JPS5993537A - Liquid charged vibration absorbing device - Google Patents
Liquid charged vibration absorbing deviceInfo
- Publication number
- JPS5993537A JPS5993537A JP20420982A JP20420982A JPS5993537A JP S5993537 A JPS5993537 A JP S5993537A JP 20420982 A JP20420982 A JP 20420982A JP 20420982 A JP20420982 A JP 20420982A JP S5993537 A JPS5993537 A JP S5993537A
- Authority
- JP
- Japan
- Prior art keywords
- fluid
- holes
- partition plate
- hole
- fluid 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.)
- Pending
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
- F16F13/26—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 characterised by adjusting or regulating devices responsive to exterior conditions
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】
本発明は車両用エンジンマウントに使用する防振装置で
あって、絞り孔を設けた仕切板で区分された厚肉ゴム弾
性体壁よりなる第１の？７１を体室および薄肉ゴム弾性
体シートよりなる第２の流体室を有し、振動が作用して
上記第１の流体室が父形した時に、仕切板の上記絞υ孔
を封入液体が流通することによシ振動の減設作用をなす
液封入防振装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention is a vibration isolating device for use in a vehicle engine mount, and includes a first vibration damping device comprising a thick rubber elastic wall partitioned by a partition plate provided with aperture holes. 71 has a body chamber and a second fluid chamber made of a thin rubber elastic sheet, and when the first fluid chamber becomes father-shaped due to vibration, the liquid enclosed in the diaphragm hole of the partition plate flows. The present invention relates to a liquid-filled vibration isolator that reduces vibration by doing so.
エンジンの共振周波数は通常１０Ｈｚ前後の低周波領域
にあって、エンジンの低速回転時にエンジンマウントの
振動振幅は最も大きくなり、回転数の上昇にしたがって
小さくなる。低周波振動の車体への伝達を低減せしめて
乗シ心地を良くするためには、上記防振装置は低周波の
制振領域にて大きな減衰係数を有する必要がある。The resonant frequency of an engine is usually in a low frequency region of around 10 Hz, and the vibration amplitude of the engine mount is greatest when the engine rotates at low speed, and decreases as the rotation speed increases. In order to reduce transmission of low frequency vibrations to the vehicle body and improve riding comfort, the vibration isolator needs to have a large damping coefficient in the low frequency vibration damping region.
また、走行中に路面から受ける低周波の振動によりエン
ジンマウントの共振振動を起こさせないだめにも同様に
制振領域での減衰係数は大きいす１うが良い。同様の目
的で制振領域では装置のバネ定数も大きくする必要があ
る。Further, in order to prevent resonance vibration of the engine mount due to low-frequency vibrations received from the road surface during driving, it is preferable that the damping coefficient in the damping region be large. For the same purpose, it is also necessary to increase the spring constant of the device in the damping region.
関連回転時のエンジン振動は小さいが、この高周波振動
は可聴領域にあるため、振動が車体に伝達されると車内
騒音が大きくなる。この高周波の防振領域における振動
の伝達を防止するだめには上記防振装置の防振領域にお
ける減衰係数を小さくする必要がある。同様の目的で防
振領域では装置のバネ定数も小さくする必要がある。Although the engine vibration during the relevant rotation is small, this high-frequency vibration is in the audible range, so when the vibration is transmitted to the car body, the noise inside the car increases. In order to prevent the transmission of vibrations in the high frequency vibration isolation area, it is necessary to reduce the damping coefficient in the vibration isolation area of the vibration isolator. For the same purpose, it is also necessary to reduce the spring constant of the device in the vibration isolation area.
このだめ、防振装置を低周波の制振領域に適応するよう
にバネ定数を大きく設計すると、高周波の防振領域では
バネ定数が大きくなり過ぎ、充分な防振効果が得られな
いという間通があつそこで、本発明は低周波領域では高
いバネ定数を示すとともに減衰作用が発揮されて有効に
制振作用をなし、高周波領域では減数作用を少なくする
とともに低いバネ定数を示して有効に防振作用をなす液
封入防振装置を提供することを目的とするものである。To avoid this, if the vibration isolator is designed with a large spring constant to adapt to the low-frequency vibration damping region, the spring constant will become too large in the high-frequency vibration damping region, and a sufficient vibration damping effect cannot be obtained. However, in the low frequency range, the present invention exhibits a high spring constant and exhibits a damping effect to effectively dampen vibrations, and in the high frequency range, it reduces the reduction effect and exhibits a low spring constant to effectively dampen vibrations. It is an object of the present invention to provide a liquid-filled vibration isolator that is effective.
