviate the pulsations in the first fluid chamber (8), thereby decreasing the dynamic spring constant. When vibrations occur in a high frequency range, the entire concave portion (25) can alleviate the pulsation within the first fluid chamber (3), making it possible to extremely reduce the vibration transmissibility.
第４図は規制部材（３３）の第２実施例を示す。FIG. 4 shows a second embodiment of the regulating member (33).
第２実施例では規制部材（３３）の外周面（３３Ａ）に
深さの異なる二つの凹部（３５） 、（３７）を形成し
、大変位入力時には外周面（３３Ａ）を流体室（９）に
臨ませ、低周波数域の振動時には深さの小さい凹部（３
５）を流体室（９）に臨ませ、高周波数域の振動時には
深さの大きい四部（３７）を波体室（９）に臨ませ、減
衰力及び振動伝達率を段階的に調整するようにした。In the second embodiment, two recesses (35) and (37) with different depths are formed on the outer circumferential surface (33A) of the regulating member (33), and when a large displacement is input, the outer circumferential surface (33A) is formed in the fluid chamber (9). When vibrations occur in the low frequency range, a small recess (3
5) facing the fluid chamber (9), and the fourth part (37) with a large depth facing the wave body chamber (9) during vibrations in a high frequency range, so that the damping force and vibration transmissibility can be adjusted in stages. I made it.
尚、実施例では第２弾性体（１８）と規制部材（２３）
、（３３）を固着した場合について説明したが、第２弾
性体（１９）内で規制部材（２３） 、（３３）のみを
回転させてもよく、更に規制部材（２３） 、（３３）
は軸方向に移動させるようにしてもよい。In addition, in the embodiment, the second elastic body (18) and the regulating member (23)
, (33) are fixed, but only the regulating members (23), (33) may be rotated within the second elastic body (19).
may be moved in the axial direction.
また、第２弾性体（１９）の変形を規制する規制部材の
構造は、実施例の如く軸状の部材に限らず任意である。Furthermore, the structure of the regulating member that regulates the deformation of the second elastic body (19) is not limited to the shaft-shaped member as in the embodiment, but may be arbitrary.
（発明の効果）
以上の説明で明らかなように本発明に係る防振支持装置
によれば、大変位入力時や低周波数域の振動時には減衰
力を大きくシ、且つ高周波数域の振動時には振動伝達率
を小さくすることができる。(Effects of the Invention) As is clear from the above explanation, the vibration isolating support device according to the present invention can increase the damping force during large displacement input or vibration in the low frequency range, and increase the damping force during vibration in the high frequency range. Transmission rate can be reduced.
第１図は防振支持装置の断面側面図、第２図は同要部の
断面平面図、第３図（ａ） 、 （ｂ） 、 （ｃ）は
規制部材の作動図、ｉ４図は第２実施例に係る規制部材
の断面図である。
尚図面中、（１）は防振支持装置、（３）、（５）は取
付部材、（７）は第１弾性体、 （１３）はダイヤプラ
ム、（３）は第１流体室、 （１５）は第２流体室、（
１８）は第２弾性体、 （２３）、（３３）は規制部材
である。
特 許 出 願 人 本田技研工業株式会社代理人
弁理士 下 １） 容一部同 弁理士
大 橋 邦 音間 弁理士 小
山 右同 弁理士 野 １）
茂ｂ
（Ｃ）
り３
３３Ａ １９Figure 1 is a cross-sectional side view of the vibration isolating support device, Figure 2 is a cross-sectional plan view of the main parts, Figures 3 (a), (b), and (c) are operation diagrams of the regulating member, and Figure i4 is the FIG. 7 is a sectional view of a regulating member according to a second embodiment. In the drawing, (1) is the vibration isolating support device, (3) and (5) are the mounting members, (7) is the first elastic body, (13) is the diaphragm, (3) is the first fluid chamber, ( 15) is the second fluid chamber, (
18) is a second elastic body, and (23) and (33) are regulating members. Patent applicant: Agent for Honda Motor Co., Ltd.
