JPH06117476A - Vibration control supporting device - Google Patents
Vibration control supporting deviceInfo
- Publication number
- JPH06117476A JPH06117476A JP27041092A JP27041092A JPH06117476A JP H06117476 A JPH06117476 A JP H06117476A JP 27041092 A JP27041092 A JP 27041092A JP 27041092 A JP27041092 A JP 27041092A JP H06117476 A JPH06117476 A JP H06117476A
- Authority
- JP
- Japan
- Prior art keywords
- fluid chamber
- main fluid
- receiving area
- pressure receiving
- vibration
- 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
Landscapes
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、例えば車両のエンジ
ン等の振動体を車体等の支持体に支持する防振支持装置
に関し、特に、比較的低周波の振動入力に対しては主流
体室及び副流体室間で流体を移動させて高動バネ定数，
高減衰を得る一方、そのような流体の移動が不可能にな
る周波数帯域の振動入力に対しては能動的に主流体室の
容積を変化させて低動バネ定数を得る流体封入式の防振
支持装置において、主流体室の容積を変化させるために
設けられるアクチュエータが発生する力を効率良く利用
できるようにしたものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an anti-vibration supporting device for supporting a vibrating body such as a vehicle engine on a supporting body such as a vehicle body, and particularly to a main fluid chamber for a relatively low frequency vibration input. And a high dynamic spring constant by moving the fluid between the sub-fluid chambers,
While high damping is achieved, a fluid-filled type vibration isolation system that actively changes the volume of the main fluid chamber to obtain a low dynamic spring constant for vibration input in the frequency band where such fluid movement is impossible In the support device, the force generated by the actuator provided for changing the volume of the main fluid chamber can be efficiently used.
【０００２】[0002]
【従来の技術】従来の流体封入式の防振支持装置として
は、例えば特開昭６１−２９３９号公報に記載されたも
のがある。かかる従来の技術は、特に車両のエンジンを
支持する装置に関するものであって、エンジン及び車体
間に介在する支持弾性体と、この支持弾性体内に形成さ
れた主流体室と、この主流体室にオリフィスを介して通
じる容積可変の副流体室と、主流体室，副流体室及びオ
リフィス内に封入された流体と、主流体室内に配設され
且つ能動的に変位する可動板と、を備えている。そし
て、オリフィスを通じての流体の移動が可能な比較的低
周波の振動が入力された場合には、その振動入力に応じ
て主流体室及び副流体室間でオリフィスを通じて流体が
移動するから、高動バネ定数及び高減衰力の防振支持装
置となり、５〜１５Ｈｚ程度の振動入力であるエンジン
シェイクを低減することができた。また、オリフィス内
の流体がスティック状態となる周波数帯域の振動が入力
された場合には、主流体室の内圧の変化がなくなるよう
に振動入力に同期して可動板を能動的に変位させ、もっ
て低動バネ定数の防振支持装置とし、２０〜３０Ｈｚ程
度の振動入力であるアイドル振動や、８０〜８００Ｈｚ
程度の振動入力であるこもり音振動・加速時振動の低減
を図っていた。2. Description of the Related Art A conventional fluid-filled type vibration-damping support device is disclosed in, for example, JP-A-61-2939. Such a conventional technique relates to a device for supporting an engine of a vehicle, in particular, a support elastic body interposed between an engine and a vehicle body, a main fluid chamber formed in the support elastic body, and a main fluid chamber A variable volume sub-fluid chamber communicating through the orifice, a main fluid chamber, a fluid enclosed in the sub-fluid chamber and the orifice, and a movable plate disposed in the main fluid chamber and actively displaced There is. When a relatively low-frequency vibration that allows the fluid to move through the orifice is input, the fluid moves through the orifice between the main fluid chamber and the sub-fluid chamber in response to the vibration input, so high motion The vibration proof support device has a spring constant and a high damping force, and engine shake, which is a vibration input of about 5 to 15 Hz, can be reduced. Also, when vibration in the frequency band where the fluid in the orifice becomes a stick state is input, the movable plate is actively displaced in synchronization with the vibration input so that the internal pressure of the main fluid chamber does not change. Anti-vibration support device with low dynamic spring constant, idle vibration which is a vibration input of about 20 to 30 Hz, and 80 to 800 Hz
It tried to reduce muffled sound vibration and vibration during acceleration, which are vibration inputs of a certain degree.
【０００３】つまり、この従来の防振支持装置によれ
ば、支持装置に高動バネ定数，高減衰が要求されるエン
ジンシェイクと、支持装置に低動バネ定数，低減衰が要
求されるアイドル振動，こもり音振動・加速時振動との
いずれに対しても防振効果を発揮することができた。That is, according to this conventional anti-vibration support device, an engine shake requiring the support device to have a high dynamic spring constant and a high damping and an idle vibration requiring a support device to have a low dynamic spring constant and a low damping. The anti-vibration effect was able to be exhibited against both muffled sound vibration and vibration during acceleration.