すなわち、本発明では仕切板に絞り孔とこれよシも流通
抵抗の小さい通孔を設け、低周波振動時には第２の流体
室の薄肉ゴム弾性体壁の一部を移動せしめて上記通孔を
閉塞し、高周波振動時には上記通孔を開放するようにし
だものである。That is, in the present invention, the partition plate is provided with a through hole that has a smaller flow resistance than the throttle hole, and at the time of low frequency vibration, a part of the thin rubber elastic wall of the second fluid chamber is moved to close the through hole. The through hole is closed and opened during high frequency vibration.
しかして、本発明の液封入防振装置によれば、低周波大
振幅時には密封流体を絞シ孔に流通せしめて減衰作用が
なされ、高周波小振幅時には通孔によシ密封流体は第２
の流体室に自由に流通し、該流体室の薄肉ゴム弾性体壁
によシ第１の流体室の液圧変化が吸収されて、バネ定数
が小さくなる。According to the liquid-filled vibration isolator of the present invention, when a low frequency and a large amplitude occur, the sealing fluid is caused to flow through the constriction hole to provide a damping effect, and when a high frequency and a small amplitude occur, the sealing fluid is passed through the throughhole and a damping effect is achieved.
The fluid flows freely through the first fluid chamber, and changes in the fluid pressure in the first fluid chamber are absorbed by the thin rubber elastic wall of the fluid chamber, reducing the spring constant.
以下、図示の実施例により本発明を説明する。The present invention will be explained below with reference to illustrated embodiments.
図において、１はエンジンの荷車を受ける厚゛ 丙の
ゴム弾性体壁で、下方に凹状をなす椀状体である。ゴム
弾性体壁１の頂部は平面に形成され、この頂面に円板状
の上板２が接合しである。In the figure, reference numeral 1 denotes a thick rubber elastic wall that receives the engine cart, and is a bowl-shaped body that is concave downward. The top of the rubber elastic wall 1 is formed into a flat surface, and a disk-shaped upper plate 2 is joined to this top surface.
上板２の中心にはボ／Ｌ／ ト８が挿通立設してあシ、
これにより、エンジンが載置固定される。A bolt 8 is inserted and stands in the center of the upper plate 2.
As a result, the engine is placed and fixed.
上記ゴム弾性体壁ｌの外周面には側板３の円筒部が接合
しである。側板３のフランジ部には抜き穴３１が設けて
あり、これにボｌレトを挿通してＭ ｉｉｆ本体がボデ
ーに固定される。側板３の円筒部の下方にはこれを受け
るように容器状の底板が固定し−Ｃある。Ｉｆ板４の中
央部上面にはベローｑが設けである。ペローｑ内にはＩ
ｆ板４の中央に設けた抜き穴を押通する油圧供給管７１
の先端が開口しており、油圧を供給することによりベロ
ー７は上方へ伸張する。なお、上記油厘゛ｉマへの給排
油はエンジン回転数あるいはエンジンとボデーの相対反
位よジエンジンの振動数を検知する図示しない制御装置
により行なわれる。A cylindrical portion of the side plate 3 is joined to the outer peripheral surface of the rubber elastic wall 1. A punch hole 31 is provided in the flange portion of the side plate 3, and a bolt is inserted through this hole to fix the M iif main body to the body. A container-shaped bottom plate is fixed to the lower side of the cylindrical portion of the side plate 3 so as to receive the cylindrical portion. A bellows q is provided on the upper surface of the central portion of the If plate 4. I is in Perot q
Hydraulic supply pipe 71 that is pushed through the hole provided in the center of the f plate 4
The tip of the bellows 7 is open, and the bellows 7 extends upward by supplying hydraulic pressure. The supply and discharge of oil to and from the oil tank is carried out by a control device (not shown) that detects the engine rotational speed or the vibration frequency of the engine due to the relative displacement between the engine and the body.
