JP4129937B2

JP4129937B2 - Hydraulic damping device

Info

Publication number: JP4129937B2
Application number: JP10058299A
Authority: JP
Inventors: 治高橋; 泉田村
Original assignee: Kozo Keikaku Engineering Inc; Sanwa Tekki Corp
Current assignee: Kozo Keikaku Engineering Inc; Sanwa Tekki Corp
Priority date: 1999-04-07
Filing date: 1999-04-07
Publication date: 2008-08-06
Anticipated expiration: 2019-04-07
Also published as: JP2000291715A

Description

【０００１】
【発明の属する技術分野】
本発明は、制振対象に対する風などによる低速の振動を減衰させる一方、地震などの高速の振動に対して過大な減衰力の発生を防止し、高層ビル、橋梁やプラントなどの大型化傾向にある柱梁架構や、高速化する鉄道車両や自動車など、多様な振動を伴う輸送機器に適用される油圧式の制振装置に関するものである。
【０００２】
【従来の技術】
従来の油圧制振装置は、支持体又は被支持体の一方にシリンダが連結され、他方にはシリンダに出入り自在に挿入したピストンロッドが連結され、このピストンロッドに、シリンダ内を第１及び第２の圧力室に区画するピストンを固定し、シリンダの内部に作動油を充填している。シリンダの第１、第２の圧力室には作動油を供給するオイルリザーバが連通し、この連通路上には弁機構が介設される。この弁機構はピストンの移動に伴う作動油の流れを制御して制振効果を得るものである。オイルリザーバ及び弁機構はシリンダの外側に一体または別体に設けられている。弁機構に用いられる調圧弁は、弁体を単一の圧縮ばねでこれを閉じる方向に付勢する型式のもので、弁座に対する弁体の位置により開放部の広さが変化して吐出される作動油の圧力を調整する。また、オイルリザーバから作動油を供給する給油弁は、オイルリザーバから供給される油通路を閉じるように弁ばねで付勢され、弁体の先端に小孔を備えている。
【０００３】
【発明が解決しようとする課題】
上記従来の油圧制振装置においては、調圧弁による作動油の圧力調整が単一のばねに依存しているので、制振装置の速度−減衰力特性を調圧弁の弁体のテーパの傾斜した輪郭線を直線状にして比例関係にしようとすると、弁ばねに若干の遊びを設ける必要が生じ、低速域では十分な圧力調整ができず、減衰力が低下して制振効果が減少してしまう。調圧弁の弁体のテーパの傾斜した輪郭線を湾曲線状にして弁ばねの遊びをなくすことができるが、加工精度などに難がある。また、シリンダの外側に弁機構やオイルリザーバが固定されるので、装置の小型化を妨げるし、製作も容易でなくコスト高になってしまうという問題がある。さらに、給油弁では、振動数や変位が大きくなってダイナミックレベルが高くなると、弁体の小孔だけでは過給油を防止することができず、これに対して小孔を拡大させると、圧力室への給油が不十分になるという問題がある。
そこで、本発明は、低速域から高速域までの作動油の速度に比例した圧力調整を行う調圧弁を用いてコンパクトな構造で、装置全体の小型化を図れ、しかも広い範囲で安定した制振作用を発揮し、さらに作動油の過不足のない適切な給油を行う油圧制振装置を提供することを課題としている。
【０００４】
【課題を解決するための手段】
上記課題を解決するため、本発明においては、支持体又は被支持体の一方に連結され、内部に作動油を収容したシリンダ１と、他方に連結され、シリンダ１に出入り自在に挿入されたピストンロッド２と、このピストンロッド２に固定され、シリンダ１内を第１及び第２の圧力室７，８に区画すると共に、軸線方向に間隔を置いて相対向し、両者の空間に油通室を形成する一対のピストン３と、油通室９に作動油を供給するオイルリザーバ１１と、第１、第２の圧力室７，８と油通室９との間に介在するようにピストン３に夫々設けられ、作動油の流通路２ａを開閉する弁機構とを具備させて油圧制振装置を構成した。特に、弁機構に、ばね力の異なる弁ばね１６ｃ，１７ｃを用いた調圧弁１６，１７を設けた。
