JPS5857536A - Vibration proof supporter - Google Patents
Vibration proof supporterInfo
- Publication number
- JPS5857536A JPS5857536A JP15433381A JP15433381A JPS5857536A JP S5857536 A JPS5857536 A JP S5857536A JP 15433381 A JP15433381 A JP 15433381A JP 15433381 A JP15433381 A JP 15433381A JP S5857536 A JPS5857536 A JP S5857536A
- Authority
- JP
- Japan
- Prior art keywords
- vibration
- fluid
- magnetic
- viscosity
- passage
- 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
- F16F13/30—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 comprising means for varying fluid viscosity, e.g. of magnetic or electrorheological fluids
- F16F13/305—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 comprising means for varying fluid viscosity, e.g. of magnetic or electrorheological fluids magnetorheological
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
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
ントとして用ムて好１な防１１ｉｉ叉持装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an anti-vibration support device, particularly to an anti-vibration support device suitable for use as an engine mount for an automobile.
自動軍用エンジンマウント−としては専らインシュレー
タラバーが用いられているが、このインシュレータラバ
ーは防振効果を得るためにばね定数を小さくしてしまう
と割振効果が得られず、逆に割振効果を得るためにばね
定数を高めると防振効果が得られないといった相剋的な
問題を抱えており、通常は割振効果を期待して防振効果
をある程度犠牲にして適宜ばね定数を決定しているのが
実状である。Insulator rubber is exclusively used for automatic military engine mounts, but if the spring constant of this insulator rubber is made small in order to obtain a vibration-proofing effect, it will not be possible to obtain an allocation effect; on the contrary, in order to obtain an allocation effect, However, if the spring constant is increased, the anti-vibration effect cannot be obtained, which is a conflicting problem, and the reality is that the spring constant is usually determined appropriately by sacrificing the anti-vibration effect to a certain extent in hopes of achieving a better distribution effect. It is.
本発明はかかる従来の実状に鑑み、防振効果。In view of the conventional situation, the present invention has an anti-vibration effect.
割振効果ともに優れた防振支持装置を提供することを目
的とするものである。The object of the present invention is to provide a vibration isolating support device that has excellent vibration distribution effects.
前記目的を達成するため５本発明にあっては磁性流体が
磁場が印那されること忙よって粘度が見かけ上質化して
、流通抵抗が変化する特性を肩している点に着目し、こ
の磁性流体を用いて振動体の感動に対して磁性流体を狭
搾通路を介して連通した第１．第２流体空間で流動させ
ると共に、損動数に応じて前記磁性流体に磁場を印加し
、ｆＢ磁性流体粘度を変化させて振動体の振動を制振す
る制振機構と、振動体の撮動を減衰するインシュレータ
ラバーとを組合せることによって防振効齋。In order to achieve the above object, the present invention focuses on the fact that the viscosity of the magnetic fluid becomes apparently higher due to the application of a magnetic field, and the flow resistance changes. The first method uses a fluid to communicate the magnetic fluid to the vibration of the vibrating body through a narrow passage. A vibration damping mechanism that controls the vibration of the vibrating body by causing the magnetic fluid to flow in a second fluid space and applying a magnetic field to the magnetic fluid according to the loss frequency to change the fB magnetic fluid viscosity, and photographing the vibrating body. Anti-vibration effect by combining with insulator rubber that dampens vibration.
割部効果の同筆を図っている。We are trying to draw parallels to the Waribe effect.
以下、本発明の実施例を図面と共Ｋｆｓ述する。Embodiments of the present invention will be described below together with the drawings.
第１図は本発明の防振支持装置を自動車用エンジンマウ
ントに過用したもので、防振支持装置ＶはエンジンＥｉ
ｌｌｌのブラケットＢ１と、車体Ｂ側のブラケッ）Ｂ２
との間に介装しである。この防振支持装置Ｍは、十分な
防振効果が得られ葛ようＫばね定数を小さく設定したイ
ンシュレータラバー１と。FIG. 1 shows the vibration isolating support device of the present invention applied to an automobile engine mount.
1ll bracket B1 and the bracket on the vehicle body B side) B2
There is an interposition between the two. This anti-vibration support device M includes an insulator rubber 1 which provides a sufficient anti-vibration effect and has a small spring constant.
このインシュレータラバー１と並設した制振機構２とか
らなっている。It consists of this insulator rubber 1 and a vibration damping mechanism 2 installed in parallel.
