JPH024816B2 - - Google Patents
Info
- Publication number
- JPH024816B2 JPH024816B2 JP24033584A JP24033584A JPH024816B2 JP H024816 B2 JPH024816 B2 JP H024816B2 JP 24033584 A JP24033584 A JP 24033584A JP 24033584 A JP24033584 A JP 24033584A JP H024816 B2 JPH024816 B2 JP H024816B2
- Authority
- JP
- Japan
- Prior art keywords
- working
- chamber
- orifice
- partition
- valve body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000012528 membrane Substances 0.000 claims description 34
- 239000007788 liquid Substances 0.000 claims description 33
- 239000012530 fluid Substances 0.000 claims description 27
- 238000005192 partition Methods 0.000 claims description 25
- 230000005284 excitation Effects 0.000 description 9
- 238000000465 moulding Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 239000004744 fabric Substances 0.000 description 3
- 238000013016 damping Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000013013 elastic material Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000004073 vulcanization Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000011162 core material Substances 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
- F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
- F16F13/106—Design of constituent elastomeric parts, e.g. decoupling valve elements, or of immediate abutments therefor, e.g. cages
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Description
【発明の詳細な説明】
産業上の利用分野
本発明は弾性体と隔壁とで作動液室を形成し、
この作動液室の外側に前記隔壁と仕切部材とで平
衡液室を形成し、この平衡液室と前記作動液室と
を連通するオリフイスを前記仕切部材に形成した
液体入り防振体のバルブ装置に関する。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention forms a hydraulic fluid chamber with an elastic body and a partition,
A liquid-filled vibration isolator valve device in which an equilibrium liquid chamber is formed outside the working liquid chamber by the partition wall and the partition member, and an orifice communicating the equilibrium liquid chamber and the working liquid chamber is formed in the partition member. Regarding.
従来の技術
一般に、液体入り防振体に匿伝わる振動の加振
周波数と振幅との関係は周波数の高帯域では振幅
が小さく、低帯域のそれは大きい。この高帯域と
低帯域とは対象とする加振周波数範囲における周
波数の高い領域、低い領域という相対的なものを
示すものであり、ここではエンジンマウントとし
て使用した場合について説明するので、例えば０
〜約30Hzを低帯域、約30〜150Hzを中帯域、約150
Hz以上を高帯域として区別している。BACKGROUND ART In general, the relationship between the excitation frequency and amplitude of vibrations transmitted privately to a liquid-filled vibration isolator is that the amplitude is small in a high frequency band and large in a low frequency band. The high band and low band refer to the relative high and low frequency areas in the target excitation frequency range, and here we will explain the case where it is used as an engine mount, so for example 0
~ About 30Hz low band, about 30~150Hz medium band, about 150
Hz and above are classified as high bands.
ところで従来のこの種の液体入り防振体として
は、作動液室と平衡液室とを複数のオリフイスで
連通し、一方のオリフイスに低帯域の大振幅時に
閉弁し高帯域の小振幅時に開弁するバルブ機構を
配設し、加振周波数が低帯域の間は前記他方のオ
リフイスに流体を通して減衰効果、所謂ロスフア
タを得てカーシエイクを低減すると共に、高帯域
の間はバルブ機構の開弁により全部のオリフイス
に流体を通して防振全体の動ばね定数を所定値に
設定して振動伝達を低下し、こもり音を減少する
ようにしたものがある。これを第８，９図に示し
て説明すると、１は支持部材を示し、車体に固定
する第１部材２と、パワーユニツトを固定する第
２支持部材３とからなる。この第１支持部材２に
結合した筒状体４の内周面に弾性体５を加硫接着
し、この弾性体５の頂面に第２支持部材３を加硫
接着して、支持部材１に弾性体５を一体に組付け
てある。この弾性体５にはその下面中央に形成し
た空洞の開口を剛性の高い隔壁６で閉塞し、その
空洞内に流体を封入して作動液室７を形成してあ
る。この作動液室７の隔壁６の外側に平衡液室８
を、可撓体９とそれの外周に加硫接着した取付部
材１０とからなる仕切部材１１との共働で形成し
てある。そして、前記作動液室７と平衡液室８と
は作動膜体１８と螺旋状に開けられたオリフイス
１３により連通されている。前記作動膜体１８に
は、弾性体５に伝わる振動の低帯域の大振幅振動
でバネ定数が高く、高帯域の小振幅振動ではバネ