【０００４】[0004]
【発明が解決しようとする課題】確かに、上記従来の装
置であれば、理論的には高動バネ定数，高減衰の防振支
持装置及び低動バネ定数，低減衰の防振支持装置として
機能し、広い周波数帯域に渡って良好な防振効果を得る
ことが可能であるが、実際には、低動バネ定数の防振支
持装置として機能させる場合、支持装置のバネ定数を見
掛け上“０”にしてエンジン側からの振動伝達をなくす
ために可動板を１０Ｎ前後の力で駆動する必要があるの
に対し、コスト，スペース，重量等の制約から車両のエ
ンジンマウントに用いられる程度の通常の電磁ソレノイ
ド等のアクチュエータでは充分な力が得られないため、
動バネ定数をそれほど小さくすることができず、防振効
果としては不十分なものであった。Certainly, the above-mentioned conventional device can theoretically be used as a high dynamic spring constant / high damping vibration isolation support device and a low dynamic spring constant / low damping vibration isolation support device. It functions and is able to obtain a good anti-vibration effect over a wide frequency band. However, when actually functioning as an anti-vibration support device with a low dynamic spring constant, the spring constant of the support device is apparently “ It is necessary to drive the movable plate with a force of about 10N in order to eliminate the vibration transmission from the engine side to 0 ", whereas it is usually used for an engine mount of a vehicle due to cost, space, weight and other restrictions. Since an actuator such as the electromagnetic solenoid of above cannot obtain sufficient force,
The dynamic spring constant could not be reduced so much, and the vibration-proof effect was insufficient.
【０００５】本発明は、このような従来の技術が有する
未解決の課題に着目してなされたものであって、アクチ
ュエータが発生する力を効率良く振動低減に利用するこ
とができる防振支持装置を提供することを目的としてい
る。The present invention has been made by paying attention to the unsolved problems of the above-mentioned conventional techniques, and it is possible to efficiently utilize the force generated by the actuator for vibration reduction. Is intended to provide.
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するため
に、請求項１記載の発明は、振動体及び支持体の一方に
固定される第１の部材と、前記振動体及び支持体の他方
に固定される第２の部材と、これら第１の部材及び第２
の部材間に介在する支持弾性体と、この支持弾性体によ
って画成された主流体室と、容積可変の副流体室と、こ
れら主流体室及び副流体室間を連通させるオリフィス
と、前記主流体室，副流体室及びオリフィス内に封入さ
れた流体と、前記主流体室の隔壁の一部を形成し且つそ
の主流体室の容積を変化させる方向に変位可能に前記第
２の部材側に配設された可動部材と、前記第２の部材側
に配設され且つ前記可動部材を変位させるアクチュエー
タと、を備えた防振支持装置において、前記主流体室に
おける前記第１の部材側の有効受圧面積が前記主流体室
における前記可動部材の受圧面積よりも小さい場合には
前記第２の部材を前記支持体側に固定し、前記主流体室
における前記第１の部材側の有効受圧面積が前記主流体
室における前記可動部材の受圧面積よりも大きい場合に
は前記第２の部材を前記振動体側に固定する。In order to achieve the above object, the invention according to claim 1 provides a first member fixed to one of a vibrating body and a support, and the other of the vibrating body and the support. A second member fixed to the first member and the first member and the second member.
A support elastic body interposed between the members of the main fluid chamber, a main fluid chamber defined by the support elastic body, a sub-fluid chamber having a variable volume, an orifice for communicating between the main fluid chamber and the sub-fluid chamber, and the main flow A fluid enclosed in the body chamber, the sub-fluid chamber and the orifice, and on the second member side so as to be displaceable in a direction which forms a part of the partition wall of the main fluid chamber and changes the volume of the main fluid chamber. In an anti-vibration support device including a movable member that is disposed and an actuator that is disposed on the side of the second member and that displaces the movable member, an effective side of the main fluid chamber on the side of the first member is effective. When the pressure receiving area is smaller than the pressure receiving area of the movable member in the main fluid chamber, the second member is fixed to the support body side, and the effective pressure receiving area of the main fluid chamber on the first member side is the above. The movable in the main fluid chamber If greater than the pressure receiving area of the timber to secure said second member to said vibration member side.
