JPS63280943A - Fluid-sealed vibration isolator - Google Patents
Fluid-sealed vibration isolatorInfo
- Publication number
- JPS63280943A JPS63280943A JP11548987A JP11548987A JPS63280943A JP S63280943 A JPS63280943 A JP S63280943A JP 11548987 A JP11548987 A JP 11548987A JP 11548987 A JP11548987 A JP 11548987A JP S63280943 A JPS63280943 A JP S63280943A
- Authority
- JP
- Japan
- Prior art keywords
- fluid
- orifice
- partition
- movable partition
- partition member
- 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.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 74
- 238000005192 partition Methods 0.000 claims abstract description 67
- 239000013013 elastic material Substances 0.000 claims description 21
- 238000013016 damping Methods 0.000 claims description 18
- 239000000126 substance Substances 0.000 abstract 3
- 230000000694 effects Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 230000006866 deterioration Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000000052 comparative effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- 230000003068 static effect Effects 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
-
- 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
- F16F13/103—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 method of assembly, production or treatment
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Manufacturing & Machinery (AREA)
- Combined Devices Of Dampers And Springs (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
Abstract
Description
【発明の詳細な説明】
Ａ０発明の目的
（１）産業上の利用分野
本発明は、振動体に取付けられる取付部材とこの振動体
を支持するための支持体側に取付けられる支持部材とが
弾性材を介して相互に連結され、前記弾性材は、オリフ
ィスを備えた隔壁を介して互いに隣接し内部に非圧縮性
流体が封入された第１及び第２の流体室のうちの対応す
る側の流体室の室壁の少なくとも一部を構成している形
式の流体封入防振装置に関する。Detailed Description of the Invention A0 Object of the Invention (1) Industrial Application Field The present invention provides an embodiment of the present invention in which a mounting member attached to a vibrating body and a supporting member attached to a supporting body for supporting the vibrating body are made of an elastic material. and the elastic member is connected to the fluid on corresponding sides of the first and second fluid chambers, which are adjacent to each other via a partition wall having an orifice and have an incompressible fluid sealed inside. The present invention relates to a fluid-filled vibration isolator that forms at least a portion of a wall of a chamber.
（２）従来の技術
特開昭６０−２６３７３６号公報には、オリフィス内の
液体の共振を利用してマウントの動ばね定数とダンピン
グ性能の改善を図るようにした液体封入マウントが記載
されており、又これとは別に５０〜２００Ｈｚの領域及
び高周波領域における動ばね特性を改善するとともに大
振幅時のダンピング機能の向上を図るようにしたものが
特願昭６１−１８０９５３号として提案されている。(2) Conventional technology Japanese Patent Application Laid-Open No. 60-263736 describes a liquid-filled mount that utilizes the resonance of liquid within an orifice to improve the dynamic spring constant and damping performance of the mount. In addition to this, a device has been proposed in Japanese Patent Application No. 180953/1982 that improves the dynamic spring characteristics in the 50-200 Hz region and high frequency region, and also improves the damping function at large amplitudes.
（３）発明が解決しようとする問題点
流体封入防振装置については、従来より動ばね特性及び
ダンピング機能の向上のために種々提案されてきたが、
特に５０Ｈｚ以上の高周波領域における特性の改善がさ
らに望まれていた。(3) Problems to be solved by the invention Regarding fluid-filled vibration isolators, various proposals have been made to improve dynamic spring characteristics and damping functions.
In particular, it has been desired to further improve the characteristics in a high frequency region of 50 Hz or higher.
そこで、本発明は、５０１１ｚ以上の高周波領域での動
ばね特性を良好にした、簡単有効な流体封入防振装置を
提供することを目的とする。SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a simple and effective fluid-filled vibration damping device that has good dynamic spring characteristics in a high frequency range of 5011z or higher.
Ｂ０発明の構成
（１）問題点を解決するための手段
本発明によれば、振動体に取付けられる取付部材と前記
振動体を支持するための支持体側に取付けられる支持部
材とが弾性材を介して相互に連結され、前記弾性材は、
オリフィスを備えた隔壁を介して互いに隣接し内部に非
圧縮性流体が封入された第１及び第２の流体室のうちの
対応する側の流体室の室壁の少なくとも一部を構成して
いる形式の流体封入防振装置において、前記隔壁内には
前記オリフィスを横断し、流体圧の変動に応じて前記オ
リフィス内で遊動するようにして可動仕切部材が組み込
まれており、前記オリフィスは前記可動仕切部材の少な
くとも一方の側において、前記可動仕切部材に向けて末
広がり形状となっている、流体封入防振装置が得られる
。B0 Structure of the Invention (1) Means for Solving Problems According to the present invention, a mounting member attached to a vibrating body and a supporting member attached to a supporting body for supporting the vibrating body are connected via an elastic material. and the elastic members are interconnected with each other.
