JPS61116132A - vibration isolator - Google Patents
vibration isolatorInfo
- Publication number
- JPS61116132A JPS61116132A JP23498384A JP23498384A JPS61116132A JP S61116132 A JPS61116132 A JP S61116132A JP 23498384 A JP23498384 A JP 23498384A JP 23498384 A JP23498384 A JP 23498384A JP S61116132 A JPS61116132 A JP S61116132A
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- leak
- piston
- pistons
- piston rod
- 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
- 239000012530 fluid Substances 0.000 abstract description 4
- 238000013016 damping Methods 0.000 description 10
- 230000000694 effects Effects 0.000 description 4
- 230000006866 deterioration Effects 0.000 description 3
- 238000007789 sealing Methods 0.000 description 2
- 230000015556 catabolic process Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 239000003292 glue Substances 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 239000003566 sealing material Substances 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/22—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with one or more cylinders each having a single working space closed by a piston or plunger
- F16F9/26—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with one or more cylinders each having a single working space closed by a piston or plunger with two cylinders in line and with the two pistons or plungers connected together
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、流体式防振器に係り、特に原子力施設のよう
な重要な機器、配管設備に対して、性能のよい防振器を
用いる必要があるものに関する。[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a fluid-type vibration isolator, and in particular, it is necessary to use a high-performance vibration isolator for important equipment and piping equipment such as nuclear facilities. Concerning something that is.
従来の流体式防振器は、第１図にその代表的構成を示す
通りのもので、１つのシリンダーに１つのピストンを用
いている。すなわち、シリンダー１内にピストン２が挿
入されており、作動流体としての油３が封入されている
。ピストン２は、ピストンロッド４に結合されており、
ピストンロッド４は、シリンダーの片側端を貫通して外
部に取り出されている。当該貫通部には、油３のリーク
９を防止するため、０リングなどのシール５が取付けら
れている。防振作用は、シリンダー１とピストンロッド
４の間で発生する６作動原理を簡単に示すと、今、図の
矢印×で示す方向に急速にピストンロッド４が変位する
とすると、シリンダーＡ側の油３が圧縮されて、油はＡ
側のバイブロを通じて流れようとするが、制御弁機構７
の作用により、急速には流れず、高い圧力を生じる。そ
のため、シリンダーのＡ側の圧力とピストンの受圧面積
の積に相当する反力が生じ、防振力となる。A conventional hydraulic vibration isolator has a typical configuration shown in FIG. 1, and uses one piston for one cylinder. That is, a piston 2 is inserted into a cylinder 1, and oil 3 as a working fluid is sealed therein. The piston 2 is coupled to a piston rod 4,
The piston rod 4 passes through one end of the cylinder and is taken out to the outside. A seal 5 such as an O-ring is attached to the penetrating portion to prevent leakage 9 of the oil 3. The vibration damping effect occurs between the cylinder 1 and the piston rod 4.6 To briefly explain the operating principle, if the piston rod 4 is rapidly displaced in the direction indicated by the arrow x in the figure, the oil on the cylinder A side 3 is compressed and the oil becomes A
It tries to flow through the side vibro, but the control valve mechanism 7
Due to the action of , it does not flow quickly and generates high pressure. Therefore, a reaction force corresponding to the product of the pressure on the A side of the cylinder and the pressure receiving area of the piston is generated, which becomes a vibration damping force.
逆の場合は、シリンダーＢ側の圧力が増加し、Ｂ側に防
振力が生じる。この繰返しで、防振的な入力に対して防
振作用を生じる。In the opposite case, the pressure on the cylinder B side increases and a vibration damping force is generated on the B side. This repetition produces a vibration damping effect against vibration damping inputs.
以上の作動原理からみると、第１図の構成の流体防振器
には、
■ Ｂ側ピストンの受圧面積は、ピストンロッドの占め
る分だけＡ側より小さくなるため、防振力に差を生じる
。Based on the above operating principle, the fluid vibration isolator with the configuration shown in Figure 1 has the following: ■ The pressure receiving area of the B side piston is smaller than that of the A side by the amount occupied by the piston rod, which causes a difference in vibration isolating force. .