定数を低くする機構となつている。 By the way, in conventional liquid-filled vibration isolators of this type, the working liquid chamber and the equilibrium liquid chamber are connected through a plurality of orifices, and one orifice has a valve that closes when the amplitude is large in the low band and opens when the amplitude is small in the high band. A valve mechanism is installed to reduce car shake by passing fluid through the other orifice to obtain a damping effect, a so-called loss factor, when the excitation frequency is in a low frequency band, and to reduce car shake by opening the valve mechanism during a high frequency band. There is one in which the dynamic spring constant of the entire vibration isolation is set to a predetermined value by passing fluid through all the orifices to reduce vibration transmission and muffled noise. This will be explained with reference to FIGS. 8 and 9. Reference numeral 1 indicates a support member, which is composed of a first member 2 that is fixed to the vehicle body and a second support member 3 that fixes the power unit. An elastic body 5 is vulcanized and bonded to the inner peripheral surface of the cylindrical body 4 coupled to the first support member 2, and a second support member 3 is vulcanized and bonded to the top surface of this elastic body 5. An elastic body 5 is integrally assembled to the. The opening of a cavity formed in the center of the lower surface of the elastic body 5 is closed with a highly rigid partition wall 6, and fluid is sealed in the cavity to form a hydraulic fluid chamber 7. An equilibrium liquid chamber 8 is located outside the partition wall 6 of this working liquid chamber 7.
is formed in cooperation with a partition member 11 consisting of a flexible body 9 and a mounting member 10 vulcanized and bonded to the outer periphery of the flexible body 9. The working fluid chamber 7 and the equilibrium fluid chamber 8 are communicated with each other through a working membrane body 18 and an orifice 13 opened in a spiral shape. The actuating membrane body 18 has a mechanism in which the spring constant is high when the vibration is transmitted to the elastic body 5 and has a large amplitude in a low band, and the spring constant is low when the vibration is small in a high amplitude band.
弁体１６は弾性体を平坦状に形成されて芯材と
しての布１７を有する作動膜体１８と、この作動
膜体１８の外周に加硫接着したリング部材１９と
で構成されている。 The valve body 16 is composed of an actuating membrane body 18 made of a flat elastic body and having a cloth 17 as a core material, and a ring member 19 vulcanized and bonded to the outer circumference of the actuating membrane body 18.
発明が解決しようとする問題点
ところが、前述の構造においては、作動膜体１
８における弾性材のたわみを非線形バネ特性にし
低帯域大振幅時に流体を他方のオリフイス１３に
流通しやすくして所要のロスフアクタを得るよう
にしてあるので、ロスフアクタが布１７の張り具
合に左右され易い。しかも作動膜体１８のばね定
数を大きくして防振体全体の動ばね定数の低レベ
ル領域を高帯域まで延ばす場合には弾性材の素
材、硬度等の変更によりばね定数を大きくしなけ
ればならず、弁体１６の製作が大変である。さら
に、加硫接着により作動膜体１８とリング部材１
９とを接合した弁体１６のばね特性の非線形領域
を微調整することができない。Problems to be Solved by the Invention However, in the above structure, the working membrane body 1
Since the deflection of the elastic material at 8 is made into a non-linear spring characteristic and the fluid flows easily to the other orifice 13 during low band and large amplitude to obtain the required loss factor, the loss factor is easily influenced by the tension of the cloth 17. . Moreover, in order to extend the low-level region of the dynamic spring constant of the entire vibration isolator to a high band by increasing the spring constant of the actuating membrane 18, the spring constant must be increased by changing the material, hardness, etc. of the elastic material. First, manufacturing the valve body 16 is difficult. Further, the actuating membrane body 18 and the ring member 1 are bonded by vulcanization.
