JPH06103054B2 - Fluid filled type vibration absorber - Google Patents

Fluid filled type vibration absorber

Info

Publication number
JPH06103054B2
JPH06103054B2 JP4877985A JP4877985A JPH06103054B2 JP H06103054 B2 JPH06103054 B2 JP H06103054B2 JP 4877985 A JP4877985 A JP 4877985A JP 4877985 A JP4877985 A JP 4877985A JP H06103054 B2 JPH06103054 B2 JP H06103054B2
Authority
JP
Japan
Prior art keywords
fluid
vibration
filled type
frequency
type 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.)
Expired - Lifetime
Application number
JP4877985A
Other languages
Japanese (ja)
Other versions
JPS61206840A (en
Inventor
俊朗 阿部
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Priority to JP4877985A priority Critical patent/JPH06103054B2/en
Publication of JPS61206840A publication Critical patent/JPS61206840A/en
Publication of JPH06103054B2 publication Critical patent/JPH06103054B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
    • B60K5/12—Arrangement of engine supports
    • B60K5/125—Telescopic supports, e.g. telescopic dampers
    • 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)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Description

【発明の詳細な説明】 産業上の利用分野 本発明は流体封入式防振体に関し、とりわけ、内燃機関
等のように振動周波数が変化されるようになつた振動体
を支持する場合に用いられる流体封入式防振体に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid-filled vibration isolator, and more particularly, it is used for supporting a vibration body whose vibration frequency is changed, such as an internal combustion engine. The present invention relates to a fluid filled type vibration damping body.

従来の技術 この種流体封入式防振体としては、たとえば本出願人に
よつて特開昭61−119830号として出願されたものがあ
る。即ち、この流体封入式防振体はオリフイス内の可動
流体質量をマスとしてダイナミツク作用が行なわれるこ
とを本出願人が解明したことに基づいて出願されたもの
である。2. Description of the Related Art As this type of fluid-filled type vibration isolator, there is, for example, an application filed by the applicant of the present application as JP-A-61-119830. That is, this fluid-filled type vibration isolator was filed based on the fact that the applicant has clarified that the dynamic action is performed by using the mass of the movable fluid in the orifice as a mass.

発明が解決しようとする問題点 しかしながら、かかる従来の流体封入式防振体にあつて
は、連通路が１本でありその開口面積は一定となつてい
た。又、連通路を２本以上設けた場合にあつてもその全
体の開口面積はやはり一定となつていた。従つて、振動
に対して共振される連通路内の流体質量は常に一定であ
り、該流体質量の固有振動数は一定値に決定されてしま
う。このため、振動減衰しようとする周波数は、前記流
体質量の共振に基づくダイナミツクダンパ効果が発揮さ
れる振動領域によつて決定されてしまう。このため、車
両の内燃機関のように振動減衰しようとする周波数領域
が広い場合は、どうしても制振しきれない領域が存在
し、車体振動が誘起されてしまう。DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention However, in such a conventional fluid-filled type vibration isolator, there is one communicating passage and the opening area thereof is constant. Further, even when two or more communication passages are provided, the overall opening area is still constant. Therefore, the fluid mass in the communication passage resonated with vibration is always constant, and the natural frequency of the fluid mass is determined to be a constant value. Therefore, the frequency at which the vibration is about to be damped is determined by the vibration region in which the dynamic damper effect based on the resonance of the fluid mass is exhibited. For this reason, when the frequency range in which the vibration is to be damped is wide as in the internal combustion engine of the vehicle, there is a region where vibration cannot be completely suppressed, and vehicle body vibration is induced.

たとえば、エンジンが横置きとなつたＦ・Ｆ（フロント
エンジンフロントドライブ）車にあつては、パワーユニ
ツトの前後ロール変位を抑制するため該パワーユニツト
と車体間にバツフアロツドが取付けられるようになつて
いる。ところが、このバツフアロツドに前記流体封入式
防振体としての構造を取り入れたとしても、各変速段で
急加速時に発生する夫々異なる周波数域でのパワーユニ
ツト振動、特にガクガク振動の大きな原因となる第２速
段，第３速段での振動を共に減衰することができなくな
つてしまうという問題点がある。For example, in an F / F (front engine front drive) vehicle in which the engine is placed horizontally, a buffer rod is attached between the power unit and the vehicle body in order to suppress the front-rear roll displacement of the power unit. . However, even if the structure as the fluid filled type vibration isolator is incorporated into this buffer, the power unit vibration in each different frequency range generated at the time of sudden acceleration at each shift stage, especially the second cause of the jerky vibration is a large cause. There is a problem that the vibrations at the third speed and the third speed cannot be damped together.