５は薄肉のゴム弾性体シートで、その中心部下面は上記
ベロー７の上面に接合しである。上記中心部には強化用
の円板部材９が埋設しである。ゴム弾性体シート５の周
縁は底板４の上端縁部に形成した段付部と仕切板６の外
周部との間に挟着せしめてあシ、周縁挟着部とベロー７
で支持された中心部との間は垂れ下がっている。Reference numeral 5 denotes a thin rubber elastic sheet whose central lower surface is joined to the upper surface of the bellows 7. A reinforcing disk member 9 is embedded in the center. The peripheral edge of the rubber elastic sheet 5 is sandwiched between the stepped part formed on the upper edge of the bottom plate 4 and the outer periphery of the partition plate 6.
There is a sag between the center supported by.
仕切板６には上記ゴム弾性体シート５の中心部に対応し
た中心部に複数の通孔６１が形成しである。また仕切板
６はゴム弾性体シート５の垂下部に対向する環状部が下
方へ膨出する厚肉部としてあり、この厚肉部には絞り孔
６２が径方向対称位置に２個形成しである。この仕切板
６によシ、厚肉ゴム弾性体壁ｌを室壁とする第１の流体
室Ａと薄肉ゴム弾性体シートを室壁とする第２の流体室
Ｂが分割形成される。A plurality of through holes 61 are formed in the partition plate 6 at a center corresponding to the center of the rubber elastic sheet 5. In addition, the partition plate 6 has a thick walled portion in which an annular portion facing the hanging portion of the rubber elastic sheet 5 bulges downward, and two throttle holes 62 are formed at radially symmetrical positions in this thick walled portion. be. Through this partition plate 6, a first fluid chamber A having a thick rubber elastic material wall 1 as a chamber wall and a second fluid chamber B having a chamber wall having a thin rubber elastic material sheet are dividedly formed.
上記の如き構成を有する防振装置の作動を以下に説明す
る。The operation of the vibration isolator having the above configuration will be explained below.
低周波の制振領域では制御装置によシ上記ぺローフに油
圧を供給し、上方に伸張せしめる。In the low-frequency damping region, the control device supplies hydraulic pressure to the above-mentioned perov to cause it to extend upward.
これにより、ベロー７で支持されたゴム弾性体シート５
の中心部はこれに対応する仕切板６０下面中心部に轟接
し、通孔６１は全て閉塞される。この状態では両流体室
Ａ％Ｂは小径の絞シイＬ６２のみで連通しており、振動
により第１の流体室Ａが変形すると、流体室Ａの内圧は
急速に上Ｊｊトシ、装置のバネ定数が大きくなる。また
、この時絞り孔６２を流通する密封液体は大きな流ＪＩ
ｎ抵抗を受け、装置の減衰係数も大きくなる。As a result, the rubber elastic sheet 5 supported by the bellows 7
The center portion of the partition plate 60 comes into contact with the center portion of the lower surface of the corresponding partition plate 60, and all of the through holes 61 are closed. In this state, both fluid chambers A%B are in communication with each other only through the small-diameter restrictor L62, and when the first fluid chamber A deforms due to vibration, the internal pressure of the fluid chamber A rapidly increases and the spring constant of the device increases. becomes larger. Also, at this time, the sealing liquid flowing through the throttle hole 62 has a large flow JI.
Due to the n resistance, the damping coefficient of the device also increases.