【０００７】また、請求項２記載の発明は、上記請求項
１記載の発明において、主流体室における第１の部材側
の有効受圧面積Ａu が主流体室における可動部材の受圧
面積Ａp よりも大きい場合、前記有効受圧面積Ａu 及び
受圧面積Ａp の比ＲA ＝Ａp／Ａu の２乗ＲA 2 と、前
記可動部材の支持バネ定数Ｋp 及び前記支持弾性体の拡
張方向バネ定数Ｋe の比ＲK ＝Ｋp ／Ｋe とを一致又は
略一致させる。According to a second aspect of the invention, in the first aspect of the invention, the effective pressure receiving area A u of the main fluid chamber on the first member side is smaller than the pressure receiving area A p of the movable member in the main fluid chamber. Again large, square and R a 2 ratio R a = a p / a u of the effective pressure receiving area a u and the pressure receiving area a p, direction of extension of the support spring constant K p and the elastic support of the movable member Match or substantially match the ratio R K = K p / K e of the spring constant K e .
【０００８】[0008]
【作用】請求項１記載の発明にあっては、主流体室の容
積を変化可能な可動部材を変位させるアクチュエータが
配設された第２の部材は、主流体室における第１の部材
の有効受圧面積Ａu が可動部材の受圧面積Ａp よりも小
さい（Ａu ＜Ａp ）場合には支持体側に固定され、有効
受圧面積Ａu が受圧面積Ａp よりも大きい（Ａu＞
Ａp ）場合には振動体側に固定される。According to the first aspect of the invention, the second member provided with the actuator for displacing the movable member capable of changing the volume of the main fluid chamber is effective as the first member in the main fluid chamber. receiving area a u is smaller than the pressure receiving area a p of the movable member (a u <A p )_Baainiwashijitaisokunikoteisare,yuko受圧Menseki_A u Ga受圧Menseki_A p Yorimookii(A u>
In the case of A p ), it is fixed to the vibrating body side.
【０００９】そして、第２の部材が支持体側に固定され
た場合、振動体で発生した力は、第１の部材，主流体室
内の流体，可動部材及び第２の部材を介して支持体側に
伝達され、その伝達される力は、アクチュエータが可動
部材を変位させ主流体室内の圧力変動を緩和することに
より低減されることになるが、主流体室の入力側の有効
受圧面積Ａu が出力側の受圧面積Ａp よりも小さいた
め、そのアクチュエータに発生する力は比較的小さくて
済む。When the second member is fixed to the support side, the force generated in the vibrating body is applied to the support side via the first member, the fluid in the main fluid chamber, the movable member and the second member. The transmitted force is reduced by the actuator displacing the movable member to reduce the pressure fluctuation in the main fluid chamber, but the effective pressure receiving area A u on the input side of the main fluid chamber is output. Since it is smaller than the pressure receiving area A p on the side, the force generated in the actuator can be relatively small.
【００１０】一方、第２の部材が振動体側に固定された
場合、振動体で発生した力は、第２の部材，可動部材，
主流体室内の流体及び第１の部材を介して支持体側に伝
達され、その伝達される力は、同様にアクチュエータが
可動部材を変位させ主流体室内の圧力変動を緩和するこ
とにより低減されることになるが、この場合も主流体室
の入力側の受圧面積Ａp が出力側の有効受圧面積Ａu よ
りも小さいため、そのアクチュエータに発生する力は比
較的小さくて済む。On the other hand, when the second member is fixed to the vibrating body side, the force generated in the vibrating body is
The force transmitted to the support body side via the fluid in the main fluid chamber and the first member, and the transmitted force is similarly reduced by the actuator displacing the movable member to mitigate the pressure fluctuation in the main fluid chamber. but becomes, for receiving area a p of the input side of the case main body chamber is smaller than the effective pressure receiving area a u of the output side, the force generated in the actuator requires only a relatively small.
【００１１】また、請求項２記載の発明にあっては、第
２の部材を振動体側に固定する場合、有効受圧面積Ａu
及び受圧面積Ａp の比ＲA 2 ＝Ａp ／Ａu の２乗ＲA 2
と、可動部材の支持バネ定数Ｋp 及び支持弾性体の拡張
方向バネ定数Ｋe の比ＲK ＝Ｋp ／Ｋe とを一致又は略
一致させているため、アクチュエータに発生する力は可
能な範囲で最も小さくて済む。According to the second aspect of the invention, when the second member is fixed to the vibrating body side, the effective pressure receiving area A u.
And ratio of pressure receiving area A p RA 2 = A p / A u squared RA 2
And the ratio R K = K p / K e of the support spring constant K p of the movable member and the expansion direction spring constant K e of the support elastic body are matched or substantially matched, the force generated in the actuator is possible. It is the smallest in the range.