そこで、本発明はかかる従来の問題点に鑑みて、連通路
内の流体質量を変化させることにより、該連通路内の流
体共振周波数を変化させ、もつて振動減衰できる周波数
領域を広げるようにした流体封入式防振体を提供するこ
とを目的とする。In view of the conventional problems, the present invention changes the fluid mass in the communication passage to change the fluid resonance frequency in the communication passage, thereby expanding the frequency range in which vibration can be damped. An object of the present invention is to provide a fluid filled type vibration damping body.

問題点を解決するための手段 かかる目的を達成するために本発明の流体封入式防振体
は、振動の入力方向に対して対向配置され、弾性的に容
積可変な第1,第２流体室と、これら第1,第２流体室を互
いに連通する複数の連通路と、少なくともこれら連通路
の１つに設けられる開閉弁と、ギヤ位置を検出する検出
手段と、この検出手段からの信号により前記ギヤ位置に
応じて前記開閉弁を開閉作動する制御手段とを備えるこ
とにより構成してある。Means for Solving the Problems In order to achieve the above object, the fluid filled type vibration damping body of the present invention is arranged so as to face the vibration input direction, and has elastically variable volume first and second fluid chambers. A plurality of communication passages that communicate these first and second fluid chambers with each other, an opening / closing valve provided in at least one of these communication passages, a detection unit that detects a gear position, and a signal from the detection unit. And a control means for opening and closing the on-off valve according to the gear position.

作用 以上の構成により本発明の流体封入式防振体にあつて
は、開閉弁により連通路が閉じられることにより、この
閉じられた連通路を介しての流体移動は行なわれなくな
る。従つて、前記開閉弁を開いた状態と閉じた状態とで
は、入力振動に対して共振される連通路内流体質量が変
化し、もつて減衰対象となる振動周波数領域を可変する
ことができる。このため、検出手段により入力されるギ
ヤ位置を検出し、制御手段で前記開閉弁を適宜開閉する
ことにより連通路内流体質量を変化させ、異なる入力振
動が夫々減衰されることになる。With the above-described structure, in the fluid filled type vibration damping body of the present invention, the communication passage is closed by the opening / closing valve, so that the fluid is not moved through the closed communication passage. Therefore, in the open state and the closed state of the on-off valve, the fluid mass in the communication passage resonated with the input vibration changes, and thus the vibration frequency range to be damped can be varied. Therefore, the gear position input by the detection unit is detected, and the control unit appropriately opens and closes the on-off valve to change the fluid mass in the communication passage, thereby damping different input vibrations.

実施例 以下、本発明の実施例を図に基づいて詳細に説明する。Example Hereinafter, an example of the present invention will be described in detail with reference to the drawings.

第１図は本発明の一実施例を示す流体封入式防振体を示
し、エンジンのロール変位を規制する際に用いられるバ
ツフアロツド１に適用した場合に例をとつて説明する。FIG. 1 shows a fluid filled type vibration damping body according to an embodiment of the present invention, and will be described as an example when it is applied to a buffer 1 used for regulating roll displacement of an engine.

即ち、該バツフアロツド１は両端部に１対の筒状体2,3
が同軸配置され、一方の筒状体２は他方の筒状体３側に
閉止壁2aを有する有底筒状に形成されると共に、他方の
筒状体３は両端に閉止壁3a,3bが設けられて密閉構造と
なつている。そして、前記一方の筒状体２の開放側はゴ
ム等で形成された弾性壁４で閉止され、この弾性壁４と
前記閉止壁2aとの間の密閉室を第１流体室５としてあ
る。また、前記弾性壁４の外側中央部には筒状体２内径
より小径の枠板６が加硫接着等により一体に固着され、
該枠板６には取付環７が固設されている。That is, the buffer rod 1 has a pair of cylindrical bodies 2, 3 at both ends.
Are arranged coaxially, one tubular body 2 is formed into a bottomed tubular shape having a closing wall 2a on the other tubular body 3 side, and the other tubular body 3 has closing walls 3a, 3b at both ends. It is provided and has a closed structure. The open side of the one tubular body 2 is closed by an elastic wall 4 made of rubber or the like, and a closed chamber between the elastic wall 4 and the closing wall 2a is a first fluid chamber 5. Further, a frame plate 6 having a diameter smaller than the inner diameter of the tubular body 2 is integrally fixed to the outer center portion of the elastic wall 4 by vulcanization adhesion or the like,
A mounting ring 7 is fixed to the frame plate 6.