また、弁機構に、圧縮長に対してばね力が曲線的に変化する弁ばね１９ｃを用いた調圧弁１８を設けた。
さらに、オイルリザーバ１１と油通室９とのの連通路２ａに給油弁１２と低圧弁１３とを設けて、給油の過不足をなくした。
【０００５】
【発明の実施の形態】
本発明の実施の一形態を図面を参照して説明する。図１は本発明に係る油圧制振装置の縦断面図、図２は図１のII−II線断面図、図３は図１のIII−III線断面図、図４は図２のIV−IV線断面図、図５は図２のV−V線断面図、図６は給油弁の縦断面図、図７（Ａ）は吸油弁の縦断面図、図７（Ｂ）は吸油弁の正面図、図８（Ａ）は第１調圧弁の縦断面図、（Ｂ）は第２調圧弁の縦断面図、図９は定圧弁の縦断面図である。
図１において、この油圧制振装置は、図示しない構築物のような支持体又は被支持体に引手４を介して連結されるシリンダ１と、被支持体又は支持体に引手５を介して連結され、シリンダ１に軸線方向へ出入り自在に挿入されたピストンロッド２とを備えている。ピストンロッド２にカラー６で固定されたピストン３は、シリンダ１内を第１及び第２の圧力室７，８に区画する。このピストン３は、軸線方向に間隔を置いて相対向して一対設けられ、互いにボルトで結合されている。ピストン３，３とシリンダ１との間には、油通室９が形成される。
【０００６】
ピストンロッド２の自由端側には、軸線方向に内部を連通路２ａが貫通している。一方、シリンダ１の閉鎖端側内部には、ピストンロッド２の端部を気密にかつ軸線方向へ出入り自在に受け入れる円筒状のロッドカバー１０が固定されている。このロッドカバー１０の一端はシリンダ１の閉鎖端壁に固定され、他端がシリンダ１の側壁に気密に嵌合し固定されている。従って、ロッドカバー１０の端部がシリンダ１の閉鎖端側を圧力室７と仕切ってオイルリザーバ１１が形成される。オイルリザーバ１１は、ロッドカバー１０に開口する連通孔１０ａによってロッドカバー１０と連通している。第１及び第２の圧力室７，８及び油通室９に充填される作動油は連通路２ａを通じてオイルリザーバ１１から供給される。ピストンロッド２の先端には連通路２ａを開閉する給油弁１２及び低圧弁１３が設けられている。
【０００７】
給油弁１２は、図６に示すように、弁室１２ａ内に弁体１２ｂが圧縮された弁ばね１２ｃを介してオイルリザーバ１１側の弁座１２ｄに押し付けられるように構成されている。弁体１２ｂは弁室１２ａに軸線方向へ摺動自在に嵌合しているが、一端側の小径部と弁室１２ａとの間に空隙を形成してそこに開口する連通孔１２ｅにより弁体１２ｂの前後の油通路が連通する。即ち、弁体１２ｂが弁ばね１２ｃに抗して図中右方へ移動して弁を開き、オイルリザーバ１１から作動油を供給し、連通路２ａ側の圧力が回復すると、弁ばね１２ｃを圧縮しながら元位置に復帰して弁を閉じる。給油弁１２は、一方の圧力室７（８）が収縮するときに、作動油自体の弾性によって他方の圧力室８（７）への作動油の供給が不足するのを防止するため、オイルリザーバ１１から作動油を補給する。
【０００８】
また、給油弁１２に隣設した低圧弁１３は、給油弁１２とほぼ同様な構成を有する。即ち、弁室１３ａ内に弁体１３ｂが圧縮された弁ばね１３ｃを介して連通路２ａ側の弁座１３ｄに押し付けられるように構成されている。弁体１３ｂは弁室１３ａに軸線方向へ摺動自在に嵌合しているが、一端側の小径部と弁室１３ａとの間に空隙を形成してそこに開口する連通孔１３ｅにより弁体１３ｂの前後の油通路が連通する。即ち、連通路２ａ側の油圧が高まって、弁体１３ｂが弁ばね１３ｃに抗して図中左方へ移動して弁を開き、オイルリザーバ１１へ作動油を吐出し、連通路２ａ側の圧力が低下すると、弁ばね１３ｃを圧縮しながら元位置に復帰して弁を閉じる。なお、弁ばね１３ｃは給油弁１２のそれよりばね力の強いものが適用される。一方の圧力室７（８）が収縮するときに、給油弁１２が開いて他方の圧力室８（７）への作動油を補給するが、作動油の供給が過大になって油通室９側の油圧が高まると、後述する他の各弁は弁ばねのばね力が大きくなった状態になってしまい、収縮側圧力室７（８）の油圧を当初の設定より上昇させてしまう。これを回避するために、低圧弁１３が開いてオイルリザーバ１１へ作動油を吐出する。なお、給油弁１２は０.２〜０.４気圧程度で開き、低圧弁１３は２〜４気圧程度で開くように設定されている。
【０００９】