【００１２】[0012]
【実施例】以下、本発明の実施例を図面に基づいて説明
する。図１乃至図３は本発明の一実施例を示す図であ
り、本実施例は、本発明に係る防振支持装置を車両のエ
ンジンマウント１に適用したものである。先ず、構成を
説明すると、図１に示すように、このエンジンマウント
１は、支持側としての車体側又は振動体側としてのエン
ジン側への取付け用の取付けボルト２ａを上部に一体に
備え且つ内側が空洞で下部が開口した取付部材２を有
し、この取付部材２の下部外面には内筒３の上端部がか
しめ止めされている。Embodiments of the present invention will be described below with reference to the drawings. 1 to 3 are views showing an embodiment of the present invention, in which the vibration-damping support device according to the present invention is applied to an engine mount 1 of a vehicle. First, the structure will be described. As shown in FIG. 1, the engine mount 1 is integrally provided with a mounting bolt 2a for mounting on a vehicle body side as a support side or an engine side as a vibrating body side and has an inner side. It has a mounting member 2 which is hollow and has a lower opening. The upper end of the inner cylinder 3 is caulked to the outer surface of the lower part of the mounting member 2.
【００１３】この内筒３の内側には、取付部材２及び内
筒３の内側の空間を上下に二分するように、それら取付
部材２及び内筒３のかしめ止め部分に挟み込まれてダイ
アフラム４が配設されていて、このダイアフラム４によ
って二分された空間のうち、ダイアフラム４の上側の空
間は大気圧に通じ、ダイアフラム４の下側の空間にはオ
リフィス構成体５が配設されている。Inside the inner cylinder 3, a diaphragm 4 is sandwiched between the mounting member 2 and the inner cylinder 3 by caulking so that the space inside the mounting member 2 and the inner cylinder 3 is divided into upper and lower parts. Of the space that is provided and is divided by the diaphragm 4, the space above the diaphragm 4 communicates with atmospheric pressure, and the orifice structure 5 is provided in the space below the diaphragm 4.
【００１４】一方、内筒３の外周面には、内周面及び外
周面の軸方向位置が内周側が高くなるように成形されて
いる円筒状の支持弾性体６の内周面が加硫接着されてい
て、その支持弾性体６の外周面は外筒７の内周面に加硫
接着されている。そして、外筒７の下端部は円筒形のア
クチュエータ保持部材８の上部にかしめ止めされ、アク
チュエータ保持部材８の下端面には、エンジン側又は車
体側への取付け用の取付けボルト９ａを下部に一体に備
えた円板状の取付部材９が固定されている。On the other hand, on the outer peripheral surface of the inner cylinder 3, the inner peripheral surface of a cylindrical support elastic body 6 which is formed such that the axial positions of the inner peripheral surface and the outer peripheral surface are higher on the inner peripheral side is vulcanized. The outer peripheral surface of the supporting elastic body 6 is vulcanized and adhered to the inner peripheral surface of the outer cylinder 7. The lower end of the outer cylinder 7 is caulked to the upper portion of the cylindrical actuator holding member 8, and the lower end surface of the actuator holding member 8 is integrally provided with a mounting bolt 9a for mounting on the engine side or the vehicle body side on the lower side. The disk-shaped mounting member 9 provided in the is fixed.
【００１５】また、アクチュエータ保持部材８の上端面
には、これと一体に外筒７の下端部にかしめ止めされた
円筒部材１０が固定されていて、さらに、この円筒部材
１０の内周面には、アクチュエータ保持部材８の上端面
との間に所定のクリアランスをもち且つ円筒形の弾性体
１１により上下方向に変位可能に可動部材１２が保持さ
れている。かかる可動部材１２は、磁化可能な材料から
なり且つ上面が凹陥した円板状に成形されている。A cylindrical member 10 fixed to the lower end portion of the outer cylinder 7 by caulking is fixed to the upper end surface of the actuator holding member 8, and the inner peripheral surface of the cylindrical member 10 is further fixed. The movable member 12 is held by the cylindrical elastic body 11 so as to be vertically displaceable with a predetermined clearance from the upper end surface of the actuator holding member 8. The movable member 12 is made of a magnetizable material and is formed into a disk shape having a concave upper surface.
【００１６】そして、アクチュエータ保持部材８の内側
には、電磁コイル等を含んで構成され、外部から供給さ
れる制御信号に応じて可動部材１２を上下方向に変位さ
せる電磁アクチュエータ１３が配設されている。さら
に、本実施例では、支持弾性体６の下面及び可動部材１
２の上面によって画成された部分に主流体室１５が形成
され、ダイアフラム４及びオリフィス構成体５によって
画成された部分に副流体室１６が形成されていて、これ
ら主流体室１５及び副流体室１６間が、オリフィス構成
体５に形成されたオリフィス５ａを介して連通してい
る。なお、これら主流体室１５，副流体室１６及びオリ
フィス５ａ内には油等の流体が封入されている。Inside the actuator holding member 8, there is arranged an electromagnetic actuator 13 including an electromagnetic coil and the like, which displaces the movable member 12 in the vertical direction in response to a control signal supplied from the outside. There is. Further, in this embodiment, the lower surface of the support elastic body 6 and the movable member 1 are
2, a main fluid chamber 15 is formed in a portion defined by the upper surface of the second fluid, and a sub fluid chamber 16 is formed in a portion defined by the diaphragm 4 and the orifice structure 5. The chambers 16 communicate with each other via the orifice 5a formed in the orifice structure 5. A fluid such as oil is enclosed in the main fluid chamber 15, the sub fluid chamber 16 and the orifice 5a.
