JPS6352260B2 - - Google Patents
Info
- Publication number
- JPS6352260B2 JPS6352260B2 JP55168540A JP16854080A JPS6352260B2 JP S6352260 B2 JPS6352260 B2 JP S6352260B2 JP 55168540 A JP55168540 A JP 55168540A JP 16854080 A JP16854080 A JP 16854080A JP S6352260 B2 JPS6352260 B2 JP S6352260B2
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- orifice
- diaphragm
- vibration
- lower 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
Links
- 239000012530 fluid Substances 0.000 claims description 16
- 239000012212 insulator Substances 0.000 claims description 15
- 238000005192 partition Methods 0.000 claims description 5
- 238000013016 damping Methods 0.000 description 20
- 230000000694 effects Effects 0.000 description 11
- 239000007788 liquid Substances 0.000 description 5
- 238000002955 isolation Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000003068 static effect Effects 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
- 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
- F16F13/20—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 characterised by comprising also a pneumatic spring
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】
本発明は防振支持装置、とりわけ自動車用エン
ジンマウントとして用いて好適な防振支持装置に
関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibration isolating support device, particularly to a vibration isolating support device suitable for use as an engine mount for an automobile.
第1図は従来の自動車用エンジンマウントとし
て用いられている防振支持装置を示すもので、1
はエンジン側に取付く上側フランジ、2はシヤシ
側に取付く下側フランジで、これら上下フランジ
1,2は円筒状のインシユレータラバー3で連結
してこれら両者間に密閉室を形成している。この
密閉室は上側フランジ1に固設した複数個のオリ
フイス5を有する仕切板4により上部室6と下部
室7とに隔成してあり、かつ上部室6の一部に空
隙6aを残して上下室6,7に流体8を充填して
ある。インシユレータラバー3の中央部外周には
径方向の変形を防止する中間リング9を設けてあ
る。この防振支持装置は下側フランジ2をスタツ
ドボルト10を介して図外のシヤシに締結する一
方、上側フランジ1をスタツドボルト11を介し
て図外のエンジンに締結して、エンジンとシヤシ
との間に介装配置される。 Figure 1 shows a vibration isolating support device used as a conventional automobile engine mount.
2 is an upper flange attached to the engine side, and 2 is a lower flange attached to the chassis side. These upper and lower flanges 1 and 2 are connected by a cylindrical insulator rubber 3 to form a sealed chamber between them. There is. This sealed chamber is separated into an upper chamber 6 and a lower chamber 7 by a partition plate 4 having a plurality of orifices 5 fixed to the upper flange 1, and a gap 6a is left in a part of the upper chamber 6. The upper and lower chambers 6 and 7 are filled with a fluid 8. An intermediate ring 9 is provided on the outer periphery of the central portion of the insulator rubber 3 to prevent deformation in the radial direction. This anti-vibration support device has a lower flange 2 fastened to a chassis (not shown) via stud bolts 10, and an upper flange 1 fastened to an engine (not shown) via stud bolts 11 to connect the engine and the chassis. An intervening device is placed in between.
この防振支持装置によれば、エンジン側あるい
はシヤシ側からの振動入力はインシユレータラバ
ー3を弾性変形させて下部室7の容積変化をもた
らす。この下部室7の容積変化により該下部室7
の内圧が上昇し、下部室7内の流体が上部室6に
移動し、この時の流体8がオリフイス5を通過す
る際の流体緩衝により振動減衰効果が得られる。 According to this vibration isolating support device, vibration input from the engine side or the chassis side causes the insulator rubber 3 to elastically deform, resulting in a change in the volume of the lower chamber 7. Due to this change in the volume of the lower chamber 7, the lower chamber 7
The internal pressure of the lower chamber 7 increases, and the fluid in the lower chamber 7 moves to the upper chamber 6. At this time, when the fluid 8 passes through the orifice 5, a vibration damping effect is obtained by the fluid buffering.