It is not possible to finely adjust the non-linear region of the spring characteristics of the valve body 16 joined with the valve body 9.
そこで本発明は、弁体におけるリング部材を接
合した作動膜体のばね定数を調節して、防振体全
体の動ばね定数の低レベル安定領域を高帯域まで
延ばしたり、低帯域でのロスフアクタを向上した
りすることができる液体入り防振体のバルブ装置
を提供するものである。 Therefore, the present invention adjusts the spring constant of the actuating membrane body to which the ring member of the valve body is joined, to extend the low-level stable region of the dynamic spring constant of the entire vibration isolator to a high band, and to reduce the loss factor in the low band. The present invention provides a valve device for a liquid-filled vibration isolator that can be improved.
問題点を解決するための手段
本発明にあつては、作動液室と平衡液室とを連
通するオリフイスに作動膜体とリング部材とから
なる弁体を遊嵌して、前記オリフイスを低帯域大
振幅振動で閉塞し高帯域小振幅振動で開放するよ
うにした構成であつて、前記弁体の作動膜体に接
合したリング部材の内径を縮小成形して作動膜体
をたわみ変形してある。Means for Solving the Problems In the present invention, a valve body consisting of a working membrane body and a ring member is loosely fitted into an orifice communicating a working liquid chamber and an equilibrium liquid chamber, and the orifice is connected to a low band The structure is such that it is closed by large-amplitude vibrations and opened by high-band small-amplitude vibrations, and the inner diameter of a ring member joined to the working membrane body of the valve body is reduced and the working membrane body is flexibly deformed. .
実施例
以下、本発明の実施例を図面と共に従来の構造
と同一部分に同一符号を付して詳述する。Embodiments Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings, in which the same parts as the conventional structure are denoted by the same reference numerals.
つまり第１〜３図において、支持部材１は例え
ば図外の車体に固定するハツト形の第１支持部材
２と、例えばパワーユニツトに固定する略截頭逆
円錐形の第２支持部材３とで構成されている。こ
の第１支持部材２の外周フランジ２ａに巻締結合
した筒状体４の内周面に弾性体５を加硫接着し、
この弾性体５の頂面に第２支持部材３を加硫接着
し、これにより支持部材１に弾性体５を一体に組
付けてある。弾性体５の第１支持部材２と遊離す
る下面中央には下部開放山形の空洞を形成し、こ
の空洞の開口を剛性の高い隔壁６で被覆すると共
に、この空洞内に流体を封入することにより、弾
性体５と隔壁６とで作動液室７が形成されてい
る。この作動液室７の外側には隔壁６と仕切部材
１１Ａとで平衡液室８Ａが形成してある。この仕
切部材８Ａは金属製の取付部材１０を備えてお
り、この取付部材１０が第１支持部材２の外周フ
ランジ２ａと共に筒状体４で巻締結合されてい
る。この取付部材１０と筒状体４とで隔壁６が挾
持されている。この隔壁６と筒状体４との間には
弾性体５の空洞下部周縁に延長した部分が介在さ
れている。また平衡液室８Ａは環状の第１平衡液
室２０とこの第１平衡液室２０の内側に仕切部材
１１Ａの剛性の高い内筒２２を境として仕切られ
た第２平衡液室２１とからなる。前記仕切部材１
１Ａにおける取付部材１０と内筒２２との間の下
部開口を閉塞して第１平衡液室２０の底部となる
可撓膜９Ａのばね定数は、仕切部材１１Ａにおけ
る内筒２２の下部開口を閉塞して第２平衡液室２
１の底部となる可撓膜９Ｂのばね定数よりも小さ
く設定されている。また、前記第１平衡液室２０
は隔壁６に形成した螺旋状のオリフイス１３によ
つて作動液室７に連通され、第２平衡液室２１は
直状のオリフイス１２によつて作動液室７に連通
されている。このオリフイス１２には、該オリフ
イス１２の中間部に形成した弁体収納室１５とこ
の弁体収納室１５に遊嵌した弁体１６Ａとで構成
されて、該オリフイス１２を弾性体５に伝わる振
動の大振幅振動で閉塞し、小振幅振動で開放する
バルブ機構１４Ａを配設してある。前記弁体１６
Ａは作動膜体１８Ａとこの作動膜体１８Ａの外周
に加硫接着して接合したリング部材１９Ａとから
なる。この作動膜体１８Ａに接合したリング部材
１９Ａの内径は縮小形成されて作動膜体１８Ａを
波状にたわみ変形させている。前記リング部材１
９Ａの縮小成形は、例えば第３図に示すように、
リング部材１９Ａに作動膜体１８Ａを平坦状に接
合した弁体１６Ａを、治具Ａのテーパ孔Ｂに大口
部側から押込んで小口部側に通すことにより、リ
ング部材１９Ａがしぼられて塑性変形を受けて形
成される。 In other words, in FIGS. 1 to 3, the support member 1 includes, for example, a hat-shaped first support member 2 that is fixed to a vehicle body (not shown), and a substantially truncated cone-shaped second support member 3 that is fixed to, for example, a power unit. It is configured. An elastic body 5 is vulcanized and bonded to the inner peripheral surface of the cylindrical body 4 which is wound and fastened to the outer peripheral flange 2a of the first support member 2,