The first and second fluid chambers are adjacent to each other via a partition wall having an orifice, and each of the first and second fluid chambers has an incompressible fluid sealed therein, and constitutes at least a part of the chamber wall of the fluid chamber on the corresponding side. In this type of fluid-filled vibration isolator, a movable partition member is incorporated in the partition wall so as to traverse the orifice and move freely within the orifice in response to fluctuations in fluid pressure, and the orifice A fluid-filled vibration isolator is obtained, which has a shape that widens toward the movable partition member on at least one side of the partition member.
（２）作 用
取付部材と支持部材との間に介装された弾性材が、オリ
フィスを備えた隔壁を介して互いに隣接し内部に非圧縮
性流体が封入された第１及び第２の流体室のうちの対応
する側の流体室の室壁の少なくとも一部を構成している
ことにより、小振幅時には、可動仕切部材の遊動により
液体圧の変動を吸収するとともに、オリフィス内の流体
の質量と、弾性材の液圧に関するばね成分による共振作
用により、弾性材の共振を防止し、動ばね特性の悪化を
防止することができる。ここで可動仕切部材を保持する
隔壁の可動仕切部材と接触する部分が末広りとなってい
るため、接触面積が少なく、可動仕切部材の動きがスム
ーズであり、液体圧の変動の吸収と弾性材の共振の防止
とに効果的に寄与する。また大振幅時には、可動仕切部
材が遊動せず、液体圧を裔めることにより、制振効果を
生じさせる。(2) Function: An elastic material interposed between the mounting member and the support member is adjacent to each other via a partition wall provided with an orifice, and the first and second fluids, in which an incompressible fluid is sealed, are By forming at least a part of the chamber wall of the fluid chamber on the corresponding side of the chamber, when the amplitude is small, fluctuations in fluid pressure are absorbed by the free movement of the movable partition member, and the mass of the fluid in the orifice is In addition, due to the resonance effect of the spring component related to the hydraulic pressure of the elastic material, resonance of the elastic material can be prevented, and deterioration of the dynamic spring characteristics can be prevented. Here, the part of the partition wall that holds the movable partition member that comes in contact with the movable partition member is widened, so the contact area is small and the movement of the movable partition member is smooth, and the elastic material can absorb fluctuations in liquid pressure. This effectively contributes to prevention of resonance. Further, when the amplitude is large, the movable partition member does not move loosely and can absorb the liquid pressure, thereby producing a damping effect.
（３）実施例 以下、図面により本発明の詳細な説明する。(3) Examples Hereinafter, the present invention will be explained in detail with reference to the drawings.
まず第１図において、振動体に取付けられる取付部材１
．と、振動体を支持するための支持体側に取付けられる
環状の支持部材２１とは環状の補強材３により補強され
た環状の弾性材４１を介して相互に連結されている。支
持部材２１は筒状の胴部の一端縁側に取付フランジを有
し、前記弾性材４１はこの取付フランジ側の端縁部に沿
って固着されている。支持部材２３の胴部の他端縁側の
内周面に沿ってダイヤフラム５の外周縁部が接合されて
おり、弾性材４．と、支持部材２Ｉと、ダイヤフラム５
とにより、内部に非圧縮性流体が充満された流体室が形
成されている。この流体室内において、支持部材２３の
胴部の内周面に沿って隔壁６９の外周部が固着されてお
り、この隔壁６１により前記流体室は弾性材４．に接す
る第１の流体室７と、ダイヤフラム５に接する第２の流
体室８とに区分けされている。隔壁６Ｉは第１の流体室
７から第２の流体室８側へ向けて形成された多数のオリ
フィス９１を備えているとともに、隔壁６１内には各オ
リフィス９Ｉを横断し、流体圧の変動に応じて各オリフ
ィス内で遊動するようにして可動仕切部材１０＋が組込
まれている。そして、各オリフィス９５は第１の流体室
７側において可動仕切部材１０．に向けて末広がり形状
となった末広部１１を有している。First, in FIG. 1, a mounting member 1 attached to a vibrating body is shown.