【００１７】かかるオリフィス５ａの流路形状等で決ま
る流体マウントとしての特性は、走行中のエンジンシェ
イク発生時、つまり５〜１５Ｈｚでエンジンマウント１
が加振された際に高動バネ定数，高減衰力を示すように
調整されている。そして、電磁アクチュエータ１３は図
示しないコントローラに接続されていて、そのコントロ
ーラは、エンジンの回転数等に基づいてこのエンジンマ
ウント１に入力される振動の周波数を判定し、オリフィ
ス５ａを通じて主流体室１５及び副流体室１６間で流体
が移動不可能な周波数帯域の振動、つまり上述したエン
ジンシェイクよりも高周波の振動であるアイドル振動や
こもり音振動・加速時振動が入力されている場合には、
その振動に同期し、取付部材９への伝達力が“０”とな
るように（具体的には支持弾性体６の弾性変形による入
力と主流体室１５の容積変動による入力を相殺できるよ
うに）、主流体室１５の隔壁の一部を形成する可動部材
１２を変位させるものである。The characteristic of the fluid mount determined by the shape of the flow path of the orifice 5a is that the engine mount 1 is generated when an engine shake occurs during traveling, that is, at 5 to 15 Hz.
Is adjusted so that it exhibits a high dynamic spring constant and high damping force when is excited. The electromagnetic actuator 13 is connected to a controller (not shown), which determines the frequency of the vibration input to the engine mount 1 based on the engine speed and the like, and the main fluid chamber 15 and the main fluid chamber 15 through the orifice 5a. When vibrations in a frequency band in which the fluid cannot move between the sub-fluid chambers 16, that is, idle vibrations, muffled sound vibrations, and vibrations during acceleration, which are vibrations of a higher frequency than the engine shake, are input,
In synchronization with the vibration, the transmission force to the mounting member 9 becomes “0” (specifically, the input due to the elastic deformation of the support elastic body 6 and the input due to the volume change of the main fluid chamber 15 can be canceled out. ), The movable member 12 forming a part of the partition wall of the main fluid chamber 15 is displaced.
【００１８】ここで、本実施例にあっては、取付部材
２，内筒３及びオリフィス構成体５によって第１の部材
が構成され、外筒７，アクチュエータ保持部材８，取付
部材９及び円筒部材１０によって第２の部材が構成され
ている。そして、主流体室１５における第１の部材の有
効受圧面積Ａu が、主流体室１５における可動部材１２
の受圧面積Ａp よりも小さい場合には、取付部材２をエ
ンジン側に固定し、取付部材９を車体側に固定する一
方、有効受圧面積Ａu が受圧面積Ａp よりも大きい場合
には、逆に、取付部材２を車体側に固定し、取付部材９
をエンジン側に固定する。In this embodiment, the first member is constituted by the mounting member 2, the inner cylinder 3 and the orifice member 5, and the outer cylinder 7, the actuator holding member 8, the mounting member 9 and the cylindrical member are provided. The second member is constituted by 10. The effective pressure receiving area A u of the first member in the main fluid chamber 15 is equal to the movable member 12 in the main fluid chamber 15.
Is smaller than the pressure receiving area A p of the case mounting member 2 is fixed to the engine side, while fixing the mounting member 9 to the vehicle body side, the effective pressure-receiving area A u is larger than the pressure receiving area A p is On the contrary, the mounting member 2 is fixed to the vehicle body side, and the mounting member 9
Is fixed to the engine side.
【００１９】次に、本実施例の作用を説明する。即ち、
エンジンシェイク発生時には、オリフィス５ａの流路形
状等を適宜選定している結果、このエンジンマウント１
は高動バネ定数，高減衰力の支持装置として機能するた
め、エンジンで発生したエンジンシェイクがエンジンマ
ウント１によって減衰され、車体側の振動レベルが低減
される。なお、かかる場合には、特に可動部材１２を変
位させる必要はない。Next, the operation of this embodiment will be described. That is,
When an engine shake occurs, the shape of the flow path of the orifice 5a is appropriately selected.