The second support member 3 is vulcanized and adhered to the top surface of the elastic body 5, thereby integrally assembling the elastic body 5 to the support member 1. By forming a lower-open chevron-shaped cavity in the center of the lower surface of the elastic body 5 that is free from the first support member 2, and covering the opening of this cavity with a highly rigid partition wall 6, and sealing a fluid in this cavity. , a hydraulic fluid chamber 7 is formed by the elastic body 5 and the partition wall 6. An equilibrium liquid chamber 8A is formed outside the working liquid chamber 7 by the partition wall 6 and the partition member 11A. The partition member 8A includes a metal attachment member 10, which is wound and fastened together with the outer peripheral flange 2a of the first support member 2 around the cylindrical body 4. The partition wall 6 is held between the mounting member 10 and the cylindrical body 4. A portion extending to the lower periphery of the cavity of the elastic body 5 is interposed between the partition wall 6 and the cylindrical body 4. The equilibrium liquid chamber 8A is composed of an annular first equilibrium liquid chamber 20 and a second equilibrium liquid chamber 21 partitioned inside the first equilibrium liquid chamber 20 by a highly rigid inner cylinder 22 of the partition member 11A. . The partition member 1
The spring constant of the flexible membrane 9A, which closes the lower opening between the mounting member 10 and the inner cylinder 22 in the partition member 11A and forms the bottom of the first equilibrium liquid chamber 20, closes the lower opening of the inner cylinder 22 in the partition member 11A. and the second equilibrium liquid chamber 2
The spring constant is set smaller than the spring constant of the flexible membrane 9B, which forms the bottom part of the flexible membrane 9B. Further, the first equilibrium liquid chamber 20
is communicated with the hydraulic fluid chamber 7 through a spiral orifice 13 formed in the partition wall 6, and the second equilibrium fluid chamber 21 is communicated with the hydraulic fluid chamber 7 through a straight orifice 12. This orifice 12 is composed of a valve body storage chamber 15 formed in the middle part of the orifice 12 and a valve body 16A loosely fitted in the valve body storage chamber 15. A valve mechanism 14A is provided which closes with large amplitude vibration and opens with small amplitude vibration. The valve body 16
A is composed of a working membrane body 18A and a ring member 19A bonded to the outer periphery of the working membrane body 18A by vulcanization bonding. The inner diameter of the ring member 19A joined to the actuating membrane body 18A is reduced to cause the actuating membrane body 18A to bend and deform in a wave-like manner. Said ring member 1
For example, the reduction molding of 9A is as shown in Fig. 3.