ところが、かかる従来の構造では前述の減衰効
果は流体8のオリフイス5通過速度によつて決定
されるのであるが、該オリフイス5径は制振領域
での低周波振動に対して十分な減衰効果が得られ
るように設定する必要があるが、高周波振動に移
行する過程において、該減衰は極大値を有した後
減少し、それに付随して防振支持装置の動ばね剛
性上昇の不利が現われる。というのは、周波数が
高くなるにつれて液体がオリフイスを通過する抵
抗が次第に大きくなり、オリフイス通過液の量、
速度とも低下し、遂にオリフイスを通過する抵抗
が液体室壁の変形抵抗よりも大きくなると、液体
室壁がへこんでオリフイスを通過して排除すべき
液体の一部を受容することによつて現われるもの
である。また、該防振領域で振動伝達率が大とな
つて車内騒音低減効果が損なわれてしまう問題が
あつた。また、前述のように上下フランジ1,2
間を密閉してあるためエンジン荷重の静的負荷に
よる内圧上昇がインシユレータラバー3のばね定
数に加えられることから、全体としてばね定数が
大となり、これも防振特性を損なう要因ともなつ
ていた。 However, in such a conventional structure, the above-mentioned damping effect is determined by the velocity of the fluid 8 passing through the orifice 5, but the diameter of the orifice 5 does not have a sufficient damping effect against low-frequency vibrations in the damping region. However, in the process of transitioning to high-frequency vibrations, the damping reaches a maximum value and then decreases, accompanied by the disadvantage of an increase in the stiffness of the dynamic spring of the vibration isolating support device. This is because as the frequency increases, the resistance for liquid to pass through the orifice gradually increases, and the amount of liquid passing through the orifice increases.
The velocity also decreases, and when the resistance to passing through the orifice becomes greater than the deformation resistance of the liquid chamber wall, the liquid chamber wall dents and accepts some of the liquid that should pass through the orifice and be removed. It is. Further, there is a problem in that the vibration transmission rate becomes large in the vibration isolation region, and the effect of reducing noise inside the vehicle is impaired. In addition, as mentioned above, the upper and lower flanges 1 and 2
Since the space is sealed, the increase in internal pressure due to the static load of the engine is added to the spring constant of the insulator rubber 3, resulting in a large spring constant as a whole, which is also a factor that impairs the anti-vibration properties. Ta.
本発明はかかる従来の実状に鑑み、下部室にダ
イヤフラムを形成して、該ダイヤフラムと下側フ
ランジとの間に所定のクリアランスを設定するこ
とにより、低周波振動の大振巾領域では下部室か
ら上部室への流体のオリフイス通過移動により大
きな振動減衰効果が得られて適切な制振特性を発
揮でき、そして、高周波振動の防振領域では下部
室の容積変化をダイヤフラムの伸縮作用で吸収し
て流体のオリフイス通過移動を抑え、以て振動減
衰効果を小とし、全体としてばね定数を小さくし
て防振特性を十分に発揮でき、簡易構成にして制
振特性と防振特性の両立を図ることのできる防振
装置を提供するものである。 In view of the conventional situation, the present invention forms a diaphragm in the lower chamber and sets a predetermined clearance between the diaphragm and the lower flange. By moving the fluid through the orifice to the upper chamber, a large vibration damping effect can be obtained and appropriate vibration damping characteristics can be achieved, and in the vibration isolation region of high frequency vibration, volume changes in the lower chamber are absorbed by the expansion and contraction action of the diaphragm. To suppress the movement of fluid through an orifice, thereby reducing the vibration damping effect, to reduce the spring constant as a whole to fully exhibit vibration damping characteristics, and to achieve both vibration damping characteristics and vibration damping characteristics with a simple configuration. The purpose of this invention is to provide a vibration isolating device that is capable of
以下、本発明の実施例を図面と共に前記従来の
構成と同一部分に同一符号を付して詳述する。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings, in which the same parts as those of the conventional structure are denoted by the same reference numerals.
第2図に示す実施例において、上側フランジ1
と下側フランジ2は、中央部外周に径方向の変形
防止用の中間リング9を設けた円筒状のインシユ
レータラバー3で連結してある。下側フランジ2
は中央に開口部2aを有し、スタツドボルト10
を介して結合したリテーナプレート20もしくは
シヤシにより開口部2aを閉塞して段部21を形
成している。ここで下側フランジ2はこのように
開口部2aを設けることなく予め厚肉にして中央
部に段部を形成するようにしてもよい。円筒状の
インシユレータラバー3内は1個または複数個の
オリフイス5を有する仕切板4で上部室6と下部
室7とに隔成してある。また、下部室7の底部に
はインシユレータラバー3と一体にダイヤフラム
22を形成してあり、この下部室7と上部室6と
に該上部室6の一部に空隙6aを残して流体8を
充填してある。ダイヤフラム22と下側フランジ
2の段部21との間には所定のクリアランス23
を設定してある。クリアランス23は例えば第3
図に示すようにダイヤフラム22の底面に突起2
2aを一体成形して確保することができる。この
クリアランス23は後述する高周波振動に対して
ダイヤフラム22が若干伸張し得るに足る程度で
よく、およそ1m/m以下でよい。 In the embodiment shown in FIG.