■ Ｂ側は、ピストンロッドがシリンダ一端部を貫通す
るので、シール機構を設けているが、高圧力発生時に、
シール部よりのり−ク９の存在する分だけ、高圧力保持
能力が低下する。■ On the B side, the piston rod passes through one end of the cylinder, so a sealing mechanism is provided, but when high pressure is generated,
The high pressure holding ability is reduced by the amount of glue 9 present in the seal portion.
■ シール材は、ピストンロッドの摺動繰返しとともに
消耗劣化するため、リーク９は、経年的に増加し、それ
に伴って性能アンバランスも増加する。(2) Since the sealing material wears out and deteriorates with repeated sliding of the piston rod, leakage 9 increases over time, and performance imbalance also increases accordingly.
などの問題があった。There were other problems.
本発明の目的は、従来技術の有する問題点を解決し、性
能のバランスを計り、かつ経年変化を極力抑制した、信
頼性の高い流体式防振器を提供するにある。An object of the present invention is to provide a highly reliable hydraulic vibration isolator that solves the problems of the prior art, balances performance, and suppresses deterioration over time as much as possible.
従来の防振器が、１組のピストンとシリンダーしか用い
ず、ピストンの両側に防振力を期待するため、ピストン
の一方側の受圧面積がピストンロッドの占める分だけ少
なくなり、防振力のアンバランスを生じた。また、同様
の理由により、ピストンロッドが、シリンダ一端部を貫
通するため、シールが必要であるが、その側にも防振力
を期待しているため、シール部の性能劣化に基づく性能
低下を招来すると同時に、経年的にも変化するものとな
った。そこで、本発明は、２組のピストンとシリンダー
を用い、ピストンロッドの結合される側のピストン受圧
面には、防振力の発生を期待しなくてもよい構造とした
ものである。また、シール部も高圧力は発生しないため
、シール部からの油のリークも従来の方式に比べ非常に
少なくなり、かつシール材も高圧力用のものを用いる必
要がなくなった。それ故にシール性の劣化が直接防振性
能に影響しなくなった。Conventional vibration isolators use only one set of piston and cylinder and expect vibration isolating force on both sides of the piston, so the pressure receiving area on one side of the piston is reduced by the amount occupied by the piston rod, and the vibration isolating force is reduced. This created an imbalance. Also, for the same reason, since the piston rod passes through one end of the cylinder, a seal is required, but since that side is also expected to have vibration-proofing power, performance degradation due to performance deterioration of the seal part is avoided. At the same time as it was introduced, it also changed over time. Therefore, the present invention uses two sets of pistons and cylinders, and has a structure in which it is not necessary to expect the generation of vibration damping force on the piston pressure receiving surface on the side to which the piston rod is connected. In addition, since high pressure is not generated in the seal portion, oil leakage from the seal portion is significantly reduced compared to conventional systems, and there is no need to use a seal material designed for high pressure. Therefore, the deterioration of sealing performance no longer directly affects vibration isolation performance.
以上のようにして、従来技術のもつ問題点を解決し、技
術的に優れた流体式防振器を得ると云う効果が得られた
。In the manner described above, the problems of the prior art have been solved and a technically superior hydraulic vibration isolator has been obtained.
第２図は、本発明の実施例を示す１本実施例は、シリン
ダー１に２対のピストン２が取付けられているものであ
り、それらは、ピストンロッド４により相互に連結され
ている。各ピストン２からの作動流体としての油３のリ
ーク９は、シール５により、シリンダー外へリークする
のを防止され、戻りパイプ１ｏを通じて制御弁機構７の
オイルタンク８側のＲ点へ導かれている。FIG. 2 shows an embodiment of the present invention. In this embodiment, two pairs of pistons 2 are attached to a cylinder 1, and they are interconnected by a piston rod 4. As shown in FIG. Leakage 9 of the oil 3 as the working fluid from each piston 2 is prevented from leaking out of the cylinder by the seal 5, and is guided to point R on the oil tank 8 side of the control valve mechanism 7 through the return pipe 1o. There is.