一方、前記他方の筒状体３内には当該内側空間を軸方向
に２分割するダイヤフラム８が固設され、該ダイヤフラ
ム８と一方の閉止壁3a（図中左側）との間の密閉室を第
２流体室９とすると共に、前記ダイヤフラム８と他方の
密止壁3b（図中右側）との間の密閉室を空気室10として
ある。また、この空気室10内には筒状体３の周壁を貫通
して筒軸直角方向に、ゴム等の弾性部材で形成された取
付筒11が固設されている。On the other hand, a diaphragm 8 that axially divides the inner space into two is fixedly provided in the other tubular body 3, and a closed chamber between the diaphragm 8 and one closing wall 3a (left side in the drawing) is provided. A second fluid chamber 9 is provided, and a closed chamber between the diaphragm 8 and the other sealing wall 3b (right side in the figure) is provided as an air chamber 10. A mounting cylinder 11 formed of an elastic member such as rubber is fixedly provided in the air chamber 10 in a direction perpendicular to the cylinder axis, penetrating the peripheral wall of the cylinder 3.

前記第１流体室５と前記第２第１流体室９は、筒状体2,
3の互いに対向する閉止壁2a,3a間に支持される複数の連
通路としての主連通管12および副連通管１で連通されて
いる。尚、主連通管12は、その肉厚を十分に厚くして通
常のバツフアロツドの連結ロツドとしての機能を持た
せ、エンジンの変位に対する大荷重に十分耐えることが
できる強度を有している。尚、前記第1,第２流体室5,9
および主，副連通路管12,13内には作動流体たとえば水
が充填されていることは勿論である。The first fluid chamber 5 and the second first fluid chamber 9 are cylindrical bodies 2,
The main communication pipes 12 and the sub-communication pipes 1 serving as a plurality of communication passages supported between the three closed walls 2a and 3a facing each other are communicated with each other. The main communicating pipe 12 has a sufficient thickness to have a function as a connecting rod of a normal buffer rod, and has strength enough to withstand a large load against displacement of the engine. The first and second fluid chambers 5 and 9 are
Of course, the main and auxiliary communication pipes 12 and 13 are filled with a working fluid such as water.

前記副連通管13には開閉弁としてのソレノイドバルブ14
が設けられ、ソレノイド14aに励磁信号が入力されてい
る状態では、弁体14bは上昇して副連通管13を連通する
と共に、ソレノイド14aに消磁信号が入力されたときに
は前記弁体14bが下降して副連通管13を閉塞するように
なつている。A solenoid valve 14 as an opening / closing valve is provided on the auxiliary communication pipe 13.
Is provided and the excitation signal is input to the solenoid 14a, the valve body 14b rises to communicate the auxiliary communication pipe 13, and when the demagnetization signal is input to the solenoid 14a, the valve body 14b descends. The auxiliary communication pipe 13 is closed.

15は図外のトランスミツシヨンのギヤ位置（変速位置）
を検出するギヤ位置検出手段で、このギヤ位置検出手段
15を振動周波数の検出手段として用いてある。即ち、車
両を加速する場合、横置き式エンジンとなつたパワーユ
ニツトが前後に振動して車体のガクガク振動の原因とな
るが、該パワーユニツトの前後振動の周波数は各変速段
によつて異なることが知られている。従つて、各変速段
を検出することによつてバツフアロツド１に入力される
振動周波数をある程度予測することができる。尚、本実
施例にあつては、ガクガク振動が特に問題となる第２速
段と第３速段を前記ギヤ位置検出手段15で検出するよう
にしてある。15 is the gear position of the transmission (shift position) not shown
The gear position detecting means for detecting
15 is used as a vibration frequency detection means. That is, when accelerating the vehicle, the power unit, which is a horizontal engine, vibrates back and forth and causes rattling vibrations of the vehicle body, but the frequency of the front and rear vibrations of the power unit varies depending on each shift stage. It has been known. Therefore, the vibration frequency input to the buffer 1 can be predicted to some extent by detecting each shift speed. In the present embodiment, the gear position detecting means 15 detects the second speed and the third speed, in which jerky vibration is a particular problem.