晶周波の防振領域では上記ベロー７の油圧を抜く。これ
により、ベロー７は下方へ収縮して（図示の状態）、ゴ
ム弾性体シート５が仕切板６より離れるから、上記両流
体室Ａ、Ｂは仕切板６に形成された複数の通孔６１によ
り連通せしめられる。この状態では密封流体はほとんど
抵抗なく両流体室Ａ、Ｂ間を流通することができ、振動
により第１の流体室Ａが変形しても、流体室Ａ中の密封
流体は流通抵抗を受けることなく速やかに第２の流体室
Ｂに流通する。したかって減衰係数は小さく、かつ第１
の流体室Ａの内圧は振動振幅の減少に伴なって速やかに
小さくなるから、バネ定数も小さくなる。In the vibration isolation region of the crystal frequency, the hydraulic pressure of the bellows 7 is removed. As a result, the bellows 7 contracts downward (the state shown in the figure), and the rubber elastic sheet 5 separates from the partition plate 6, so that both fluid chambers A and B are connected to the plurality of through holes 61 formed in the partition plate 6. communication is established. In this state, the sealing fluid can flow between both fluid chambers A and B with almost no resistance, and even if the first fluid chamber A is deformed due to vibration, the sealing fluid in fluid chamber A will not experience any flow resistance. The fluid quickly flows to the second fluid chamber B without any problems. Therefore, the damping coefficient is small and the first
Since the internal pressure of the fluid chamber A quickly decreases as the vibration amplitude decreases, the spring constant also decreases.
上記装置のエンジン側、ポデー側は実施例と反対として
ももちろん良い。Of course, the engine side and the podium side of the above device may be opposite to those in the embodiment.
以上の如く、本発明の防振装置は低周波の制振領域では
減衰係数、バネ定数をともに大きくし、高周波の防振領
域ではともに小さくして、エンジンの低速回転から高速
回転に至る単体への振動伝達を低減せしめて、車両の居
住性の改善および走行性能の大縣な向上を実現したもの
である。As described above, the vibration isolator of the present invention increases both the damping coefficient and the spring constant in the low frequency vibration damping region, and decreases both in the high frequency vibration damping region. By reducing vibration transmission, the vehicle's comfort and driving performance are significantly improved.
図は防振装置の半断面図である。 Ａ・・・・・−第１の流体室 Ｂ・・・・・・第２の流体室 １・・・・・・厚肉ゴム弾性体壁 ５・・・・・・薄肉ゴム弾性体シート ６・・・・・・仕切板 ６１・・・・・・通 孔 ６２・・・・・・絞り孔 ７・・・・・・ベロー The figure is a half sectional view of the vibration isolator. A...--first fluid chamber B...Second fluid chamber 1... Thick rubber elastic wall 5... Thin rubber elastic sheet 6... Partition plate 61・・・Through hole 62...Aperture hole 7...Bello
Claims (2)
イと、薄肉のゴム弾性体壁・よりなり絞シ孔を有する仕
切板で第１の流体室と仕切られた第２の流体室とを備え
、上記厚肉ゴム弾性体壁に支持された被支持体の振動に
より上記両流体室の容積が＋１１．７１’ ＆化して、
上記絞シ孔を辿って封入液体が流化するようになしだ液
封入防振装置において、仕切板には上記絞シ孔と共にこ
れよりも流血抵抗の小さい通孔を設け、上記第２の流体
室のゴｌ、弾性体壁の背面側には該壁の上記通孔と対向
する部分を仕切板方向へ支持するとともに上下動可能な
支持部材を設け、低周波大振幅時には支持部材を上昇せ
しめて薄肉のゴム弾性体壁により仕切板の上記通孔を閉
塞して上記絞り孔に流体を流通せしめ、高周波小振幅時
には支持部材を下降せしめて上記通孔を開口せしめてこ
れによシ流体を流通せしめるようになしたことを特徴と
する液封入防振装置。(1) The first fluid layer consists of a thick rubber elastic wall.
and a second fluid chamber separated from the first fluid chamber by a thin rubber elastic wall and a partition plate having a constriction hole, and the second fluid chamber is supported by the thick rubber elastic wall. Due to the vibration of the support, the volumes of both fluid chambers become +11.71'&,
In the liquid-filled vibration isolator, the liquid enclosed in the vibration isolator is configured to flow along the squeeze holes, and the partition plate is provided with a through hole having a smaller blood flow resistance together with the squeeze holes, so that the second fluid flows through the partition plate. On the rear side of the elastic wall of the chamber, a support member is provided that supports the portion of the wall facing the above-mentioned through hole toward the partition plate and is movable up and down, and the support member is raised when a low frequency and large amplitude occurs. The through hole of the partition plate is closed by a thin rubber elastic wall to allow the fluid to flow through the aperture hole, and when the high frequency and small amplitude are used, the support member is lowered to open the through hole and allow the fluid to flow through. A liquid-filled vibration isolating device characterized by being designed to allow circulation.