．． and an annular support member 21 attached to the support body side for supporting the vibrating body are interconnected via an annular elastic member 41 reinforced by an annular reinforcing member 3. The support member 21 has a mounting flange on one end edge of the cylindrical body, and the elastic member 41 is fixed along the end edge on the mounting flange side. The outer peripheral edge of the diaphragm 5 is joined along the inner peripheral surface of the other end edge side of the body of the support member 23, and the elastic material 4. , the support member 2I, and the diaphragm 5
As a result, a fluid chamber filled with an incompressible fluid is formed. In this fluid chamber, the outer circumferential portion of a partition wall 69 is fixed along the inner circumferential surface of the body of the support member 23, and the partition wall 61 allows the fluid chamber to be closed by the elastic material 4. The first fluid chamber 7 is in contact with the diaphragm 5, and the second fluid chamber 8 is in contact with the diaphragm 5. The partition wall 6I is provided with a large number of orifices 91 formed from the first fluid chamber 7 toward the second fluid chamber 8 side, and the partition wall 61 has a plurality of orifices 91 that cross each of the orifices 9I to accommodate fluctuations in fluid pressure. A movable partition member 10+ is incorporated so as to move freely within each orifice accordingly. Each orifice 95 is connected to the movable partition member 10 on the first fluid chamber 7 side. It has a widening portion 11 that is widened toward the end.
上記オリフィス９５の有効長さし及び入口面積（小径部
所面積）Ｓｏは次式により設定される。The effective length and inlet area (area of the small diameter portion) So of the orifice 95 are set by the following equation.
Ｌ ４・ｋ
３、 ４・π！ ・ｆ、２ ・３％ 、ρ但
し、ｋ・・・弾性材４１の静ばね定数と、共振を問題と
する周波数における動倍率と
の積
Ｓｔ・・・取付部材１．及び支持部材２７間の単位相対
変位当りの、第１流体室７
の体積変化量
ｆｌ・・・弾性材４１の共振周波数
ρ・・・封入流体の密度
而して、上式に実測されるに、ｆ、、Ｓｔ、 ρを代入
すれば、適切なＳ、１とＬの関係を求めることができる
。こうしてＳ、１及びＬを最適値に設定することにより
、オリフィス９Ｉ内の流体の共振作用により、弾性材４
１の共振を抑制することができる。L 4・k 3, 4・π!・f, 2 ・3%, ρ However, k...Product of the static spring constant of the elastic material 41 and the dynamic magnification at the frequency where resonance is a problem St...Mounting member 1. and the volume change fl of the first fluid chamber 7 per unit relative displacement between the support member 27...the resonance frequency ρ of the elastic material 41...the density of the sealed fluid, which is actually measured using the above formula. By substituting ,f,,St,ρ, an appropriate relationship between,S,1,and,L,can be found. By setting S, 1, and L to optimal values in this way, the elastic material 4 is
1 resonance can be suppressed.
尚、弾性材４１の共振を抑えるためのオリフィス９１を
、これまで述べてきた寸法よりも、径を小さくかまたは
有効長さを長くして形成し、これによりオリフィス９１
内の流体の共振を僅かに低周波側へ移動させると、高周
波領域での動ばね定数は高（なるが２次振動領域（４０
〜２００１１ｚ）での動ばね定数は下がる（第１５図参
照）。また、これとは反対に、高周波側ヘシフトさせる
と、逆の現象が起こる（第１６図参照）。このような操
作は、特定の周波数での動ばね定数を重点的に下げたい
場合に利用される。Note that the orifice 91 for suppressing the resonance of the elastic material 41 is formed with a smaller diameter or a longer effective length than the dimensions described above, so that the orifice 91
If the resonance of the fluid in the inner part is slightly shifted to the lower frequency side, the dynamic spring constant in the high frequency region will be high (but it will be in the secondary vibration region (40
~20011z), the dynamic spring constant decreases (see Figure 15). On the other hand, when shifting to the high frequency side, the opposite phenomenon occurs (see FIG. 16). Such an operation is used when it is desired to intensively lower the dynamic spring constant at a specific frequency.
ところで、第１図の流体封入防振装置においては、各オ
リフィス９１は第１の流体室７側におきて可動仕切部材
１０＋に向けて末広がり形状となっているため、可動仕
切部材ＩＯ１の受圧面積が大きく、且つ可動仕切部材と
、それを保持する隔壁６９との間の接触面積が小さいた
め、小振幅の中・高周波振動が加わった場合に、可動仕
切部材ＩＯ３の遊動がスムーズに行われ、動ばね特性の
悪化を防止し得る。By the way, in the fluid-filled vibration isolator of FIG. 1, each orifice 91 is located on the first fluid chamber 7 side and has a shape that widens toward the movable partition member 10+, so that the pressure receiving area of the movable partition member IO1 is is large, and the contact area between the movable partition member and the partition wall 69 that holds it is small, so that when small-amplitude medium and high frequency vibrations are applied, the movable partition member IO3 moves smoothly, Deterioration of dynamic spring characteristics can be prevented.