and the lower flange 2 are connected by a cylindrical insulator rubber 3 provided with an intermediate ring 9 for preventing radial deformation on the outer periphery of the central portion. Lower flange 2
has an opening 2a in the center, and a stud bolt 10
A stepped portion 21 is formed by closing the opening 2a with a retainer plate 20 or a chassis connected via a retainer plate 20 or a chassis. Here, the lower flange 2 may be made thicker in advance without providing the opening 2a as described above, and may have a stepped portion formed in the center. The inside of the cylindrical insulator rubber 3 is separated into an upper chamber 6 and a lower chamber 7 by a partition plate 4 having one or more orifices 5. Further, a diaphragm 22 is formed integrally with the insulator rubber 3 at the bottom of the lower chamber 7, and a gap 6a is left in a part of the upper chamber 6 between the lower chamber 7 and the upper chamber 6 to allow fluid 8. It is filled with. A predetermined clearance 23 is provided between the diaphragm 22 and the stepped portion 21 of the lower flange 2.
has been set. The clearance 23 is, for example, the third
As shown in the figure, there are protrusions 2 on the bottom of the diaphragm 22.
2a can be secured by integrally molding. The clearance 23 may be sufficient to allow the diaphragm 22 to expand slightly against high-frequency vibrations to be described later, and may be approximately 1 m/m or less.
なお、下側フランジ2は第4図に示すように段
部を形成することなくフラツトな状態に成形し、
ダイヤフラム22をインシユレータラバー3底部
の若干上方に一体成形してクリアランス23を設
定するようにしてもよい。 Note that the lower flange 2 is formed into a flat state without forming a step as shown in FIG.
The clearance 23 may be set by integrally molding the diaphragm 22 slightly above the bottom of the insulator rubber 3.
以上の実施例構造によれば、高周波振動の防振
領域ではインシユレータラバー3の大きな変形は
ないが、下部室7の流体8は仕切板4のオリフイ
ス5を通過して容積変化しようとする傾向にあ
る。ところが、下部室7の内圧上昇は速やかにダ
イヤフラム22に影響して該ダイヤフラム22を
伸張させる。この結果、下部室7内の容積変化は
該ダイヤフラム22で吸収され、流体8がオリフ
イス5を流通するのを回避し、以て振動減衰作用
を可及的に小さく抑え、良好な振動特性を得るこ
とができるのである。 According to the structure of the embodiment described above, in the high-frequency vibration isolation region, there is no major deformation of the insulator rubber 3, but the fluid 8 in the lower chamber 7 passes through the orifice 5 of the partition plate 4 and attempts to change its volume. There is a tendency. However, the rise in internal pressure in the lower chamber 7 quickly affects the diaphragm 22 and causes it to expand. As a result, the volume change in the lower chamber 7 is absorbed by the diaphragm 22, and the fluid 8 is prevented from flowing through the orifice 5, thereby minimizing the vibration damping effect and obtaining good vibration characteristics. It is possible.
一方、低周波大振巾の制振領域ではインシユレ
ータラバー3の変形が大きく、ダイヤフラム22
が下側フランジ2に密着して、所謂底付きを生じ
るため、下部室7内の流体8はオリフイス5を通
過して上部室6側に移動して該下部室7は容積変
化し、この時の流体8のオリフイス5通過によつ
て大きな振動減衰効果を発揮し、良好な制振特性
が得られるのである。 On the other hand, in the damping region of low frequency and large amplitude, the deformation of the insulator rubber 3 is large and the diaphragm 22
Because the fluid 8 in the lower chamber 7 passes through the orifice 5 and moves toward the upper chamber 6, the volume of the lower chamber 7 changes, and at this time, the lower chamber 7 changes in volume. By passing the fluid 8 through the orifice 5, a large vibration damping effect is exhibited, and good vibration damping characteristics are obtained.