そして、前記ギヤ位置検出手段15で検出されたギヤ位置
信号は、前記ソレノイド14aに励磁信号および消磁信号
を出力する制御手段16に入力され、第２速段の時はエン
ジン前後振動の周波数が低いと判断してソレノイド14a
に消磁信号を出力すると共に、第３速段の時は前記周波
数が高いと判断してソレノイド14aに励磁信号を出力す
るようになつている。The gear position signal detected by the gear position detection means 15 is input to the control means 16 which outputs an excitation signal and a demagnetization signal to the solenoid 14a, and the frequency of the engine longitudinal vibration is low at the second speed. Solenoid 14a
In addition to outputting the demagnetization signal to the solenoid 14a, at the time of the third speed, it is determined that the frequency is high and the excitation signal is output to the solenoid 14a.

以上の構成により本実施例のバツフアロツド１は、第２
図に示すように第１流体室５側に設けられた取付環７が
パワーユニツトＡ側に取付けられると共に、第２流体室
９側に設けられた取付筒11が車体側Ｂに取付けられ、パ
ワーユニツトに発生する振動が前記取付環7,取付筒11を
結ぶ作用力線Ｘ方向に作用するようになつている。尚、
Ｐは弾性主軸で、この弾性主軸Ｐを中心にパワーユニツ
トＡは前後振動される。With the above configuration, the buffer pad 1 of the present embodiment is the second
As shown in the figure, the mounting ring 7 provided on the first fluid chamber 5 side is mounted on the power unit A side, and the mounting cylinder 11 provided on the second fluid chamber 9 side is mounted on the vehicle body side B. The vibration generated in the unit acts in the direction of the force line X connecting the mounting ring 7 and the mounting cylinder 11. still,
P is an elastic main shaft, and the power unit A is oscillated back and forth around the elastic main shaft P.

そして、振動周波数が低い第２速段時にはソレノイドバ
ルブ14が開弁して副連通管13を連通するため、第1,第２
流体室5,9内の流体は主連通管12および副連通管13の両
者を介して移動できるようになつていると共に、振動周
波数が高い第３速段時には、ソレノイドバルブ14が閉弁
して副連通管13を閉塞するため、主連通管12のみを介し
て流体移動できるようになつている。Then, at the second speed where the vibration frequency is low, the solenoid valve 14 opens to connect the auxiliary communication pipe 13, so that the first, second
The fluid in the fluid chambers 5 and 9 can be moved through both the main communication pipe 12 and the sub communication pipe 13, and the solenoid valve 14 is closed at the third speed where the vibration frequency is high. Since the sub communication pipe 13 is closed, the fluid can be moved only through the main communication pipe 12.

ところで、一般に流体封入式防振体は、振動入力側の流
体室の拡張弾性およびダイヤフラム，空気室による弾性
をばねとし、オリフイス内の流体を質量とする共振現象
により振動伝達特性が支配されることが本出願人によつ
て解析されており、特に振動減衰作用に着目すると流体
封入式防振体はダイナミツクダンバであることが証明さ
れている。従つて、かかる理論を本実施例のバツフアロ
ツド１にあてはめてみると、流体室の拡張弾性は第１流
体室５の弾性壁４における剪断方向（図中左右方向）の
ばね定数であり、この弾性壁４の剪断方向ばね定数と、
ダイヤフラム８および空気室10で構成される弾性による
ばね定数とが全体のばね定数となり、かつ主，副連通管
12,13内の流体質量を質量体とする共振現象である。
尚、該連通管12,13内の流体質量mdを考える場合、この
質量mdは等価可動流体質量として表わされ、実際の連通
管12,13内流体質量ｍに、第１流体室５の有効受圧面積a
1を連通管12,13の断面積a2で除した値の二乗を乗した値
で与えられる。即ち、 となる。そして、前記ばね定数および等可動流体質量で
決定される連通管12,13内の流体共振周波数によつて振
動の減衰周波数が決定される。By the way, generally, in a fluid-filled type vibration isolator, the vibration transfer characteristics are dominated by the resonance phenomenon in which the expansion elasticity of the vibration chamber on the vibration input side and the elasticity of the diaphragm and the air chamber are used as springs, and the fluid in the orifice is the mass. Has been analyzed by the applicant of the present invention, and it has been proved that the fluid-filled type vibration isolator is a dynamic damper, especially when focusing on the vibration damping action. Therefore, when applying this theory to the buffer rod 1 of this embodiment, the expansion elasticity of the fluid chamber is the spring constant in the shearing direction (left and right direction in the figure) of the elastic wall 4 of the first fluid chamber 5, and this elasticity The shear direction spring constant of the wall 4,
The spring constant due to elasticity constituted by the diaphragm 8 and the air chamber 10 becomes the overall spring constant, and the main and auxiliary communication pipes
This is a resonance phenomenon in which the mass of fluid in 12 and 13 is a mass body.
When considering the fluid mass md in the communication pipes 12 and 13, this mass md is expressed as an equivalent movable fluid mass, and the actual fluid mass m in the communication pipes 12 and 13 is calculated based on the effective mass of the first fluid chamber 5. Pressure receiving area a
It is given as the value obtained by multiplying the square of the value obtained by dividing 1 by the cross-sectional area a 2 of the communication tubes 12, 13. That is, Becomes Then, the damping frequency of the vibration is determined by the fluid resonance frequency in the communication pipes 12 and 13 determined by the spring constant and the equal movable fluid mass.

