JPH0743002B2 - Anti-vibration support device - Google Patents
Anti-vibration support deviceInfo
- Publication number
- JPH0743002B2 JPH0743002B2 JP61083331A JP8333186A JPH0743002B2 JP H0743002 B2 JPH0743002 B2 JP H0743002B2 JP 61083331 A JP61083331 A JP 61083331A JP 8333186 A JP8333186 A JP 8333186A JP H0743002 B2 JPH0743002 B2 JP H0743002B2
- Authority
- JP
- Japan
- Prior art keywords
- elastic body
- fluid chamber
- vibration
- support device
- deformation
- 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 - Lifetime
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
- F16F13/10—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)
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。Description: TECHNICAL FIELD The present invention relates to a fluid-filled type vibration-damping support device suitable for use as a support device for an engine of an automobile.
（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) As a fluid-filled type vibration-damping support device for supporting an automobile engine, a first fluid chamber conventionally defined by a first elastic body that deforms based on relative displacement between a vibrating body and the support body. And the first
It is known to include a second fluid chamber that communicates with a fluid chamber via a communication passage and that has a second fluid chamber whose volume changes according to the volume change 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 an anti-vibration support device, the damping force should be increased when a large displacement is input such as when the vehicle suddenly starts or suddenly stops, or when the engine vibrates in the low frequency range, and the vibration transmissibility is reduced when the vibration occurs 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、高周波周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。(Problems to be Solved by the Invention) However, in the conventional device, when an attempt is made to set the cross-sectional area of the communication passage to be small and the damping force to be large, the dynamic spring constant becomes high, and the vibration transmissibility at the time of vibration in the high frequency range is increased. There is a problem that is difficult to reduce 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 a damping force during large displacement input or vibration in a low frequency range, and to vibrate during vibration in a high frequency range. An object is to provide an anti-vibration support device that can reduce the transmissibility.
（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、 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（19）の変形限度を可変制御する規制部
材（23）を設け、 前記規制部材（23）は回転自在に支持された軸状部材と
し、この軸状部材を前記第２弾性体（19）に当接してそ
の変形を規制するとともに、同軸状部材の外周面（23
A）には前記第２弾性体（19）によって空気室（27）を
画制するための凹部（25）を形成した。(Means for Solving the Problems) In order to achieve the above object, the present invention provides a second elastic body (19) that is easier to deform than the first elastic body (7) in the first fluid chamber (9). No, a regulating member (23) for variably controlling the deformation limit of the second elastic body (19) is provided, and the regulating member (23) is a rotatably supported shaft member, and the shaft member is 2 The elastic body (19) is brought into contact with the elastic body (19) to restrict its deformation, and at the same time, the outer peripheral surface (23
A recess (25) for defining the air chamber (27) is formed in A) by the second elastic body (19).
（作用） 軸状部材をなす規制部材（23）の回転角度に応じて第２
弾性体（19）の変形限度が変化されるので、上記回転角
度を選ぶことにより、大変位入力や低周波数域の振動時
には第２弾性体（19）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。(Operation) According to the rotation angle of the regulating member (23) forming the shaft-like member, the second
Since the deformation limit of the elastic body (19) is changed, by selecting the above rotation angle, the second elastic body (19) is not deformed at the time of large displacement input or vibration in the low frequency range, or the second elastic body (19 The amount of deformation of 19) is reduced and the damping force is increased by the fluid passing through the communication passageway (11).
高周波数域の振動時には第２弾性体（19）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。When vibrating in a high frequency range, the amount of deformation of the second elastic body (19) is increased, the pulsation in the first fluid chamber (9) caused by the vibration is relaxed, the dynamic spring constant is reduced, and the vibration transmissibility is reduced. .
（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 sectional side view of the anti-vibration supporting device, and FIG. 2 is a sectional plan view of the main part 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、両取付部材（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 an anti-vibration support device, (3) is a mounting member that is mounted on an engine that is a vibrating body, (5) is a mounting member that is mounted on a vehicle body that is a supporting body, and both mounting members (3), (5) The spaces are connected by a hollow elastic body (7) having a truncated cone shape,
A first fluid chamber (9) is defined by an elastic body (7) that is deformed 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 has a circular substrate portion (5A),
The outer peripheral portion (5B) is formed thickly on the outer periphery of the substrate portion (5A), and the orifice (11) is formed in the center of the substrate portion (5A).
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）とダイヤフラム（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 a 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) include: A second volume that changes based on a volume change of the first fluid chamber (9)
A fluid chamber (15) 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。Then, facing the first fluid chamber (9), the second elastic body (1
9) is provided.