Patent Attorney Part 2 1) Patent Attorney
Kuni Ohashi Otoma Patent Attorney
Udo Yama Patent Attorney No 1)
Shigeru b (C) Ri3 33A 19
Claims (1)
体で画成された第１流体室と、 前記第１流体室に連通路を介して連通し、前記第１流体
室の容積変化に基いて容積が変化する第２流体室とを備
える防振支持装置において、前記第１流体室に前記第１
弾性体よりも変形容易な第２弾性体を臨ませ、 前記第２弾性体の変形量を可変制御する規制部材を設け
たことを特徴とする防振支持装置。[Scope of Claims] A first fluid chamber defined by a first elastic body that deforms based on relative displacement between the vibrating body and the support body; a second fluid chamber whose volume changes based on a change in volume of the first fluid chamber;
A vibration isolating support device, characterized in that a second elastic body that is easier to deform than the elastic body is provided, and a regulating member that variably controls the amount of deformation of the second elastic body is provided.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61083331A JPH0743002B2 (en) | 1986-04-10 | 1986-04-10 | Anti-vibration support device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61083331A JPH0743002B2 (en) | 1986-04-10 | 1986-04-10 | Anti-vibration support device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62242149A true JPS62242149A (en) | 1987-10-22 |
| JPH0743002B2 JPH0743002B2 (en) | 1995-05-15 |
Family
ID=13799445
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61083331A Expired - Lifetime JPH0743002B2 (en) | 1986-04-10 | 1986-04-10 | Anti-vibration support device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0743002B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10064769A1 (en) * | 2000-12-22 | 2002-08-29 | Contitech Luftfedersyst Gmbh | Hydro spring |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS591829A (en) * | 1982-06-28 | 1984-01-07 | Toyoda Gosei Co Ltd | Liquid-enclosing vibration-proof device |
| JPS5940032A (en) * | 1982-08-30 | 1984-03-05 | Toyota Motor Corp | Vibration isolator |
-
1986
- 1986-04-10 JP JP61083331A patent/JPH0743002B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS591829A (en) * | 1982-06-28 | 1984-01-07 | Toyoda Gosei Co Ltd | Liquid-enclosing vibration-proof device |
| JPS5940032A (en) * | 1982-08-30 | 1984-03-05 | Toyota Motor Corp | Vibration isolator |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10064769A1 (en) * | 2000-12-22 | 2002-08-29 | Contitech Luftfedersyst Gmbh | Hydro spring |
| EP1346167A1 (en) * | 2000-12-22 | 2003-09-24 | ContiTech Luftfedersysteme GmbH | Hydraulic spring |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0743002B2 (en) | 1995-05-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6422545B1 (en) | Vacuum actuated active decoupler mount | |
| JP4381333B2 (en) | Fluid filled vibration isolator | |
| GB2158182A (en) | A hydraulically damped rubber mounting | |
| JPH03149424A (en) | Mount provided with inertia track with adjustable length | |
| JPH0752436Y2 (en) | Controlled engine mount | |
| JPH0144938B2 (en) | ||
| US5887844A (en) | Fluid-sealed vibration isolating device | |
| JPH0689802B2 (en) | Dynamic vibration damper using inertial fluid | |
| JPH06103057B2 (en) | Fluid filled anti-vibration bush | |
| US20050236750A1 (en) | Assembly bearing with hydraulic damping | |
| JPS59231233A (en) | Vibration isolating device sealed with liquid | |
| JP4220107B2 (en) | Controlled liquid-filled vibration isolator | |
| JPS62242149A (en) | Elastic suspension device | |
| JPH05584Y2 (en) | ||
| US5681032A (en) | Engine mount with controllable rigidity | |
| JPS6165933A (en) | Anti-vibration support | |
| JPS60172744A (en) | Vibrationproof device containing fluid | |
| JP3035233B2 (en) | Liquid filled type vibration damping device | |
| KR20070048551A (en) | Engine mount in which fluid is enclosed | |
| JPS59110931A (en) | Hydrostatic vibration-proof device | |
| JPS62270841A (en) | Engine support device for automobile | |
| EP1371874B1 (en) | Hydraulic engine mounting | |
| JPS60184738A (en) | Hydraulic mount | |
| KR101167290B1 (en) | engin mount | |
| JP4210851B2 (en) | Fluid-filled engine mount for vehicles |