The ring member 19A is squeezed and plastically deformed by pushing the valve body 16A, which has the ring member 19A and the actuating membrane 18A flatly joined, into the tapered hole B of the jig A from the large opening side and passing it through the small opening side. It is formed in response to
以上の実施例構造によれば、弾性体５の加振周
波数が低帯域の場合には、作動液室７の流体の振
幅も大きく、作動液室７側から第２平衡液室２１
側若しくは第２平衡液室２１側から作動液室７側
に向けてオリフイス１２内を流動する流体が、該
オリフイス１２から弁体収納室１５内に移動して
弁体１６Ａの作動膜体１８Ａを押し、この作動膜
体１８Ａがたわみ変形されていることによつて第
２図に仮想線で示すように上下方向に大きく弾性
変形を受けて、弁体収納室１５の底面または天井
のオリフイス１２まわりに密接してオリフイス１
２を閉塞する。したがつて、流体が作動液室７と
第１平衡液室２０とにオリフイス１３を通つて流
動してロスフアクタを受け、振動が減衰される。
一方、弾性体５の加振周波数が高帯域の場合に
は、作動液室７の流体の振幅も小さく、作動膜体
１８Ａの上下方向の変形も小さくかつ多く繰返え
されるので、オリフイス１２が開放状態となり、
流体が弁体１６Ａと弁体収納室１５との間の隙間
ならびにオリフイス１２を通つて、第２平衡液室
２１と作動液室７とにも流動し、弾性体５、作動
液室７および平衡液室８Ａの全体によつて形成さ
れる防振体の動ばね定数の低レベル安定領域を高
帯域まで延ばすことができる。第４図は前記弁体
１６Ａにおける加振周波数と防振体の動ばね定数
との関係を、作動膜体１８Ａのばね定数をフアク
タとして測定した結果を示すものであり、作動膜
体１８Ａのばね定数を大きくすることにより動ば
ね定数の低レベル安定領域が高帯域まで延びる。
また、第５図は前記弁体１６Ａにおける加振周波
数の低帯域とロスフアクタとの関係をリング部材
１９Ａの縮小成形率（しぼり率）をフアクタとし
て測定したものであり、縮小成形率が小さくなる
にしたがつてロスフアクタが大きくなつている。
この第４図と第５図の測定結果から明らかなよう
に、リング部材１９Ａの縮小成形率を変更するこ
とによつて弁体１６Ａのばね特性の非線形領域を
微調整して、防振体の動ばね定数の低レベル安定
領域を高帯域まで延ばすことができて、低帯域の
ロスフアクタを大きくすることができる。 According to the above embodiment structure, when the excitation frequency of the elastic body 5 is in a low band, the amplitude of the fluid in the hydraulic fluid chamber 7 is also large, and the second equilibrium fluid chamber 21 is moved from the hydraulic fluid chamber 7 side.
The fluid flowing in the orifice 12 from the side or the second equilibrium liquid chamber 21 side toward the working liquid chamber 7 side moves from the orifice 12 into the valve body storage chamber 15 and moves the working membrane body 18A of the valve body 16A. Due to the bending and deformation of the actuating membrane body 18A, the actuating membrane body 18A undergoes large elastic deformation in the vertical direction as shown by the imaginary line in FIG. Orifice 1 in close proximity to
Block 2. Therefore, fluid flows into the working fluid chamber 7 and the first equilibrium fluid chamber 20 through the orifice 13 and is subjected to loss factors, thereby damping vibrations.
On the other hand, when the excitation frequency of the elastic body 5 is in a high band, the amplitude of the fluid in the working fluid chamber 7 is also small, and the vertical deformation of the working membrane body 18A is small and repeated many times. It becomes open,
The fluid flows through the gap between the valve body 16A and the valve body storage chamber 15 and the orifice 12, and also flows into the second equilibrium liquid chamber 21 and the working liquid chamber 7. The low-level stable region of the dynamic spring constant of the vibration isolator formed by the entire liquid chamber 8A can be extended to a high band. FIG. 4 shows the result of measuring the relationship between the excitation frequency of the valve body 16A and the dynamic spring constant of the vibration isolator using the spring constant of the actuating membrane body 18A as a factor. By increasing the constant, the low-level stable region of the dynamic spring constant extends to a high band.