図２乃至図４に示すように、両ピストン３，３には、第１及び第２圧力室７，８と油通室９との間を開閉する吸油弁１４が夫々設けられている。この吸油弁１４は、図７に示すように、ピストン３に形成された弁室１４ａ内に弁体１４ｂが弁ばね１４ｃを介して設けられている。弁体１４ｂは弁ばね１４ｃで弁室１４ａを油通室９から閉じる方向に付勢される。吸油弁１４は、容積が拡張して負圧になった一方の圧力室７（８）へ、収縮して作動油を吐出する他方の圧力室８（７）から油通室９を介して作動油を供給するように開く。吸油弁１４と圧力室７，８との仕切り板１５には複数の油通孔１５ａを有し、弁室１４ａと圧力室７，８とを連通させる。
【００１０】
図２、図３及び図５に示すように、ピストン３，３には、第１及び第２圧力室７，８と油通室９との間を開閉する第１，第２調圧弁１６，１７が夫々設けられている。第１調圧弁１６は、図８に示すように、逆向き一対の弁体１６ｂ，１６ｂが軸線方向へ伸縮自在に夫々連結されてピストン３，３間をわたり、弁ばね１６ｃで弁座１６ａ側に夫々付勢されて弁を閉じている。弁体１６ｂは傾斜した輪郭線が直線を成す先細りのテーパを有し、その端部が開口内に挿入されてテーパ面が弁座１６ａに当接するようになっている。第２調圧弁１７も第１調圧弁１６と同様に、逆向き一対の弁体１７ｂ，１７ｂが軸線方向へ伸縮自在に夫々連結されてピストン３，３間をわたり、弁ばね１７ｃで弁座１７ａ側に夫々付勢されて弁を閉じている。そして弁体１７ｂは先細りのテーパを有し、開口内に挿入されている。第２調圧弁１７の弁ばね１７ｃは第１調圧弁１６のそれ１６ｃよりばね力の大きいものが適用される。そして、一方の圧力室７（８）が収縮して油圧が高まると、先ず第１調圧弁１６の弁体１６ｂ，１６ｂ間が収縮し始め、油圧が一定以上になってから第２調圧弁１７の弁体１７ｂ，１７ｂ間が収縮し始めて共に圧縮されるようになっている。なお、調圧弁１６，１７は後記する定圧弁１８のそれより弁座１６ｄ，１７ｄの開口径が小さく、しかも両弁ばね１６ｃ，１７ｆのばね力が小さいので、定圧弁１８に設定された作動開始圧力以下の範囲でのピストン３の移動時に作動油の流れに対してピストン３の移動速度に比例した圧力を与える。また、この速度範囲内において、一定の速度以下の低速のピストン３の移動に対し第１調圧弁１６が弁ばね１６ｃの弱いばね力で作動油の圧力を調整し、一定の速度以上のピストン３の移動に対し第１調圧弁１６の弁ばね１６ｃと共に第２調圧弁１７が弁ばね１７ｃの強いばね力を合算した力で作動油の圧力を調整することにより移動速度に比例した圧力を与える。各弁座１６ａ，１７ａは、固定ねじ１６ｄ，１７ｄを調整ナット１６ｅ，１７ｅに螺合させてピストン３に固定される。固定ねじ１６ｄ，１７ｄのねじ穴は調整ナット１６ｅ，１７ｅに円弧状に複数設けられており、固定ねじ１６ｄ，１７ｄに結合させるねじ穴を適宜変更することにより弁座１６ａ，１７ａの位置が前後に変わって弁ばね１６ｃ，１７ｃの圧縮長を調整することができる。
【００１１】
図２乃至図４に示すように、ピストン３，３には、第１及び第２圧力室７，８と油通室９との間を開閉する二つの定圧弁１８が設けられている。各定圧弁１８は、図９に示すように、逆向き一対の弁体１８ｂ，１８ｂが軸線方向へ伸縮自在に連結され、ピストン３，３間をわたっており、圧縮された弁ばね１８ｃで延長方向へ弁座１８ａに夫々付勢されている。弁座１８ａは、固定ねじ１８ｄを調整ナット１８ｅに螺合させてピストン３に固定される。固定ねじ１８ｄのねじ穴は調整ナット１８ｅに複数設けられており、固定ねじ１８ｄに結合させるねじ穴を適宜変更することにより弁座１８ａの位置が前後に位置調整でき弁ばね１８ｃの圧縮長を調整することができる。この定圧弁１８は、ピストン３の速度の増加と共に調圧弁１６，１７の調整する圧力が上昇し、一定の圧力に達したときに開いて圧力上昇を防止して、ピストン３の移動を許容する。
【００１２】
この油圧制振装置は例えば高層建築物の構造材間に介設する。両者間に振動による相対的変位が生じると、ピストンロッド２がシリンダ１内に押し込まれ、あるいはそれから引き出される。いま、風などにより高層建築物に加わる一定の速度以下の遅い振動により、ピストン３が左行すると、圧力室７側の調圧弁１６が開いて作動油の流れに対してピストン３の移動速度に比例した抵抗を与えて、振動を減衰させる。このとき、低速域の振動の場合には、ピストン３の移動に伴う第１調圧弁１６の弁ばね１６ｃの弱いばね力で作動油の圧力を調整する。高速域の振動の場合には、ピストン３の移動に伴う第１調圧弁１６の弁ばね１６ｃの弱いばね力に第２調圧弁１７の弁ばね１７ｃの強いばね力を加えて作動油の圧力を調整する。従って、低速域から高速域まで速度に比例した圧力が発生するので、振動に対する適切な減衰力が得られる。