第２図は割振機構の一例を示すもので、３はアルミニウ
ムのような反磁性金）［のケーシングで。Figure 2 shows an example of the allocation mechanism, and 3 is a casing made of diamagnetic gold such as aluminum.
該ケーシング３は一斗状に形成してあり、その上熾開口
部にゴム等の弾性体からなる端Ｍ４を液密的に取付けて
第１ｆｉ体冨５を形成していると共Ｋ。The casing 3 is formed in the shape of a bell, and an end M4 made of an elastic material such as rubber is attached to the open end of the casing 3 in a liquid-tight manner to form a first fi body 5.
下ｆｌｌｌｉｃはゴム等の弾性体からなるぺａ−ズ７を
液密的に取付けて第２ｆ＃、体Ｎ６としてあり、そして
、ケーシング５の小径部分をこれら第１．第２４体Ｎ５
．６を連通ずる狭搾通路８としである。第１゜第２ｆｉ
体室５．６および通路８には磁性流体９を充満封入して
あり、ケーシング３を端蓋４と共に車体側ブラケットＢ
２にボルト・ナツト１０固定しである。この４雪４はそ
の略中央部をロッド１１を介して振動体、即ち、エンジ
ン側ブラケットＢ１に連結してあり、エンジンＥの振動
に対して端Ａ４を弾性変形させて磁性流体９を第１ｆｌ
ｔ体室５と第２流体室６との間で流動させるようにしで
ある。A pair 7 made of an elastic material such as rubber is attached to the lower flllic in a liquid-tight manner to form the second f# and body N6, and the small diameter portion of the casing 5 is connected to these first flllic. 24th body N5
．． 6 is connected to a narrow passage 8. 1st゜2nd fi
The body chamber 5.6 and passage 8 are filled with magnetic fluid 9, and the casing 3 is attached to the vehicle body side bracket B together with the end cover 4.
2 is fixed with bolts and nuts 10. The four snowflakes 4 are connected to a vibrating body, that is, an engine-side bracket B1, through a rod 11 at a substantially central portion thereof, and elastically deform the end A4 in response to the vibrations of the engine E to move the magnetic fluid 9 to the first fl.
The liquid is caused to flow between the body chamber 5 and the second fluid chamber 6.
前記狭搾通路８外周にはソレノイド１２を配設してあり
、このソレノイド１２を車体−ブラケット８．２（４Ｌ
＜は、エンジン側ブラケットＢｌ）、に配した公知の感
動センサ１３の検出作用にもとづいて、演算装置１４．
１１１流制御装置１５を介して励磁し、該通路Ｂを通過
する磁性流体９にエンジンＥの振１１ＥｂＶｃ応じて磁
場を印加して該磁性流体９σ）粘度を変化、つまり、低
周波大振幅のときに磁力を大として見かけの粘度を高め
、高周波振動（例えばＡ ＯＨｚ以上）の時に磁力を小
さくもしくはソレノイド１２の励磁を停止して見かけの
粘度を下げ本来の粘度忙なるようにしである。A solenoid 12 is disposed on the outer periphery of the narrowed passage 8, and this solenoid 12 is connected to the vehicle body-bracket 8.2 (4L
< is based on the detection action of the known emotion sensor 13 disposed on the engine side bracket Bl), and the arithmetic unit 14.
111 is excited via the flow control device 15, and a magnetic field is applied to the magnetic fluid 9 passing through the passage B in accordance with the vibration 11EbVc of the engine E to change the viscosity of the magnetic fluid 9σ, that is, when the magnetic fluid 9 is at low frequency and large amplitude. The magnetic force is increased to increase the apparent viscosity, and the magnetic force is decreased or the excitation of the solenoid 12 is stopped at the time of high frequency vibration (for example, AOHz or higher) to lower the apparent viscosity and maintain the original viscosity.
以上の構成からなる実施例装置によれば、高周波撮動の
場合には、振動センサ１３の攬出作用によりソレノイド
１２の励磁が停とし、もしくは励磁力が小さく制御され
、従って１割振機構２の磁性流体９０粘度が下がる。こ
のため、第１流体室５と第２流体室６との間での磁性流
体の流動時の抵抗は小さく、該制振機構２はその制振機
能を発揮しない。従って、この振動はインシュレータラ
バー１で＃ｔ′！！Ｉされて車体側への伝達が阻止され
。According to the embodiment device having the above configuration, in the case of high-frequency imaging, the excitation of the solenoid 12 is stopped by the excitation action of the vibration sensor 13, or the excitation force is controlled to be small, so that the 1-distribution mechanism 2 Ferrofluid 90 viscosity decreases. Therefore, the resistance when the magnetic fluid flows between the first fluid chamber 5 and the second fluid chamber 6 is small, and the vibration damping mechanism 2 does not exhibit its vibration damping function. Therefore, this vibration #t'! in the insulator rubber 1! ! I and the transmission to the vehicle body side is blocked.