第１７図に、反共振オリフィスを１つのオリフィス９゜
で構成した例を示す。こうしたものでは、加振時、可動
仕切部材１０ｏとオリフィス９゜との間の流体が矢印で
示すように複雑な動きをするため、流体の移動に対し僅
かであるがダンピング現象が生じる。このため、２次振
動領域での動ばね特性の悪化が起こる。したがって良好
な動ばね特性を得るには、反共振オリフィスは多数のオ
リフィスの集合体から構成することがよい。FIG. 17 shows an example in which the anti-resonance orifice is composed of one 9° orifice. In such a device, when the vibration is applied, the fluid between the movable partition member 10o and the orifice 9° moves in a complicated manner as shown by the arrow, so a damping phenomenon occurs, albeit slightly, with respect to the movement of the fluid. Therefore, the dynamic spring characteristics deteriorate in the secondary vibration region. Therefore, in order to obtain good dynamic spring characteristics, it is preferable that the anti-resonance orifice be constituted by an aggregate of a large number of orifices.
第２図は第１図の流体封入防振装置の変形例であって、
隔壁６□の各オリフィス９□は、可動仕切部材の両側に
おいて、それぞれ可動仕切部材に向けて末広部１２１．
１２□を有している。FIG. 2 shows a modification of the fluid-filled vibration isolator shown in FIG.
Each orifice 9□ of the partition wall 6□ has a divergent portion 121. on each side of the movable partition member toward the movable partition member.
It has 12□.
第３図の流体封入防振装置においては、隔壁の中央部に
、例えば２０Ｈ２以下の低周波におけるダンピング特性
を改善するための低周波用オリフィス１３を有している
。The fluid-filled vibration damping device shown in FIG. 3 has a low frequency orifice 13 in the center of the partition wall for improving damping characteristics at low frequencies of, for example, 20H2 or less.
第４図の流体封入防振装置においては、隔壁６、の中央
部に、弾性材側のオリフィスの末広部からダイヤフラム
側の流体室へと貫ける低周波用オリフィス１４を有して
いる。このため、大振幅の低周波入力に対し高いダンピ
ング特性を有する。The fluid-filled vibration damping device shown in FIG. 4 has a low-frequency orifice 14 in the center of the partition wall 6 that can penetrate from the widening part of the orifice on the elastic material side to the fluid chamber on the diaphragm side. Therefore, it has high damping characteristics against large amplitude low frequency input.
第５図の流体封入防振装置においては、多数のオリフィ
スのうち選択されたオリフィス内において、可動仕切部
材１０！に低周波用オリフィス１５が形成されている。In the fluid-filled vibration isolator shown in FIG. 5, the movable partition member 10! A low frequency orifice 15 is formed in the.
この場合においても、大振幅の低周波入力に対し高いダ
ンピング特性を有する。In this case as well, it has high damping characteristics for large amplitude low frequency inputs.
第６図には、第２図と同様な構造を有する流体封入防振
装置において、隔壁６４の中央部に低周波用オリフィス
１６が形成されている流体封入防振装置が示されている
。この場合においても、大振幅の低周波入力に対し高い
ダンピング特性を有する。FIG. 6 shows a fluid-filled vibration isolator having a structure similar to that of FIG. 2, in which a low-frequency orifice 16 is formed in the center of a partition wall 64. In this case as well, it has high damping characteristics for large amplitude low frequency inputs.
第７図の流体封入防振装置においては、隔壁６、の外周
寄りのオリフィス９５の弾性材側の末広部に開口部１７
を有し、隔壁６９の外周部内を経由してダイヤフラム５
例の流体室内の開口部１９まで延設された低周波用オリ
フィス１８を有する。In the fluid-filled vibration isolator shown in FIG.
, and the diaphragm 5 passes through the outer circumference of the partition wall 69
It has a low frequency orifice 18 extending to an opening 19 in the fluid chamber of the example.
この場合には、低周波域において非常に高いダンピング
特性を有する。In this case, it has extremely high damping characteristics in the low frequency range.
第８図の流体封入防振装置においては、隔壁６、の外周
部において、弾性材４．側に開口部２１を有し、隔壁６
９の外周部内を経由してダイヤフラム５側の開口部２２
まで延在する低周波用オリフィス２０を有する。この場
合にも、低周波域において非常に高いダンピング特性を
有する。In the fluid-filled vibration isolator shown in FIG. 8, the elastic material 4. It has an opening 21 on the side, and the partition wall 6
9 through the opening 22 on the diaphragm 5 side.