防振力の発生の原理は、第１図に示した従来の防振器と
本質的な差はない、すなわち、ピストンロッド４に取付
けられた支持部材１１とシリンダー１との間で防振力が
発生する。今、ピストンが矢印×の方向に急速に変位す
ると、シリンダーのＡ側に高圧力が発生し、防振力が生
じる。逆の場合は、シリンダーのＤ側の圧力が高くなり
防振力が発生する。従って、いずれの場合においても、
リーク９の生じるシリンダーのＤ側及びＣ側は、制御弁
機構７の吸込み側のＲ点に結合されており、高圧力の発
生はない、シリンダーＡ側とＤ側は、ピストンロッドの
貫通もなく、受圧面積も等しく防振力発生の面から差が
なくなる。The principle of generation of vibration isolating force is essentially the same as that of the conventional vibration isolator shown in FIG. occurs. Now, when the piston rapidly displaces in the direction of arrow x, high pressure is generated on the A side of the cylinder, and a vibration damping force is generated. In the opposite case, the pressure on the D side of the cylinder increases and vibration damping force is generated. Therefore, in any case,
The D and C sides of the cylinder where the leak 9 occurs are connected to the R point on the suction side of the control valve mechanism 7, and no high pressure is generated.The cylinder A and D sides have no piston rod penetration. , the pressure-receiving area is also the same, so there is no difference in terms of vibration-proofing force generation.
本発明によれば、２対のピストンとシリンダーを用いる
ものは、防振力にアンバランスがなく、かつ、ピストン
ロッドの貫通する側に防振力を期待しないので、シール
部のリークによる性能のアンバランスと経年的変化を生
じないと云う効果がある。According to the present invention, since there is no unbalance in vibration damping force and no vibration damping force is expected on the side through which the piston rod passes, the performance of the system using two pairs of pistons and cylinders is reduced due to leakage from the seal part. It has the effect of not causing imbalance or changes over time.
第ζ図は、従来技術による防振器の断面図、第２図は、
本発明の一実施例の断面図である。
１・・・シリンダー、２・・・ピストン、３・・・油、
４・・・ピストンロッド、５・・・Ｏリングシール、６
・・・パイプ。
７・・・制御弁機構、８・・・オイルタンク、９・・・
リーク、１０・・・戻りパイプ、１１・・・支持部材。Figure ζ is a sectional view of a vibration isolator according to the prior art, and Figure 2 is a
FIG. 1 is a cross-sectional view of an embodiment of the present invention. 1...Cylinder, 2...Piston, 3...Oil,
4... Piston rod, 5... O-ring seal, 6
···pipe. 7... Control valve mechanism, 8... Oil tank, 9...
Leak, 10... Return pipe, 11... Support member.
Claims (1)
ーを備えたことを特徴とする防振器。1. A hydraulic vibration isolator characterized by comprising two pairs of pistons and cylinders.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23498384A JPS61116132A (en) | 1984-11-09 | 1984-11-09 | vibration isolator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23498384A JPS61116132A (en) | 1984-11-09 | 1984-11-09 | vibration isolator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS61116132A true JPS61116132A (en) | 1986-06-03 |
Family
ID=16979303
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23498384A Pending JPS61116132A (en) | 1984-11-09 | 1984-11-09 | vibration isolator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61116132A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2218835A1 (en) * | 2009-02-12 | 2010-08-18 | Luc Didden | Shovel loader comprising two hinged frames. |
| BE1018654A3 (en) * | 2009-02-12 | 2011-06-07 | Didden Luc | LOADER. |
| JP5161395B1 (en) * | 2012-11-14 | 2013-03-13 | 株式会社免制震ディバイス | Vibration suppression device |
| JP2014163496A (en) * | 2013-02-27 | 2014-09-08 | Takenaka Komuten Co Ltd | Fluid damper |
-
1984
- 1984-11-09 JP JP23498384A patent/JPS61116132A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2218835A1 (en) * | 2009-02-12 | 2010-08-18 | Luc Didden | Shovel loader comprising two hinged frames. |
| BE1018654A3 (en) * | 2009-02-12 | 2011-06-07 | Didden Luc | LOADER. |
| JP5161395B1 (en) * | 2012-11-14 | 2013-03-13 | 株式会社免制震ディバイス | Vibration suppression device |
| JP2014163496A (en) * | 2013-02-27 | 2014-09-08 | Takenaka Komuten Co Ltd | Fluid damper |
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