Since it functions as a support device for high dynamic spring constant and high damping force, the engine shake generated in the engine is damped by the engine mount 1, and the vibration level on the vehicle body side is reduced. In such a case, it is not particularly necessary to displace the movable member 12.
【００２０】一方、オリフィス５ａ内の流体がスティッ
ク状態となり主流体室１５及び副流体１６間での流体の
移動が不可能になるアイドル振動周波数以上の周波数の
振動が入力された場合には、電磁アクチュエータ１３が
可動部材１２を変位させ、主流体室１５の内圧の変動を
調整するから、このエンジンマウント１は低動バネ定数
の支持装置として機能し、高周波の振動がこのエンジン
マウント１で吸収され、車体側の振動レベルが低減され
る。On the other hand, when the vibration in the frequency higher than the idle vibration frequency is input, which causes the fluid in the orifice 5a to stick and prevents the fluid from moving between the main fluid chamber 15 and the sub-fluid 16, Since the actuator 13 displaces the movable member 12 and adjusts the fluctuation of the internal pressure of the main fluid chamber 15, the engine mount 1 functions as a support device having a low dynamic spring constant, and high-frequency vibration is absorbed by the engine mount 1. The vibration level on the vehicle body side is reduced.
【００２１】そして、本実施例にあっては、有効受圧面
積Ａu が受圧面積Ａp よりも小さい場合には取付部材９
を車体側に固定し、有効受圧面積Ａu が受圧面積Ａp よ
りも大きい場合には取付部材９をエンジン側に固定する
ため、電磁アクチュエータ１３に発生する力が小さくて
済む。即ち、図２又は図３に示すように、支持弾性体６
の支持方向のバネ定数をＫm，支持弾性体６の拡張方向
のバネ定数をＫe ，弾性体１１の支持方向のバネ定数を
Ｋp ，振動に伴ってエンジンに生じる変位をｘ，電磁ア
クチュエータ１３に発生する制御力をＦa ，エンジンか
らエンジンマウント１を介して車体に伝達される伝達力
をＦb とすると、伝達力Ｆb が０となるような制御力Ｆ
a は、取付部材９を車体側に固定した場合には下記の
（１）式のようになり、取付部材９をエンジン側に固定
した場合には下記の（２）式のようになる（なお、説明
を簡単にするため、可動部材１２の質量は考慮していな
い。）。In this embodiment, the mounting member 9 is used when the effective pressure receiving area A u is smaller than the pressure receiving area A p.
Is fixed to the vehicle body side, and when the effective pressure receiving area A u is larger than the pressure receiving area A p , the mounting member 9 is fixed to the engine side, so that the force generated in the electromagnetic actuator 13 can be small. That is, as shown in FIG. 2 or FIG.
, K m , the spring constant of the elastic support 6 in the expanding direction K e , the spring constant of the elastic support 11 in the support direction K p , the displacement of the engine caused by vibration x, the electromagnetic actuator Let F a be the control force generated at 13 and F b be the transmission force transmitted from the engine to the vehicle body via the engine mount 1, the control force F at which the transmission force F b becomes zero.
When the mounting member 9 is fixed to the vehicle body, a is expressed by the following formula (1), and when the mounting member 9 is fixed to the engine side, it is expressed by the following formula (2). , The mass of the movable member 12 is not taken into consideration for the sake of simplicity.)
【００２２】 Ｆa ＝｛（Ｋm ／（ＲA Ｋe ））・（Ｋp ＋ＲA 2 Ｋe ）＋Ｋp ｝ｘ／ＲA ＝Ｚ・ｘ／ＲA ……（１） Ｆa ＝｛（Ｋm ／（ＲA Ｋe ））・（Ｋp ＋ＲA 2 Ｋe ）＋Ｋp ｝ｘ ＝Ｚ・ｘ ……（２） ただし、 ＲA ＝Ａp ／Ａu Ｚ＝（Ｋm ／（ＲA Ｋe ））・（Ｋp ＋ＲA 2 Ｋe ）＋Ｋp である。F a = {(K m / (R A K e )) · (K p + R A 2 K e ) + K p } x / R A = Z · x / R A (1) F a = {(K m / (R A K e )) ・ (K p + R A 2 K e ) + K p } x = Z ・ x (2) where R A = A p / A u Z = (K m / (R A K e )) · (K p + R A 2 K e ) + K p .