It has a low frequency orifice 20 that extends up to In this case as well, it has very high damping characteristics in the low frequency range.
第９図の流体封入防振装置においては、可撓性の可動仕
切部材２３が緩みを持った状態で隔壁６、により保持さ
れているとともに、隔壁６６の中央部には低周波用オリ
フィス２４が形成されている。In the fluid filled vibration isolator shown in FIG. 9, a flexible movable partition member 23 is held in a loose state by a partition wall 6, and a low frequency orifice 24 is provided in the center of the partition wall 66. It is formed.
第１０図の流体封入防振装置においては、隔壁６、の中
央部に一対の低周波用オリフィス２５゜２６が形成され
、各低周波用オリフィス２５．２６には、それぞれ互い
に逆向きの逆止弁２７，２８が配設されている。各逆止
弁２７，２Ｂの剛性を適度に調整することにより、広い
周波域における良好なダンピング特性を得ることができ
る。In the fluid filled vibration isolator shown in FIG. 10, a pair of low frequency orifices 25 and 26 are formed in the center of the partition wall 6, and each of the low frequency orifices 25 and 26 has a non-return check that is oriented in opposite directions. Valves 27, 28 are provided. By appropriately adjusting the rigidity of each check valve 27, 2B, good damping characteristics in a wide frequency range can be obtained.
第１１図の流体封入防振装置においては、隔壁６６に低
周波用オリフィス２９が形成されており、この低周波用
オリフィス２９に対し出没可能な制御弁３０が配設され
ている。動的な大荷重入力が加わった際、制御弁３０を
操作することにより適切なダンピング特性を得ることが
できる。In the fluid-filled vibration isolator shown in FIG. 11, a low frequency orifice 29 is formed in the partition wall 66, and a control valve 30 that can move in and out of the low frequency orifice 29 is provided. When a dynamic large load input is applied, appropriate damping characteristics can be obtained by operating the control valve 30.
第１２図の流体封入防振装置においては、互いに対向す
る取付部材１□、１３が相互に連結部材３１により連結
され、各取付部材１＝、１３はそれぞれ弾性材４２３４
３を介して支持部材２□に連結されている。そして隔壁
６ｑの中央部には低周波用オリフィス３２が形成されて
いる。このような構造とすることにより、大荷重の引張
り人力が加わっても、一方の流体室の流体圧が正となる
ため、流体室内のキャビテーションが防止され、大荷重
に対する良好なタンピング特性が得られる。In the fluid-filled vibration isolator shown in FIG. 12, mounting members 1□, 13 facing each other are connected to each other by a connecting member 31, and each mounting member 1=, 13 is made of an elastic material 4234.
3 to the support member 2□. A low frequency orifice 32 is formed in the center of the partition wall 6q. With this structure, even when a large pulling force is applied, the fluid pressure in one fluid chamber remains positive, preventing cavitation in the fluid chamber and providing good tamping characteristics against large loads. .
第１３図の流体封入防振装置においては、一対の取付部
材１４．１ｓが隔壁３３を挾んで相互に連結され、各取
付部材１．，１１、隔壁３３と支持部材２３との間には
、それぞれ環状の弾性材４＝、４５．４６が介装されて
いる。隔壁３３に形成された複数個のオリフィス９５．
９５内には、各オリフィス９５．９５を横断するように
して、それぞれ低周波用オリフィス３６９３７を有する
可動仕切部材３４．３５が遊嵌されており、各オリフィ
ス９＝、９ｓには、弾性材４４の側から各可動仕切部材
３４．３５に向けて末広がりとなっている末広部３８．
３９が形成されている。In the fluid-filled vibration isolator shown in FIG. 13, a pair of mounting members 14.1s are connected to each other with a partition wall 33 in between, and each mounting member 1. , 11, annular elastic members 4=, 45, 46 are interposed between the partition wall 33 and the support member 23, respectively. A plurality of orifices 95 formed in the partition wall 33.
95, movable partition members 34.35 each having a low frequency orifice 36937 are loosely fitted so as to cross each orifice 95.95, and each orifice 9=, 9s is provided with an elastic material 44. The widening portion 38. widens toward each movable partition member 34.35 from the side of the movable partition member 34.35.
39 is formed.
第１４図には、第１３図の流体封入防振装置の弾性材４
４に代えてダイヤフラム４０を適用した場合の流体封入
防振装置が示されている。FIG. 14 shows the elastic material 4 of the fluid-filled vibration isolator shown in FIG. 13.