Furthermore, FIG. 5 shows the relationship between the low band of the excitation frequency and the loss factor in the valve body 16A, measured using the reduction molding rate (wringing rate) of the ring member 19A as a factor, and as the reduction molding rate becomes smaller, Therefore, the loss factor is increasing.
As is clear from the measurement results in FIGS. 4 and 5, by changing the reduction molding rate of the ring member 19A, the nonlinear region of the spring characteristics of the valve body 16A can be finely adjusted, and the vibration isolator can be improved. The low-level stable region of the dynamic spring constant can be extended to the high band, and the loss factor in the low band can be increased.
ここで前記実施例においては作動膜体１８Ａを
波状にたわみ変形したものを例示して説明した
が、第６図に示すように作動膜体１８Ｂを円弧状
にたわみ変形したり、第７図に示すようにたわみ
変形した作動膜体１８Ｂを布１７入りに構成した
場合でも同様の効果がある。 In the above embodiment, the working membrane body 18A is flexibly deformed into a wave shape. However, as shown in FIG. As shown, the same effect can be obtained even when the actuating membrane body 18B, which has been deflected and deformed, is made of cloth 17.
なお、本発明にあつては、リング部材の縮小成
形はリング部材の素材選定に伴ない機械的以外の
例えば加熱手段によつても可能である。 In addition, in the present invention, the reduction molding of the ring member can also be performed by means other than mechanical, for example, heating means, depending on the material selection of the ring member.
発明の効果
以上のように本発明によれば、作動膜体を接合
したリング部材の内径を縮小成形して作動膜体を
たわみ変形した簡単な構造でありながら、リング
部材の縮小成形率の変更により弁体のばね特性の
非線形領域を微調整して、防振体の動ばね定数の
低レベル安定領域を高帯域まで延ばすことができ
るうえ、低帯域でのロスフアクタを大きくするこ
とができる実用上大なる効果がある。Effects of the Invention As described above, according to the present invention, the reduction molding rate of the ring member can be changed despite the simple structure in which the inner diameter of the ring member to which the actuating membrane body is joined is reduced and the actuating membrane body is flexibly deformed. This makes it possible to fine-tune the nonlinear region of the spring characteristics of the valve body, extending the low-level stable region of the dynamic spring constant of the vibration isolator to the high band, and also increasing the loss factor in the low band. It has a great effect.
第１図は本発明の一実施例を示す断面図、第２
図は同実施例の弁体を示す断面図、第３図は同実
施例の弁体の縮小成形例を示す概略図、第４図は
同実施例の加振周波数と動ばね定数との関係を示
す特性図、第５図は同実施例の加振周波数とロス
フアクタとの関係を示す特性図、第６，７図は本
発明の各異なる例を示す断面図、第８図は従来の
液体入り防振体を示す断面図、第９図は同従来の
弁体を示す断面図である。
１…支持部材、５…弾性体、６…隔壁、７…作
動液室、８，８Ａ…平衡液室、９，９Ａ，９Ｂ…
可撓膜、１１，１１Ａ…仕切部材、１２，１３…
オリフイス、１４，１４Ａ…バルブ機構、１５…
弁体収納室、１６，１６Ａ…弁体、１８，１８Ａ
…作動膜体、１９，１９Ａ…リング部材。
FIG. 1 is a cross-sectional view showing one embodiment of the present invention, and FIG.