【００２３】以上から、ＲA ＞１（Ａu ＜Ａp ）の場合
には、上記（１）式で示される制御力Ｆa の方が上記
（２）式で示される制御力Ｆa よりも小さくなるから、
図２に示すように、電磁アクチュエータ１３が車体側に
配されるようにエンジンマウント１を設置する一方、Ｒ
A ＜１（Ａu ＞Ａp ）の場合には、上記（２）式で示さ
れる制御力Ｆa の方が上記（１）式で示される制御力Ｆ
a よりも小さくなるから、図３に示すように、電磁アク
チュエータ１３がエンジン側に配されるようにエンジン
マウント１を設置すれば、電磁アクチュエータ１３に発
生する制御力Ｆaは小さくて済むようになるのである。From the above, in the case of R A > 1 (A u <A p ), the control force F a expressed by the above equation (1) is better than the control force F a expressed by the above equation (2). Also becomes smaller,
As shown in FIG. 2, while the engine mount 1 is installed so that the electromagnetic actuator 13 is arranged on the vehicle body side, R
In the case of A <1 (A u > A p ), the control force F a represented by the above formula (2) is the control force F represented by the above formula (1).
Since it is smaller than a, if the engine mount 1 is installed so that the electromagnetic actuator 13 is arranged on the engine side as shown in FIG. 3, the control force F a generated in the electromagnetic actuator 13 may be small. It will be.
【００２４】この結果、電磁アクチュエータ１３が発生
する制御力Ｆa を効率良く利用することができるから、
アクチュエータの配設位置等について特に言及していな
かった従来の流体マウントに比較し、同程度の性能のア
クチュエータを用いた場合には、防振効果が確実に向上
するようになる。さらに、上記（２）式で示す制御力Ｆ
a が発生するＲA ＜１（Ａu ＞Ａp ）の場合には、その
比ＲA の２乗ＲA 2 と、弾性体１１の支持方向のバネ定
数をＫp及び支持弾性体６の拡張方向のバネ定数をＫe
の比ＲK ＝Ｋp ／Ｋe に一致又は略一致させれば、電磁
アクチュエータ１３の制御力ＦA はさらに小さくて済む
ようになる。As a result, the control force F a generated by the electromagnetic actuator 13 can be efficiently used,
Compared to the conventional fluid mount, which does not particularly mention the position where the actuator is arranged, when using an actuator having the same level of performance, the vibration damping effect is surely improved. Furthermore, the control force F shown in the above equation (2)
In the case of R A <1 (A u > A p ), where a occurs, the ratio R A squared R A 2 , the spring constant of the elastic body 11 in the supporting direction, K p, and the supporting elastic body 6 are set. The spring constant in the expansion direction is K e
The control force F A of the electromagnetic actuator 13 can be further reduced by matching or substantially matching the ratio R K = K p / K e .
【００２５】これは、制御力Ｆa を比ＲA の関数とした
場合、ＲA ＝（Ｋp ／Ｋe ）1/2 でＦa が最低値をとる
からである。なお、上記実施例では、本発明に係る防振
支持装置を車両のエンジンを支持するエンジンマウント
１に適用した場合について説明したが、本発明の適用対
象はこれに限定されるものではなく、車両のエンジン以
外の振動体を支持する装置であってもよい。This is because when the control force F a is a function of the ratio R A , F a has the lowest value when R A = (K p / K e ) 1/2 . In addition, in the above-described embodiment, the case where the anti-vibration support device according to the present invention is applied to the engine mount 1 that supports the engine of the vehicle has been described. However, the application target of the present invention is not limited to this and the vehicle is applied. It may be a device that supports a vibrator other than the engine.
【００２６】また、上記実施例では、アクチュエータと
して電磁式のアクチュエータを適用した場合について説
明したが、可動部材１２を所定の周波数で変位させるこ
とができるアクチュエータであれば他の形式であっても
構わない。Further, in the above-mentioned embodiment, the case where the electromagnetic actuator is applied as the actuator has been described, but other types may be used as long as the actuator can displace the movable member 12 at a predetermined frequency. Absent.
【００２７】[0027]
【発明の効果】以上説明したように、本発明によれば、
主流体室における第１の部材の有効受圧面積と主流体室
における可動部材の受圧面積との大小関係に基づいて可
動部材を変位させるアクチュエータを振動体側又は支持
体側に配設する構成としたため、アクチュエータに発生
する力が小さくて済み、その結果、防振効果を向上する
ことができるという効果がある。As described above, according to the present invention,
The actuator for displacing the movable member based on the magnitude relationship between the effective pressure receiving area of the first member in the main fluid chamber and the pressure receiving area of the movable member in the main fluid chamber is arranged on the vibrating body side or the support body side. The force generated in the device is small, and as a result, the vibration damping effect can be improved.
【００２８】また、請求項２記載の発明であれば、さら
にアクチュエータに発生する力を小さくすることができ
るという効果がある。According to the second aspect of the invention, the force generated in the actuator can be further reduced.
【図１】本発明の一実施例の構成を示す断面図である。FIG. 1 is a sectional view showing a configuration of an embodiment of the present invention.