A fluid-filled vibration damping device is shown in which a diaphragm 40 is used instead of the diaphragm 40.
Ｃ１発明の効果
以上のように本発明によれば、取付部材と支持部材との
間に介装された弾性材が、オリフィスを備えた隔壁を介
して互いに隣接し内部に非圧縮性流体が封入された第１
及び第２の流体室のうちの対応する側の流体室の室壁の
少なくとも一部を構成しているので、オリフィスの有効
長さ及び入口面積を適当に設定することにより、オリフ
ィス内の流体の共振作用により弾性材の共振を抑制する
ことができる。また、オリフィスの前記末広がり形状に
より、可動仕切部材の遊動がスムーズであり、閏周波小
振幅時の動ばね定数を低下させることができる。しかも
、可動仕切部材を設けると共にオリフィスの形状を工夫
しただけであるから、装置は、構造が簡単、且つコンパ
クトである。C1 Effects of the Invention As described above, according to the present invention, the elastic material interposed between the mounting member and the support member is adjacent to each other via the partition wall provided with the orifice, and the incompressible fluid is sealed inside. The first
and at least a part of the chamber wall of the fluid chamber on the corresponding side of the second fluid chamber. Resonance of the elastic material can be suppressed by the resonance effect. Further, due to the shape of the orifice expanding toward the end, the movable partition member can smoothly move, and the dynamic spring constant at the time of a small leap frequency amplitude can be reduced. Moreover, since only the movable partition member is provided and the shape of the orifice is modified, the device has a simple and compact structure.
第１図は本発明の一実施例に基づく流体封入防振装置の
縦断面図、第２図ないし第１４図はそれぞれ本発明の別
の実施例に基づく流体封入防振装置の縦断面図、第１５
図は第１図の実施例において、オリフィスの径をより小
さくし、または有効長さをより長くした場合の動ばね特
性線図、第１６図は第１図の実施例において、オリフィ
スの径をより大きくし、または有効長さをより短くした
場合の動ばね特性線図、第１７図は第１図の実施例に対
する比較例の縦断面図である。
１、〜ＩＳ・・・取付部材、２３〜２３・・・支持部材
、４、〜４６・・・弾性材、６１〜６９・・・隔壁、７
，８・・・流体室、９５〜９５・・・オリフィス、１０
．．１０２、２３，３４．３５・・・可動仕切部材時
許 出 願 人 本田技研工業株式会社代理人 弁
理士 落 合 健第１５図
第１６図
周波数（Ｈｚ）FIG. 1 is a longitudinal cross-sectional view of a fluid-filled vibration isolator according to an embodiment of the present invention, and FIGS. 2 to 14 are longitudinal cross-sectional views of a fluid-filled vibration isolator according to another embodiment of the present invention, respectively. 15th
The figure shows a dynamic spring characteristic diagram when the diameter of the orifice is made smaller or the effective length is made longer in the embodiment shown in Fig. 1. FIG. 17 is a longitudinal sectional view of a comparative example to the embodiment shown in FIG. 1, ~IS... Mounting member, 23-23... Supporting member, 4, ~46... Elastic material, 61-69... Partition wall, 7
, 8... Fluid chamber, 95-95... Orifice, 10
．． ．． 102, 23, 34.35...When movable partition member
Applicant: Honda Motor Co., Ltd. Agent Patent Attorney Ken Ochiai Figure 15 Figure 16 Frequency (Hz)
Claims (3)
）と前記振動体を支持するための支持体側に取付けられ
る支持部材（２＿１〜２＿３）とが弾性材（４＿１〜４
＿６）を介して相互に連結され、前記弾性材（４＿１〜
４＿６）は、オリフィス（９＿１〜９＿５）を備えた隔
壁（６＿１〜６＿９）を介して互いに隣接し内部に非圧
縮性流体が封入された第１及び第２の流体室（７、８）
のうちの対応する側の流体室（７）の室壁の少なくとも
一部を構成している形式の流体封入防振装置において、
前記隔壁（６＿１〜６＿９）内には前記オリフィス（９
＿１〜９＿５）を横断し、流体圧の変動に応じて前記オ
リフィス（９＿１〜９＿５）内で遊動するようにして可
動仕切部材（１０＿１、１０＿２、２３、３４、３５）
が組み込まれており、前記オリフィス（９＿１〜９＿５
）は前記可動仕切部材（１０＿１、１０＿２、２３、３
４、３５）の少なくとも一方の側において、前記可動仕
切部材（１０＿１、１０＿２、２３、３４、３５）に向
けて末広がり形状となっている、流体封入防振装置。(1) Mounting members attached to the vibrating body (1_1 to 1_5
) and support members (2_1 to 2_3) attached to the support body side for supporting the vibrating body are made of elastic materials (4_1 to 4).