前記第２弾性体（19）は取付部材（５）の外周部（5B）
内に配設し、第２弾性体（19）は外周部（5B）に形成し
た欠部（21）を介して半部を流体室（９）に臨ませる。The second elastic body (19) is the outer peripheral portion (5B) of the mounting member (5).
The second elastic body (19) is disposed inside, and a half portion of the second elastic body (19) faces the fluid chamber (9) through a notch (21) formed in the outer peripheral portion (5B).
前記第２弾性体（19）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 (19) is formed so that it can be deformed more easily than the first elastic body (7), and in the embodiment, an elastic material has an annular cross section.
前記第２弾性体（19）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。A regulating member (23) for regulating the deformation of the second elastic body (19) is inserted inside the second elastic body (19).
前記規制部材（23）は軸状を呈しスリーブ（24A），（2
4B）により回転自在に支持し、規制部材（23）の外周面
（23A）には欠部（21）に臨ませて凹部（25）を周方向
半部にわたって延出形成し、凹部（25）と第２弾性体
（19）とで基室（27）を画成する。The regulating member (23) has a shaft shape and has sleeves (24A), (2
4B) is rotatably supported, and the concave portion (25) is formed so as to extend over the circumferential half portion so as to face the cutout portion (21) on the outer peripheral surface (23A) of the regulating member (23), and the concave portion (25) is formed. And the second elastic body (19) define a base chamber (27).
実施例では第２弾性体（19）の耐久性を高めるため、第
２弾性体（19）と規制部材（23）を固着し、外周部（5
B）の支持孔（29）で第２弾性体（19）と規制部材（2
3）を回転自在に支持した。In the embodiment, in order to enhance the durability of the second elastic body (19), the second elastic body (19) and the regulating member (23) are fixed to each other, and the outer peripheral portion (5
The second elastic body (19) and the regulating member (2) are provided in the support hole (29) of B).
3) was 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 regulation 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）を欠部（21）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）の半部を欠部（21）
側に臨ませ、且つ周波数が高くなるにつれて軸部材（2
3）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）全体を欠部（21）側に臨ませ
るように構成する。The drive means (31) is operated on the basis of various operating parameters such as acceleration, engine speed, engine frequency, accelerator opening degree, etc., and when a large displacement is input, as shown in FIG. ), The outer peripheral surface (23A) faces the notch (21) side, and in the low frequency vibration range including idle rotation, as shown in FIG. 3 (b), a half of the recess (25) is notched ( twenty one)
The shaft member (2
3) is gradually rotated so that the entire concave portion (25) faces the notch (21) side in the high frequency vibration range as shown in FIG. 3 (c).
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（19）は規制部材（23）の外周面（23A）
により変形が阻止され、従って第１流体室（９）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 the present embodiment is configured as described above, when a large displacement is input, the second elastic body (19) has the outer peripheral surface (23A) of the regulating member (23).
Therefore, the deformation is prevented, so that a large damping force can be obtained by the fluid passing through the orifice (11) when the volume of the first fluid chamber (9) 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２弾性体（19）は凹部（25）の半部を介して
変形可能であり、第１流体室（９）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。When vibrating in the low frequency range, the second elastic body (19) can be deformed through the half of the recess (25) by the pulsation in the first fluid chamber (9), and the second fluid body (19) can be deformed in the first fluid chamber (9). The pulsation is weakened as compared with the case of the large displacement input, and a desired damping force can be generated by the fluid passing through the orifice (11).
更に、振動周波数が高くなるにつれて欠部（21）に臨む
凹部（25）の容積を増大させ、第２弾性体（19）の変形
し得る容積を増大して第１流体室（９）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（９）
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 recess (25) facing the notch (21) is increased, and the deformable volume of the second elastic body (19) is increased to increase the volume of the first fluid chamber (9). The pulsation is gradually relaxed and the dynamic spring constant is reduced. When vibrating in the high frequency range, the entire recess (25) causes the first fluid chamber (9) to move.
The pulsation in the inside can be relaxed and the vibration transmissibility can be made extremely small.
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（35）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
凹部（37）を流体室（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) having different depths are formed on the outer peripheral surface (33A) of the regulating member (33), and the outer peripheral surface (33A) is connected to the fluid chamber (9) when a large displacement is input. The concave portion (35) having a small depth is exposed to the fluid chamber (9) during vibration in the low frequency range, and the concave portion (37) having a large depth is exposed to the fluid chamber (9) during vibration in the high frequency range. No, the damping force and the vibration transmissibility were adjusted stepwise.