ここに優れた防振効果を発揮できるのである。This is where the excellent anti-vibration effect can be demonstrated.
他方、低周波大振幅の振動が生じた場合、感動センサ１
Ｓの検出作用によりソレノイド１２の励磁力が高められ
、狭搾通路８を流通する磁性流体９の粘度が高められる
。このｌｔＩ果、第１流体璽５と第２流体室６との間で
の磁性流体９の流動が狭搾通路８部分で流通抵抗が大と
なるために看しく制約を受け、ことに制振機構２０機能
が発揮されて優れた制振効果が傳られるのである。On the other hand, when vibrations with low frequency and large amplitude occur, the emotion sensor 1
Due to the detection action of S, the excitation force of the solenoid 12 is increased, and the viscosity of the magnetic fluid 9 flowing through the narrowed passage 8 is increased. As a result of this, the flow of the magnetic fluid 9 between the first fluid chamber 5 and the second fluid chamber 6 is severely restricted due to the large flow resistance in the narrow passage 8 portion, and is particularly damped. The function of the mechanism 20 is fully utilized and an excellent vibration damping effect is achieved.
第５，４図は割振機構２の６異なる例を示すもので、第
３図に示すものｋあってはケーシング３Ａを円筒状とし
て、Ｔｍ開口部にも弾性体からなろ端蓋１６を、第１流
体室５と第２１５！体Ｎ６とを隔成する仕切板１７と共
に液密的にボルト・ナツト１８固定し、そして、この仕
切板１７の略中央部に狭搾通路８Ａを形成して、この通
路外周にソレノイド１２を配したものである。FIGS. 5 and 4 show six different examples of the allocation mechanism 2. In the one shown in FIG. 1 fluid chamber 5 and 215th! A bolt/nut 18 is fixed liquid-tightly together with a partition plate 17 that separates the body N6 from the body N6, and a narrowed passage 8A is formed approximately in the center of this partition plate 17, and a solenoid 12 is arranged around the outer periphery of this passage. This is what I did.
従って、この実施例の場合も、低周波大振幅の時にはソ
レノイド１２の励磁力が高められることによって１通路
８Ａを流通する磁性流体９（ｎ粘度が高められて、第２
図に示すものと同様の割振機能を発揮することができる
。Therefore, in the case of this embodiment as well, when the low frequency and large amplitude are present, the excitation force of the solenoid 12 is increased, so that the viscosity of the magnetic fluid 9 (n) flowing through the first passage 8A is increased, and the second
It is possible to perform an allocation function similar to that shown in the figure.
第４図に示す実施例は仕切板１７に複数個の小孔８ａを
開設して狭搾通路８人とする開方、第１流体室５にソレ
ノイド１２を配して、このソレノイド１２の励磁によっ
て第１流体Ｎ５の磁性流体９の粘度を高め、該磁性流体
９が第１ｆｉ体室５から第２ｆｉ体室６へ流動する際に
、前記小孔８ａ部分で大なる流通抵抗が得られて前述と
同様の振賑囁能を発揮し得るようにしたものである。In the embodiment shown in FIG. 4, a plurality of small holes 8a are formed in the partition plate 17 so that eight people can pass through the narrow passage, and a solenoid 12 is disposed in the first fluid chamber 5, and the solenoid 12 is excited. By increasing the viscosity of the magnetic fluid 9 of the first fluid N5, when the magnetic fluid 9 flows from the first fi body chamber 5 to the second fi body chamber 6, a large flow resistance is obtained in the small hole 8a portion. It is designed to be able to exhibit the same exciting ability as mentioned above.
第５図は本発明装置の異なる例を示すもので、本実施例
ではインシュレータラバーと制振機構とな一体ＩＦＩＣ
構成して装置の小型化を図り１部品点数並に組付工数を
削減している。FIG. 5 shows a different example of the device of the present invention. In this embodiment, an integrated IFIC is used as an insulator rubber and a vibration damping mechanism.
This structure reduces the size of the device, reduces the number of parts, and reduces the number of assembly steps.