【００１３】
一方、地震などにより高層建築物に加わる一定の速度以上の振動により、ピストン３が急激に左行すると、調圧弁１６．１７の発生する圧力が定圧弁１８の作動開始圧力に達し、定圧弁１８が開いて作動油を油通室９に吐出して過大な抵抗力を抑制して建屋などの破損を防止する。
【００１４】
振動時のピストンの移動によって一方の圧力室７（８）が収縮するとき、給油弁１２が開き、連通路２ａを介してオイルリザーバ１１から作動油を補給する。従って、作動油自体の弾性による他方の圧力室８（７）への作動油の供給不足を防止する。このとき、他方の圧力室８（７）への作動油の供給により油通路２ａ側の油圧が一定以上に高まると、低圧弁１３が開いて、調圧弁１６．１７及び定圧弁１８の動作開始圧力が初期の設定から狂うことがない。
【００１５】
他の実施形態を図１０及び図１１に示す。本実施形態においては、先の第１，第２調圧弁に代えて、ばね力変動型の調圧弁１９を設ける。この調圧弁１９の弁ばね１９ｃには、ピッチが不均一な不等ピッチばねを適用している。弁ばね１９ｃのばね力は、通常のばねのように圧縮長によって比例的に変化せず、圧縮長の小さい範囲でばね力が弱く、大きい範囲で強くなる曲線状の変化を示す。従って、低速域の振動の場合には、ピストン３の移動に伴う調圧弁１９の弁ばね１９ｃの弱いばね力で作動油の圧力を調整し、高速域の振動の場合には、ピストン３の移動に伴う調圧弁１９の強いばね力で作動油の圧力を調整する。従って、低速域から高速域まで低速域でも十分な圧力調整ができ、適切な減衰力が得られる。
【００１６】
【発明の効果】
以上のように、本発明の油圧制振装置においては、低速域からピストンの速度に比例した振動減衰力を発生するため、風などの微振動にも有効に作用するので、低速域から高速域まで広い範囲で振動の減衰力を得ることができる。
また、シリンダ及びピストンに一体に組み込む構成であるから、装置がコンパクトになり、全体を小型化することができ、製作も容易で、安価に提供することができる。
さらに、ピストンの移動時に作動油の供給を過不足なく適切に行うことができ、弁機構の動作を初期の設定通りに確実に行うできるから、安定した制振作用を発揮するという効果がある。
【図面の簡単な説明】
【図１】本発明に係る油圧制振装置の縦断面図である。
【図２】図１のII−II線断面図である。
【図３】図１のIII−III線断面図である。
【図４】図２のIV−IV線断面図である。
【図５】図２のV−V線断面図である。
【図６】給油弁の縦断面図である。
【図７】（Ａ）は吸油弁の縦断面図、（Ｂ）は吸油弁の正面図である。
【図８】調圧弁の縦断面図である。
【図９】定圧弁の縦断面図である。
【図１０】図１のVIII−VIII線断面図である。
【図１１】他の実施形態の調圧弁の縦断面図である。
【符号の説明】
１シリンダ
２ピストンロッド
２ａ連通路
３ピストン
７圧力室
８圧力室
９油通室
１０給油弁
１１オイルリザーバ
１４吸油弁
１６第１の調圧弁
１６ｃ弁ばね
１７第２の調圧弁
１７ｃ弁ばね
１８定圧弁
１９調圧弁
１９ｃ弁ばね[0001]
BACKGROUND OF THE INVENTION
The present invention attenuates low-speed vibration caused by wind or the like on the object to be damped, while preventing excessive damping force from being generated due to high-speed vibration such as an earthquake, and tends to increase the size of high-rise buildings, bridges, plants, etc. The present invention relates to a hydraulic vibration control device that is applied to transportation equipment with various vibrations, such as a column beam structure, a railway vehicle and an automobile that are increased in speed.