よシなり、供給流体圧を振動数により制御する制御手段
を設けた特許請求の範囲第１項記載の液封入防振装置。(2) The liquid-filled vibration isolator according to claim 1, wherein the support member is a bellows that expands and contracts depending on the supply fluid pressure, and is provided with a control means for controlling the supply fluid pressure by a frequency.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20420982A JPS5993537A (en) | 1982-11-20 | 1982-11-20 | Liquid charged vibration absorbing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20420982A JPS5993537A (en) | 1982-11-20 | 1982-11-20 | Liquid charged vibration absorbing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5993537A true JPS5993537A (en) | 1984-05-30 |
Family
ID=16486636
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20420982A Pending JPS5993537A (en) | 1982-11-20 | 1982-11-20 | Liquid charged vibration absorbing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5993537A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0163817A2 (en) * | 1984-06-07 | 1985-12-11 | Audi Ag | Hydraulic motor mount |
| US4754956A (en) * | 1985-09-18 | 1988-07-05 | S.A.G.A. - Societa' Applicazioni Gomma Antivibranti S.P.A. | Support for the elastic suspension of the engine in a motor-car with respect to the chassis of the same |
| US5356122A (en) * | 1989-08-03 | 1994-10-18 | Firma Carl Freudenberg | Hydraulically damped bearing for a piston engine having a relief valve for insulating engine idling vibrations |
| EP0643238A1 (en) * | 1993-09-09 | 1995-03-15 | Firma Carl Freudenberg | Switchable hydraulical damping support |
| DE19612198A1 (en) * | 1995-03-29 | 1996-10-10 | Tokai Rubber Ind Ltd | Fluid filled elastic connection for absorbing vehicle engine vibrations |
| US5687959A (en) * | 1995-04-29 | 1997-11-18 | Firma Carl Freudenberg | Hydraulically damping rubber bearing |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4998368A (en) * | 1973-01-29 | 1974-09-18 | ||
| JPS5262157A (en) * | 1975-11-17 | 1977-05-23 | Toyota Motor Co Ltd | Backward extrusion metal die |
-
1982
- 1982-11-20 JP JP20420982A patent/JPS5993537A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4998368A (en) * | 1973-01-29 | 1974-09-18 | ||
| JPS5262157A (en) * | 1975-11-17 | 1977-05-23 | Toyota Motor Co Ltd | Backward extrusion metal die |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0163817A2 (en) * | 1984-06-07 | 1985-12-11 | Audi Ag | Hydraulic motor mount |
| US4754956A (en) * | 1985-09-18 | 1988-07-05 | S.A.G.A. - Societa' Applicazioni Gomma Antivibranti S.P.A. | Support for the elastic suspension of the engine in a motor-car with respect to the chassis of the same |
| US5356122A (en) * | 1989-08-03 | 1994-10-18 | Firma Carl Freudenberg | Hydraulically damped bearing for a piston engine having a relief valve for insulating engine idling vibrations |
| EP0643238A1 (en) * | 1993-09-09 | 1995-03-15 | Firma Carl Freudenberg | Switchable hydraulical damping support |
| DE19612198A1 (en) * | 1995-03-29 | 1996-10-10 | Tokai Rubber Ind Ltd | Fluid filled elastic connection for absorbing vehicle engine vibrations |
| US5642873A (en) * | 1995-03-29 | 1997-07-01 | Tokai Rubber Industries, Ltd. | Fluid-filled elastic mount having pushing member for controlling fluid communication through orifice passage |
| DE19612198C2 (en) * | 1995-03-29 | 2003-05-28 | Tokai Rubber Ind Ltd | Fluid-filled elastic fastening |
| US5687959A (en) * | 1995-04-29 | 1997-11-18 | Firma Carl Freudenberg | Hydraulically damping rubber bearing |
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