The elastic members (4_1 to 4_6) are connected to each other via
4_6) are first and second fluid chambers (7, 8) which are adjacent to each other via partition walls (6_1 to 6_9) having orifices (9_1 to 9_5) and in which an incompressible fluid is sealed.
In a fluid-filled vibration isolator of a type that constitutes at least a part of the chamber wall of the fluid chamber (7) on the corresponding side of the fluid chamber (7),
The orifice (9) is provided in the partition wall (6_1 to 6_9).
movable partition members (10_1, 10_2, 23, 34, 35) that traverse the orifices (9_1 to 9_5) and move freely within the orifices (9_1 to 9_5) according to changes in fluid pressure;
is incorporated, and the orifice (9_1 to 9_5
) is the movable partition member (10_1, 10_2, 23, 3
4, 35), the fluid-filled vibration isolator has a shape that widens toward the movable partition member (10_1, 10_2, 23, 34, 35).
０＿１、１０＿２、２３、３４、３５）が横断していな
い低周波用オリフィス（１３、１４、１６、１８、２０
、２４〜２６、２９、３２）が前記可動仕切部材（１０
＿１、１０＿２、２３、３４、３５）と並列に形成され
ている、特許請求の範囲第（１）項記載の流体封入防振
装置。(2) The movable partition member (1
Low frequency orifices (13, 14, 16, 18, 20) that are not crossed by
, 24 to 26, 29, 32) are the movable partition members (10
_1, 10_2, 23, 34, 35), the fluid-filled vibration isolating device according to claim (1).
一つのオリフィス内において、前記可動仕切部材（１０
＿１、１０＿２、２３、３４、３５）に低周波用オリフ
ィス（１５、３６、３７）が形成されている特許請求の
範囲第１項記載の流体封入防振装置。(3) In at least one of the orifices (9_1 to 9_5), the movable partition member (10
2. The fluid-filled vibration damping device according to claim 1, wherein low frequency orifices (15, 36, 37) are formed in the portions (_1, 10_2, 23, 34, 35).
Priority Applications (8)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62115489A JPH0788869B2 (en) | 1987-05-12 | 1987-05-12 | Fluid filled vibration isolation device |
| US07/192,443 US4903951A (en) | 1987-05-12 | 1988-05-11 | Fluid-filled vibroisolating device |
| GB8811292A GB2206176B (en) | 1987-05-12 | 1988-05-12 | Fluid-filled vibroisolating device |
| DE3816445A DE3816445A1 (en) | 1987-05-12 | 1988-05-13 | FLUID FILLED, VIBRATION DETECTING DEVICE |
| FR8806471A FR2615260B1 (en) | 1987-05-12 | 1988-05-13 | DEVICE, FILLED WITH FLUID, VIBRATION INSULATING |
| DE3844810A DE3844810C2 (en) | 1987-05-12 | 1988-05-13 | Engine vibration equaliser for IC engine |
| US07/624,459 US5139240A (en) | 1987-05-12 | 1990-12-10 | Fluid-filled vibroisolating device |
| GB9109245A GB2242724B (en) | 1987-05-12 | 1991-04-30 | Fluid filled vibroisolating device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62115489A JPH0788869B2 (en) | 1987-05-12 | 1987-05-12 | Fluid filled vibration isolation device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63280943A true JPS63280943A (en) | 1988-11-17 |
| JPH0788869B2 JPH0788869B2 (en) | 1995-09-27 |
Family
ID=14663784
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62115489A Expired - Lifetime JPH0788869B2 (en) | 1987-05-12 | 1987-05-12 | Fluid filled vibration isolation device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0788869B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4938463A (en) * | 1988-06-06 | 1990-07-03 | Honda Giken Kogyo Kabushiki Kaisha | Fluid-filled vibration damper |
| US5148897A (en) * | 1991-07-18 | 1992-09-22 | Monroe Auto Equipment Company | Piston valving for shock absorbers |
| WO2009022515A1 (en) * | 2007-08-13 | 2009-02-19 | Bridgestone Corporation | Vibration isolation device |
| JP2012107639A (en) * | 2010-11-15 | 2012-06-07 | Toyo Tire & Rubber Co Ltd | Liquid-sealed vibration control device |
| JPWO2016027606A1 (en) * | 2014-08-20 | 2017-05-18 | 株式会社ブリヂストン | Vibration isolator |
| WO2019131043A1 (en) * | 2017-12-26 | 2019-07-04 | 株式会社ブリヂストン | Vibration isolating device |