The figure is a sectional view showing the valve body of the same example, Figure 3 is a schematic diagram showing an example of reduction molding of the valve body of the same example, and Figure 4 is the relationship between the excitation frequency and dynamic spring constant of the same example. FIG. 5 is a characteristic diagram showing the relationship between excitation frequency and loss factor of the same embodiment. FIGS. 6 and 7 are cross-sectional views showing different examples of the present invention. FIG. FIG. 9 is a cross-sectional view showing a built-in vibration isolator, and FIG. 9 is a cross-sectional view showing the conventional valve body. DESCRIPTION OF SYMBOLS 1... Support member, 5... Elastic body, 6... Partition wall, 7... Working liquid chamber, 8, 8A... Equilibrium liquid chamber, 9, 9A, 9B...
Flexible membrane, 11, 11A... partition member, 12, 13...
Orifice, 14, 14A...Valve mechanism, 15...
Valve body storage chamber, 16, 16A... Valve body, 18, 18A
... Working membrane body, 19, 19A... Ring member.
Claims (1)
室を形成し、この作動液室の外側に前記隔壁と可
撓膜を備えた仕切部材とで平衡液室を形成し、こ
の平衡液室を前記作動液室に連通するオリフイス
を前記隔壁に形成する一方、このオリフイスに作
動膜体とこの作動膜体の外周に接合したリング部
材とからなる弁体を遊嵌して、前記オリフイスを
前記弾性体に伝わる振動の大振幅振動で閉塞し、
小振幅振動で開放するようにした構成であつて、
前記弁体の作動膜体は接合されたリング部材の内
径を縮小成形することにより作動膜体がたわみ変
形させられたものであることを特徴とする液体入
り防振体のバルブ装置。1. A hydraulic fluid chamber is formed by the elastic body assembled to the support member and the partition, and an equilibrium liquid chamber is formed outside of this hydraulic fluid chamber by the partition and a partition member provided with a flexible membrane, and this equilibrium liquid is An orifice that communicates a chamber with the working fluid chamber is formed in the partition wall, and a valve body consisting of a working membrane body and a ring member joined to the outer periphery of the working membrane body is loosely fitted into the orifice. blockage due to large amplitude vibrations transmitted to the elastic body,
It has a configuration that opens with small amplitude vibration,
A valve device for a liquid-filled vibration isolator, characterized in that the actuating membrane body of the valve body is flexibly deformed by reducing the inner diameter of a joined ring member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24033584A JPS61119831A (en) | 1984-11-14 | 1984-11-14 | Valve mechanism of vibration preventer including liquid |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24033584A JPS61119831A (en) | 1984-11-14 | 1984-11-14 | Valve mechanism of vibration preventer including liquid |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61119831A JPS61119831A (en) | 1986-06-07 |
| JPH024816B2 true JPH024816B2 (en) | 1990-01-30 |
Family
ID=17057950
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24033584A Granted JPS61119831A (en) | 1984-11-14 | 1984-11-14 | Valve mechanism of vibration preventer including liquid |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61119831A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06127656A (en) * | 1992-10-21 | 1994-05-10 | House Foods Corp | Equipment for transferring bottle to sterile room |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2605694B1 (en) * | 1986-10-27 | 1989-06-16 | Hutchinson | IMPROVEMENTS IN HYDRAULIC ANTI-VIBRATION DEVICES |
| JPS63145036U (en) * | 1987-03-13 | 1988-09-26 | ||
| US5139240A (en) * | 1987-05-12 | 1992-08-18 | Honda Giken Kogyo Kabushiki Kaisha | Fluid-filled vibroisolating device |
| FR2672357A1 (en) * | 1991-02-01 | 1992-08-07 | Hutchinson | IMPROVEMENTS IN HYDRAULIC ANTI-VIBRATION DEVICES. |
| DE19650230B4 (en) * | 1996-12-04 | 2004-04-22 | Contitech Formteile Gmbh | Multi-chamber hydraulic mount |
| JP5064115B2 (en) * | 2007-05-28 | 2012-10-31 | 倉敷化工株式会社 | Liquid filled anti-vibration support device |
-
1984
- 1984-11-14 JP JP24033584A patent/JPS61119831A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06127656A (en) * | 1992-10-21 | 1994-05-10 | House Foods Corp | Equipment for transferring bottle to sterile room |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61119831A (en) | 1986-06-07 |
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