【図２】電磁アクチュエータを車体側に固定した場合の
モデルを示す図である。FIG. 2 is a diagram showing a model in which an electromagnetic actuator is fixed to a vehicle body side.
【図３】電磁アクチュエータをエンジン側に固定した場
合のモデルを示す図である。FIG. 3 is a diagram showing a model in which an electromagnetic actuator is fixed to the engine side.
１ エンジンマウント（防振支持装置） ２ 取付部材 ３ 内筒 ５ オリフィス構成体 ５ａ オリフィス ６ 支持弾性体 ７ 外筒 ８ アクチュエータ保持部材 ９ 取付部材 １０ 円筒部材 １１ 弾性体 １２ 可動部材 １３ 電磁アクチュエータ １５ 主流体室 １６ 副流体室 1 Engine Mount (Vibration Isolation Supporting Device) 2 Mounting Member 3 Inner Cylinder 5 Orifice Constituent 5a Orifice 6 Supporting Elastic Body 7 Outer Cylinder 8 Actuator Holding Member 9 Mounting Member 10 Cylindrical Member 11 Elastic Body 12 Movable Member 13 Electromagnetic Actuator 15 Main Fluid Chamber 16 Sub-fluid chamber
Claims (2)
１の部材と、前記振動体及び支持体の他方に固定される
第２の部材と、これら第１の部材及び第２の部材間に介
在する支持弾性体と、この支持弾性体によって画成され
た主流体室と、容積可変の副流体室と、これら主流体室
及び副流体室間を連通させるオリフィスと、前記主流体
室，副流体室及びオリフィス内に封入された流体と、前
記主流体室の隔壁の一部を形成し且つその主流体室の容
積を変化させる方向に変位可能に前記第２の部材側に配
設された可動部材と、前記第２の部材側に配設され且つ
前記可動部材を変位させるアクチュエータと、を備えた
防振支持装置において、前記主流体室における前記第１
の部材側の有効受圧面積が前記主流体室における前記可
動部材の受圧面積よりも小さい場合には前記第２の部材
を前記支持体側に固定し、前記主流体室における前記第
１の部材側の有効受圧面積が前記主流体室における前記
可動部材の受圧面積よりも大きい場合には前記第２の部
材を前記振動体側に固定することを特徴とする防振支持
装置。1. A first member fixed to one of a vibrating body and a support, a second member fixed to the other of the vibrating body and a support, and the first and second members. A supporting elastic body interposed therebetween, a main fluid chamber defined by the supporting elastic body, a sub-fluid chamber having a variable volume, an orifice for communicating between the main fluid chamber and the sub-fluid chamber, and the main fluid chamber , A fluid enclosed in the sub-fluid chamber and the orifice, and forming a part of the partition wall of the main fluid chamber and displaceable in the direction in which the volume of the main fluid chamber is changed, and disposed on the second member side An anti-vibration support device that includes a movable member that is disposed and an actuator that is disposed on the second member side and that displaces the movable member.
When the effective pressure receiving area on the member side is smaller than the pressure receiving area on the movable member in the main fluid chamber, the second member is fixed to the support side, and the second member on the first member side in the main fluid chamber is fixed. The anti-vibration support device characterized in that when the effective pressure receiving area is larger than the pressure receiving area of the movable member in the main fluid chamber, the second member is fixed to the vibrating body side.
圧面積Ａu が主流体室における可動部材の受圧面積Ａp
よりも大きい場合、前記有効受圧面積Ａu 及び受圧面積
Ａp の比ＲA ＝Ａp ／Ａu の２乗ＲA 2 と、前記可動部
材の支持バネ定数Ｋp 及び前記支持弾性体の拡張方向バ
ネ定数Ｋe の比ＲK ＝Ｋp ／Ｋe とを一致又は略一致さ
せる請求項１記載の防振支持装置。2. The effective pressure receiving area A u of the main fluid chamber on the side of the first member is the pressure receiving area A p of the movable member in the main fluid chamber.
Is larger than the ratio R A = A p / A u squared RA 2 of the effective pressure receiving area A u and the pressure receiving area A p , the support spring constant K p of the movable member and the expansion of the support elastic body. The anti-vibration support device according to claim 1, wherein the ratio R K = K p / K e of the directional spring constants K e is matched or substantially matched.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27041092A JPH06117476A (en) | 1992-10-08 | 1992-10-08 | Vibration control supporting device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27041092A JPH06117476A (en) | 1992-10-08 | 1992-10-08 | Vibration control supporting device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH06117476A true JPH06117476A (en) | 1994-04-26 |
Family
ID=17485878
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP27041092A Pending JPH06117476A (en) | 1992-10-08 | 1992-10-08 | Vibration control supporting device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06117476A (en) |
-
1992
- 1992-10-08 JP JP27041092A patent/JPH06117476A/en active Pending
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