| CN111433488A (en) * | 2017-12-11 | 2020-07-17 | 株式会社普利司通 | Vibration isolation device |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6986488B2 (en) * | 2018-05-22 | 2021-12-22 | 株式会社ブリヂストン | Anti-vibration device |
| JP6986490B2 (en) * | 2018-05-22 | 2021-12-22 | 株式会社ブリヂストン | Anti-vibration device |
| JP6986489B2 (en) * | 2018-05-22 | 2021-12-22 | 株式会社ブリヂストン | Anti-vibration device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6040841A (en) * | 1983-08-15 | 1985-03-04 | Bridgestone Corp | Vibration-proof device |
| JPS612941A (en) * | 1984-06-07 | 1986-01-08 | アウデイ アクチエンゲゼルシヤフト | Vibration-proof device |
-
1987
- 1987-05-12 JP JP62115489A patent/JPH0788869B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6040841A (en) * | 1983-08-15 | 1985-03-04 | Bridgestone Corp | Vibration-proof device |
| JPS612941A (en) * | 1984-06-07 | 1986-01-08 | アウデイ アクチエンゲゼルシヤフト | Vibration-proof device |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4938463A (en) * | 1988-06-06 | 1990-07-03 | Honda Giken Kogyo Kabushiki Kaisha | Fluid-filled vibration damper |
| US5148897A (en) * | 1991-07-18 | 1992-09-22 | Monroe Auto Equipment Company | Piston valving for shock absorbers |
| WO2009022515A1 (en) * | 2007-08-13 | 2009-02-19 | Bridgestone Corporation | Vibration isolation device |
| JP2009041761A (en) * | 2007-08-13 | 2009-02-26 | Bridgestone Corp | Antivibration device |
| US8196700B2 (en) | 2007-08-13 | 2012-06-12 | Bridgestone Corporation | Anti-vibration device |
| JP2012107639A (en) * | 2010-11-15 | 2012-06-07 | Toyo Tire & Rubber Co Ltd | Liquid-sealed vibration control device |
| JPWO2016027606A1 (en) * | 2014-08-20 | 2017-05-18 | 株式会社ブリヂストン | Vibration isolator |
| CN111433488A (en) * | 2017-12-11 | 2020-07-17 | 株式会社普利司通 | Vibration isolation device |
| WO2019131043A1 (en) * | 2017-12-26 | 2019-07-04 | 株式会社ブリヂストン | Vibration isolating device |
| JP2019116905A (en) * | 2017-12-26 | 2019-07-18 | 株式会社ブリヂストン | Vibration isolation device |
| CN111527326A (en) * | 2017-12-26 | 2020-08-11 | 株式会社普利司通 | Vibration isolation device |
| US11428290B2 (en) | 2017-12-26 | 2022-08-30 | Prospira Corporation | Vibration isolating device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0788869B2 (en) | 1995-09-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH033088B2 (en) | ||
| JPS62224746A (en) | Fluid seal type vibrationproof supporting body | |
| JP2776463B2 (en) | Anti-vibration device | |
| JPS63280943A (en) | Fluid-sealed vibration isolator | |
| US3101937A (en) | Combination spring-piston vibration isolator | |
| EP0178652B1 (en) | Liquid-filled type vibration damping structure | |
| US4802658A (en) | Vibration isolating apparatus | |
| JPH05209646A (en) | Multi-compartment liquid pressure bushing | |
| JPH0534535B2 (en) | ||
| JPH01238730A (en) | Fluid seal type mount device | |
| JPH01153833A (en) | Sleeve type rubber shock absorber | |
| JPH01193426A (en) | Liquid-in type mounting device | |
| JPS60155029A (en) | Vibration isolating device containing fluid | |
| JPH05584Y2 (en) | ||
| JPH01229132A (en) | Fluid sealed type mount device | |
| JP2760938B2 (en) | Bushing type bearing device | |
| JPH01164831A (en) | Fluid-filled type cylinder type mount | |
| JP3764534B2 (en) | Liquid filled vibration isolator | |
| JP2848399B2 (en) | Inner / outer cylinder type fluid-filled vibration isolator | |
| JPH11141595A (en) | Vibration control device | |
| JP4365004B2 (en) | Vibration isolator | |
| JP2002122175A (en) | Liquid filled mount | |
| JPH0599274A (en) | Amplitude-sensitive vibration-proof rubber device | |
| JP3721828B2 (en) | Fluid filled vibration isolator | |
| JPH11278294A (en) | Shimmy reduction device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term | ||
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20070927 Year of fee payment: 12 |