一方、前記連通管12,13内流体の共振周波数は、一般に
ばね定数を質量で除した値の平方根に比例するため、質
量が大きくなることにより共振周波数は低くなる一方、
質量が小さくなることにより共振周波数は高くなる。従
つて、本実施例では第２速段で主，副連通管12,13を連
通して、連通管内の流体質量を大きくすることにより、
低周波側のパワーユニツト振動を有効に抑制できる。On the other hand, the resonance frequency of the fluid in the communication pipes 12 and 13 is generally proportional to the square root of the value obtained by dividing the spring constant by the mass, so that the resonance frequency becomes lower as the mass increases,
The resonance frequency increases as the mass decreases. Therefore, in this embodiment, by connecting the main and auxiliary communication pipes 12 and 13 at the second speed to increase the fluid mass in the communication pipe,
The power unit vibration on the low frequency side can be effectively suppressed.

一方、第３速段で副連通管13を閉塞して主連通路12のみ
を連通させることにより、連通管内の流体質量を小さく
して高周波側のパワーユニツト振動を有効に抑制でき
る。このように、加速時の振動周波数領域が夫々異なる
パワーユニツト振動が抑制されることにより、特に問題
となつていた第２速段，第３速段時のガクガク振動を共
に防止若しくは大幅に減少させることができる。On the other hand, by closing the auxiliary communication pipe 13 and communicating only the main communication passage 12 at the third speed, the fluid mass in the communication pipe can be reduced and the power unit vibration on the high frequency side can be effectively suppressed. In this way, by suppressing the power unit vibrations in which the vibration frequency regions at the time of acceleration are different from each other, the jerky vibrations at the second speed and the third speed, which are particularly problematic, are both prevented or significantly reduced. be able to.

ところで、前記主連通管12および副連通管13の内径は、
両連通管12,13の内径合計が第２速段時の発生周波数に
対応し、主連通管12のみの内径が第３速段時の発生周波
数に対応するよう決定されていることは勿論であり、本
実施例にあつては主連通管12内径が大きく、副連通管13
内径が小さくなつている。By the way, the inner diameters of the main communication pipe 12 and the sub communication pipe 13 are
Of course, it is decided that the total inner diameter of both communication pipes 12 and 13 corresponds to the generation frequency at the second speed stage, and the inner diameter of only the main communication pipe 12 corresponds to the generation frequency at the third speed stage. In the present embodiment, the main communication pipe 12 has a large inner diameter and the sub communication pipe 13 has a large inner diameter.
The inner diameter is getting smaller.

尚、本実施例では流体封入式防振体がバツフアロツドに
適用された場合に例にとつて述べたが、これに限ること
なく一般に用いられる防振体たとえばエンジンマウント
等に適用してもよいことはいうまでもない。In this embodiment, the fluid-filled type vibration isolator has been described as an example in the case of being applied to a buffer, but it is not limited to this and may be applied to a commonly used vibration isolator such as an engine mount. Needless to say.