尚、実施例では第２弾性体（19）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 the embodiment, the second elastic body (19) and the regulating member (23),
Although the case where the (33) is fixed has been described, only the restricting members (23) and (33) may be rotated in the second elastic body (19), and the restricting members (23) and (33) are the shafts. You may make it move to a 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。Further, the structure of the restricting member for restricting the deformation of the second elastic body (19) is not limited to the shaft-like member as in the embodiment, and is 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、簡易な構成が可能な軸状部材をなす規制部材
の回転角度に応じて第２弾性体の変形限度が変化される
ので、上記回転角度を選ぶことにより、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することができ
る。(Effects of the Invention) As is apparent from the above description, according to the vibration isolating support device of the present invention, the deformation of the second elastic body according to the rotation angle of the restricting member that constitutes the shaft-shaped member that can be simply configured. Since the limit is changed, by selecting the above-mentioned rotation angle, it is possible to increase the damping force at the time of large displacement input or vibration in the low frequency range, and to reduce the vibration transmissibility at the time of vibration in the high frequency range.
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、第４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）はダイヤフラム、
（９）は第１流体室、（15）は第２流体室、（19）は第
２弾性体、25は凹部、27は空気室、（23），（33）は規
制部材である。FIG. 1 is a sectional side view of a vibration-proof support device, FIG. 2 is a sectional plan view of the same part, FIGS. 3 (a), (b), and (c) are operation views of a regulating member, and FIG. It is sectional drawing of the restricting member which concerns on 2nd Example. In the drawings, (1) is an anti-vibration support device, (3) and (5) are mounting members, (7) is a first elastic body, and (13) is a diaphragm.
(9) is a first fluid chamber, (15) is a second fluid chamber, (19) is a second elastic body, 25 is a recess, 27 is an air chamber, and (23) and (33) are restricting members.
Claims (1)
形する第１弾性体で画成された第１流体室と、前期第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
変化に基づ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弾性体の変形限度を可変制御
する規制部材を設け、前記規制部材は回転自在に支持さ
れた軸状部材とし、この軸状部材を前記第２弾性体に当
接してその変形を規制するとともに、同軸状部材の外周
面には前記第２弾性体によって空気室を画成するための
凹部を形成したことを特徴とする防振支持装置1. A first fluid chamber defined by a first elastic body that deforms based on relative displacement between a vibrating body and a support, and the first period of the first period.
An anti-vibration support device, comprising: a second fluid chamber that communicates with a fluid chamber via a communication passage and whose volume changes based on a volume change of the first fluid chamber, wherein the first elastic body is provided in the first fluid chamber. The second that is easier to transform than
A restricting member that variably controls the deformation limit of the second elastic body is provided so as to face the elastic body, and the restricting member is a rotatably supported shaft member, and the shaft member contacts the second elastic body. The vibration-isolating support device is characterized in that the second elastic member forms a recess for defining an air chamber on the outer peripheral surface of the coaxial member while contacting with each other to restrict its deformation.
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 JPS62242149A (en) | 1987-10-22 |
| JPH0743002B2 true 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) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10064769A1 (en) * | 2000-12-22 | 2002-08-29 | Contitech Luftfedersyst Gmbh | Hydro spring |
Family Cites Families (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
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62242149A (en) | 1987-10-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4583723A (en) | Elastically damping device for suspension of engine | |
| JPH0247614B2 (en) | ||
| JP3035222B2 (en) | Liquid filled type vibration damping device | |
| JPH0689802B2 (en) | Dynamic vibration damper using inertial fluid | |
| JPS59231233A (en) | Vibration isolating device sealed with liquid | |
| JP4220107B2 (en) | Controlled liquid-filled vibration isolator | |
| JP3978537B2 (en) | Fluid filled vibration isolator | |
| JPH0743002B2 (en) | Anti-vibration support device | |
| JPH01224544A (en) | Fluid seal type vibrationproof device | |
| JPH05584Y2 (en) | ||
| JPH03125045A (en) | Liquid damping type vibration isolator | |
| JP2944470B2 (en) | Liquid sealing rubber device | |
| JPH08240242A (en) | Engine mount | |
| JPS59110931A (en) | Hydrostatic vibration-proof device | |
| JPS60172744A (en) | Vibrationproof device containing fluid | |
| JPH0247615B2 (en) | ||
| JPS62228726A (en) | Valve device of liquid-filled type insulator | |
| JPH0222515Y2 (en) | ||
| JPH05248482A (en) | Liquid-sealed type mount | |
| JP3088686B2 (en) | Liquid filled type vibration damping device | |
| US6634629B1 (en) | Hydraulic engine mounting | |
| US5088699A (en) | Electrorheopectic fluid filled vibration damping mount for use with automotive engines and the like | |
| JPH0222514Y2 (en) | ||
| JPS59194141A (en) | Liquid enclosed vibration damper | |
| JPH0739696Y2 (en) | Center bearing support |