制振機構２のケーシング３ｂは円筒状のインシュレータ
ラバー、即ち、防振４！ｌ能を十分に発揮し得るようＫ
ばね定数を小さく設定したインシュレータラバー１人で
形成してあり、その上端開口部忙金属製の４１９を加硫
接着する開方、下噛開ロ部にゴム等の弾性体からなる＊
霊１６と、第１゜第２ｆｌｔ体室５，６を隔成する仕切
板１７とをボルト・ナツト１０により車体側ブラケット
ａｔと共に液密的に共締め固定し、上部＠１１２１９の
略中央部をロッド１１によりエンジン側ブラケットＢ、
に連結し、そして、第１．第２流体室５．６に磁性流体
９を密封充満すると共に、仕切板１７の略中央部に狭搾
通路８Ａを形成して、その外周にソレノイド１２を配し
、このソレノイド１２を前記各実施例Ｅ同様ＫＩＮ体側
ブラケットＢｚ（４しくはエンジン側ブラケットＢ１）
Ｋ配した感動セ／す／Ｊの検出作用にもとづいて演算
装置１４．電流制御ｌｌ＠置１５を介して励磁するよう
にしである。The casing 3b of the vibration damping mechanism 2 is a cylindrical insulator rubber, that is, the vibration damping mechanism 2! In order to fully demonstrate one's abilities,
It is made of one insulator rubber with a small spring constant, and the upper end opening where the metal 419 is vulcanized and bonded, and the lower opening part are made of elastic material such as rubber *
The spacer 16 and the partition plate 17 that separates the first and second flt body chambers 5 and 6 are liquid-tightly fixed together with the vehicle body side bracket at using bolts and nuts 10, and the approximately central part of the upper part @11219 is fixed. Engine side bracket B by rod 11,
and the first. The second fluid chamber 5.6 is hermetically filled with the magnetic fluid 9, and a narrowed passage 8A is formed approximately in the center of the partition plate 17, and a solenoid 12 is disposed around the outer periphery of the narrowed passage 8A. Same as Example E, KIN body side bracket Bz (4 or engine side bracket B1)
The arithmetic unit 14. It is designed to be excited via the current control device 15.
この実施例装置では、高周波振動の時は振動センサ１３
の検出作用によりソレノイド１２の励磁が俸止し、もし
くは励磁力が小さく制−されるため、磁性流体９の第１
．第２流体室５．６間での流動は抵抗が小さく自由に行
われ、従って割振機能は発揮しない、−万、ケーシング
３ｂはばね定数の小さなインシュレータラバー１人で形
成しであるため、ｉｓはこのインシュレータラバー１人
で減渡され、ここに堕撮機能を発揮し得るのである。In this embodiment device, when high frequency vibration occurs, the vibration sensor 13
The excitation of the solenoid 12 is stopped or the excitation force is suppressed to a small value due to the detection action of the magnetic fluid 9.
．． The flow between the second fluid chambers 5 and 6 occurs freely with low resistance, so the distribution function is not exerted. Since the casing 3b is formed by a single insulator rubber with a small spring constant, IS is This insulator rubber can be reduced by one person, and it can perform the function of capturing a captured image.
低周波大損幅の振動時は、撮動センサ／３の検出作用に
よりソレノイド１２の励磁力が高められ。When there is vibration with a large low frequency loss, the excitation force of the solenoid 12 is increased by the detection action of the imaging sensor/3.
これにより狭搾通路８Ａを流通する磁性流体９の粘度が
高められて該通路８Ａ部分の流通抵抗が高オる。この結
果、磁性流体９の第１．第２譜１体室５．６間でのＷｔ
、勧が著しく制約され、ここに割振機能を発揮するので
ある。As a result, the viscosity of the magnetic fluid 9 flowing through the narrow passage 8A is increased, and the flow resistance of the passage 8A is increased. As a result, the first . 2nd staff 1 body room 5.6 Wt
This is where the allocation function comes into play, as the allocation is severely restricted.
なお、前記各実施例説明図では振動センサな車体側ブラ
ケットに配しているが、エンジン側ブラケットにも配し
て両センサの柳出ＩＩを比較して演算装置より電流制御
装置へ信号を送ってソレノイドの励磁力を制御するよう
にしてもよい。In the explanatory diagrams of each of the above embodiments, a vibration sensor is placed on the vehicle body side bracket, but it is also placed on the engine side bracket and the Yanagi De II of both sensors are compared and a signal is sent from the calculation device to the current control device. Alternatively, the excitation force of the solenoid may be controlled.