また、本実施例ではオリフィスとして用いた連通管を
主，副２本用いて２種類の振動周波数領域の振動減衰す
るようにしてあるが、更に開閉弁を設けた連通管を増設
し、３種類以上の振動周波数領域を減衰するようにして
もよいことは勿論である。Further, in the present embodiment, the communication pipe used as the orifice is used to attenuate the vibration in two types of vibration frequency regions by using two main and sub communication pipes. Of course, the above vibration frequency range may be attenuated.

発明の効果 以上説明したように本発明の流体封入式防振体にあつて
は、振動周波数に応じて全体的な連通路の開口面積を変
化させることができるため、連通路内の流体質量が変化
されて当該該連通路内流体の共振周波数を前記振動周波
数に応じて可変とすることができる。従つて、１つの流
体封入式防振体で複数の振動周波数領域を夫々減衰する
ことができるという優れた効果を奏する。EFFECTS OF THE INVENTION As described above, in the fluid filled type vibration damping body of the present invention, since the overall opening area of the communication passage can be changed according to the vibration frequency, the fluid mass in the communication passage can be changed. The resonance frequency of the fluid in the communication passage that has been changed can be made variable according to the vibration frequency. Therefore, there is an excellent effect that one fluid-filled type vibration isolator can respectively attenuate a plurality of vibration frequency regions.

【図面の簡単な説明】[Brief description of drawings]

第１図は本発明の流体封入式防振体の一実施例を示す断
面図、第２図は本発明の流体封入式防振体の取付状態を
示す概略構成図である。 １……バツフアロツド（流体封入式防振体）、５……第
１流体室、９……第２流体室、12……主連通管（連通
路）、13……副連通管（連通路）、14……ソレノイドバ
ルブ（開閉弁）、15……ギヤ位置検出手段（振動周波数
の検出手段）、16……制御手段。FIG. 1 is a sectional view showing an embodiment of the fluid filled type vibration damping body of the present invention, and FIG. 2 is a schematic configuration diagram showing the mounting state of the fluid filled type vibration damping body of the present invention. 1 …… But float (fluid filled vibration isolator), 5 …… First fluid chamber, 9 …… Second fluid chamber, 12 …… Main communication pipe (communication passage), 13 …… Sub communication pipe (communication passage) , 14 …… Solenoid valve (open / close valve), 15 …… Gear position detection means (vibration frequency detection means), 16 …… Control means.

Claims (1)

【特許請求の範囲】[Claims] 【請求項１】振動の入力方向に対して対向配置され、弾
性的に容積可変な第1,第２流体室と、これら第1,第２流
体室を互いに連通する複数の連通路と、少なくともこれ
ら連通路の１つに設けられる開閉弁と、ギヤ位置を検出
する検出手段と、この検出手段からの信号により前記ギ
ヤ位置に応じて前記開閉弁を開閉作動する制御手段とを
備えたことを特徴とする流体封入式防振体。1. A first fluid chamber and a second fluid chamber, which are arranged to face each other in a vibration input direction and have elastically variable volumes, and a plurality of communication passages for communicating the first fluid chamber with the second fluid chamber. An on-off valve provided in one of these communication passages, a detection means for detecting a gear position, and a control means for opening and closing the on-off valve according to the gear position by a signal from the detection means are provided. Characteristic fluid-filled type vibration damping body.
JP4877985A 1985-03-12 1985-03-12 Fluid filled type vibration absorber Expired - Lifetime JPH06103054B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP4877985A JPH06103054B2 (en) 1985-03-12 1985-03-12 Fluid filled type vibration absorber

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP4877985A JPH06103054B2 (en) 1985-03-12 1985-03-12 Fluid filled type vibration absorber

Publications (2)

Publication Number Publication Date
JPS61206840A JPS61206840A (en) 1986-09-13
JPH06103054B2 true JPH06103054B2 (en) 1994-12-14

Family

ID=12812739

Family Applications (1)

Application Number Title Priority Date Filing Date
JP4877985A Expired - Lifetime JPH06103054B2 (en) 1985-03-12 1985-03-12 Fluid filled type vibration absorber

Country Status (1)

Country Link
JP (1) JPH06103054B2 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63125838A (en) * 1986-11-13 1988-05-30 Mazda Motor Corp Mounting device for power unit
JPH03503923A (en) * 1988-12-22 1991-08-29 ムーグ　インコーポレーテツド Machine mount for vibration isolation
JP5012746B2 (en) * 2008-09-24 2012-08-29 日産自動車株式会社 Liquid filled torque rod

Also Published As

Publication number Publication date
JPS61206840A (en) 1986-09-13

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