以上のように本発明によれば、高周波振動に対
しては下部室底部に設けたダイヤフラムの伸縮に
より、該下部室の容積変化を吸収し、流体のオリ
フイス通過を抑制できるため振動減衰作用を小と
して殆どインシユレータラバーのみの小さなばね
定数が得られ、防振特性を十分に発揮できるもの
であり、そして、低周波大振巾に対しては下部室
の流体をオリフイスに通過させて大きな減衰効果
を発揮させ制振特性を十分に得ることができ、仍
つて、簡易構成でありながら防振特性と制振特性
の両立を図ることができるという実用上優れた効
果を有する。 As described above, according to the present invention, in response to high-frequency vibrations, the diaphragm provided at the bottom of the lower chamber expands and contracts to absorb changes in the volume of the lower chamber and suppress fluid passage through the orifice, thereby reducing the vibration damping effect. As a result, a small spring constant can be obtained almost exclusively from the insulator rubber, which can sufficiently exhibit vibration isolation characteristics.In addition, for low frequency and large amplitude, the fluid in the lower chamber is passed through the orifice to achieve large damping. The present invention has excellent practical effects in that it is possible to exhibit the effect and obtain sufficient vibration damping characteristics, and to achieve both vibration damping characteristics and vibration damping characteristics despite the simple configuration.
第1図は従来の装置を示す断面図、第2図は本
発明装置を示す断面図、第3図は同要部の拡大
図、第4図は本発明の異なる例を示す断面図であ
る。
1……上側フランジ、2……下側フランジ、3
……インシユレータラバー、4……仕切板、5…
…オリフイス、6……上部室、7……下部室、8
……流体、22……ダイヤフラム、23……クリ
アランス。
FIG. 1 is a sectional view showing a conventional device, FIG. 2 is a sectional view showing the device of the present invention, FIG. 3 is an enlarged view of the same essential parts, and FIG. 4 is a sectional view showing a different example of the present invention. . 1...Upper flange, 2...Lower flange, 3
...Insulator rubber, 4...Partition plate, 5...
...Orifice, 6...Upper chamber, 7...Lower chamber, 8
...Fluid, 22...Diaphragm, 23...Clearance.
Claims (1)
シユレータラバーで連結し、かつ該インシユレー
タラバー内の空間をオリフイスを有する仕切板で
上下2部室に隔成すると共に、下部室の底部に前
記インシユレータラバーと一体にダイヤフラムを
形成し、上部室の一部に空隙を残して上下2部室
に流体を充填すると共に、前記ダイヤフラムと、
前記下側フランジまたは前記下側フランジの段部
との間に、所定のクリアランスを設定したことを
特徴とする防振支持装置。1. The lower flange and the upper flange are connected by a cylindrical insulator rubber, and the space inside the insulator rubber is divided into upper and lower chambers by a partition plate having an orifice, and at the bottom of the lower chamber A diaphragm is formed integrally with the insulator rubber, and the upper and lower chambers are filled with fluid leaving a gap in a part of the upper chamber, and the diaphragm and
A vibration isolating support device characterized in that a predetermined clearance is set between the lower flange or the stepped portion of the lower flange.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP16854080A JPS5794144A (en) | 1980-11-29 | 1980-11-29 | Anti-vibration supporting device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP16854080A JPS5794144A (en) | 1980-11-29 | 1980-11-29 | Anti-vibration supporting device |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP21223987A Division JPS63167140A (en) | 1987-08-26 | 1987-08-26 | Vibration isolating support structure |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS5794144A JPS5794144A (en) | 1982-06-11 |
JPS6352260B2 true JPS6352260B2 (en) | 1988-10-18 |
Family
ID=15869901
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP16854080A Granted JPS5794144A (en) | 1980-11-29 | 1980-11-29 | Anti-vibration supporting device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5794144A (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS57130827A (en) * | 1981-02-02 | 1982-08-13 | Nissan Motor Co Ltd | Engine mount device containing fluid |
JPS5830545A (en) * | 1981-08-17 | 1983-02-23 | Nissan Motor Co Ltd | Antivibration body |
JPS60215134A (en) * | 1984-04-10 | 1985-10-28 | Bridgestone Corp | Vibration isolating device |
JPH0649405B2 (en) * | 1984-08-06 | 1994-06-29 | マツダ株式会社 | Rear suspension device for automobile |
FR2710957B1 (en) * | 1993-10-05 | 1995-12-08 | Hutchinson | Improvements to hydraulic anti-vibration supports. |
JP5702250B2 (en) * | 2011-08-08 | 2015-04-15 | 東洋ゴム工業株式会社 | Liquid-filled vibration isolator |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS55109840A (en) * | 1979-02-17 | 1980-08-23 | Tokai Rubber Ind Ltd | Antivibration holder |
-
1980
- 1980-11-29 JP JP16854080A patent/JPS5794144A/en active Granted
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS55109840A (en) * | 1979-02-17 | 1980-08-23 | Tokai Rubber Ind Ltd | Antivibration holder |
Also Published As
Publication number | Publication date |
---|---|
JPS5794144A (en) | 1982-06-11 |
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