以上のよ５に本発明装置によれば、Ｉ振、制振共に優れ
た磯＃ｒＰ＆発揮することができて１Ｍ振支持装置とし
て要求される特性を満足して肪振叉持効果を一段と同上
できるという実用上火なる効果を有する。As described above, according to the device of the present invention, it is possible to exhibit excellent rock #rP& in both I vibration and vibration damping, and it satisfies the characteristics required as a 1M vibration support device, further improving the fat vibration support effect. It has the practical effect of being able to do something like fire.
第１図は本発明装置の一実施例を示す側面図。
第２．ｇ、４図は制振機構の６異なる例を示す断面図、
第５図は本発明装置の畳なる例を示す断面図である。
１．１人・・・インシュレータラバー、２・・・制振機
構、５・・・第１ｆＬ体室、６・・・第２流体呈、８・
８Ａ・・・狭搾通路。
第１図
第２図
第４図
第５図FIG. 1 is a side view showing one embodiment of the device of the present invention. Second. g, Figure 4 is a cross-sectional view showing six different examples of vibration damping mechanisms;
FIG. 5 is a sectional view showing a folding example of the device of the present invention. 1.1 person... insulator rubber, 2... vibration damping mechanism, 5... 1st fL body chamber, 6... second fluid presentation, 8...
8A...Narrow passage. Figure 1 Figure 2 Figure 4 Figure 5
Claims (1)
璽と第２流体室とを有すると共に内部に磁性流体を封入
し、振動体の振動に対して磁性流体を第１、第２流体室
間で流動させ、かつ、磁性流体に娠勧数に応じて磁場を
印加して磁性流体 。 の粘度を変化させて畿動体の振動を割部する割振機構と
、振動体の振動′４を諷衰するインシュレータラバーと
の岨合せからなる防振支持ｉ置。[Claims] 111 No. 1151I communicated via a narrowed passage! It has a body seal and a second fluid chamber, and a magnetic fluid is sealed inside, and the magnetic fluid is made to flow between the first and second fluid chambers in response to the vibration of the vibrating body, and the magnetic fluid is made to flow in response to the vibration of the vibrating body. Apply a magnetic field accordingly to the ferrofluid. A vibration-proof support arrangement consisting of a combination of an oscillation mechanism that divides the vibrations of a vertically moving body by changing the viscosity of the oscillator, and an insulator rubber that attenuates the vibrations of the vibrating body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15433381A JPS5857536A (en) | 1981-09-29 | 1981-09-29 | Vibration proof supporter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15433381A JPS5857536A (en) | 1981-09-29 | 1981-09-29 | Vibration proof supporter |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5857536A true JPS5857536A (en) | 1983-04-05 |
Family
ID=15581851
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15433381A Pending JPS5857536A (en) | 1981-09-29 | 1981-09-29 | Vibration proof supporter |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5857536A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0137112A2 (en) * | 1983-10-11 | 1985-04-17 | METZELER Gesellschaft mit beschränkter Haftung | Two space hydraulic damping support |
| JPS61116141A (en) * | 1984-11-13 | 1986-06-03 | Yakumo Kogyo Kk | Vibration damping equipment |
| US4733758A (en) * | 1986-08-18 | 1988-03-29 | Lord Corporation | Tunable electrorheological fluid mount |
| EP1249637A1 (en) * | 2001-04-10 | 2002-10-16 | Bayerische Motoren Werke Aktiengesellschaft | Device for the suppression of vibrations of a moving system |
| CN108488305A (en) * | 2018-06-20 | 2018-09-04 | 上海理工大学 | A kind of band thickening fluid elastic collision damper |
-
1981
- 1981-09-29 JP JP15433381A patent/JPS5857536A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0137112A2 (en) * | 1983-10-11 | 1985-04-17 | METZELER Gesellschaft mit beschränkter Haftung | Two space hydraulic damping support |
| US4880216A (en) * | 1983-10-11 | 1989-11-14 | Metzeler Kautschuk Gmbh | Two-chamber engine bearing which has hydraulic damping |
| JPS61116141A (en) * | 1984-11-13 | 1986-06-03 | Yakumo Kogyo Kk | Vibration damping equipment |
| US4733758A (en) * | 1986-08-18 | 1988-03-29 | Lord Corporation | Tunable electrorheological fluid mount |
| EP1249637A1 (en) * | 2001-04-10 | 2002-10-16 | Bayerische Motoren Werke Aktiengesellschaft | Device for the suppression of vibrations of a moving system |
| CN108488305A (en) * | 2018-06-20 | 2018-09-04 | 上海理工大学 | A kind of band thickening fluid elastic collision damper |
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