[0002]
[Prior art]
In a conventional hydraulic vibration damping device, a cylinder is connected to one of a support body or a supported body, and a piston rod that is inserted into and out of the cylinder is connected to the other. The piston partitioned into two pressure chambers is fixed, and the inside of the cylinder is filled with hydraulic oil. An oil reservoir that supplies hydraulic oil communicates with the first and second pressure chambers of the cylinder, and a valve mechanism is interposed on the communication path. This valve mechanism obtains a damping effect by controlling the flow of hydraulic oil accompanying the movement of the piston. The oil reservoir and the valve mechanism are integrally or separately provided outside the cylinder. The pressure regulating valve used in the valve mechanism is a type that urges the valve body in a direction to close it with a single compression spring, and the opening part changes in width depending on the position of the valve body with respect to the valve seat. Adjust the hydraulic oil pressure. The oil supply valve that supplies hydraulic oil from the oil reservoir is urged by a valve spring so as to close the oil passage supplied from the oil reservoir, and has a small hole at the tip of the valve body.
[0003]
[Problems to be solved by the invention]
In the conventional hydraulic damping device, since the pressure adjustment of the hydraulic oil by the pressure regulating valve depends on a single spring, the speed-damping force characteristic of the damping device is inclined by the taper of the valve body of the pressure regulating valve. If you try to make the contour line in a straight line and make it proportional, it will be necessary to provide some play in the valve spring, and it will not be possible to adjust the pressure sufficiently in the low speed range, reducing the damping force and reducing the damping effect End up. Although the tapered contour of the valve body of the pressure regulating valve can be curved, the play of the valve spring can be eliminated, but the processing accuracy and the like are difficult. Further, since the valve mechanism and the oil reservoir are fixed outside the cylinder, there is a problem in that the apparatus is prevented from being miniaturized and the manufacturing is not easy and the cost is increased. Furthermore, in a fuel supply valve, if the frequency and displacement increase and the dynamic level increases, it is not possible to prevent supercharging with only a small hole in the valve body. There is a problem of insufficient refueling.
Therefore, the present invention has a compact structure using a pressure regulating valve that adjusts the pressure in proportion to the speed of the hydraulic oil from the low speed range to the high speed range, and can achieve downsizing of the entire apparatus and stable vibration suppression in a wide range. It is an object of the present invention to provide a hydraulic vibration control device that exhibits an action and performs appropriate oil supply without excessive or insufficient hydraulic oil.
[0004]
[Means for Solving the Problems]
In order to solve the above-mentioned problems, in the present invention, a cylinder 1 connected to one of a support body or a support body and containing hydraulic oil inside, and a piston connected to the other and inserted into the cylinder 1 so as to freely enter and exit. The rod 2 is fixed to the piston rod 2, and the inside of the cylinder 1 is partitioned into first and second pressure chambers 7 and 8, and is opposed to each other with an interval in the axial direction. The piston 3 so as to be interposed between the first and second pressure chambers 7 and 8 and the oil passage chamber 9. And a valve mechanism that opens and closes the hydraulic oil flow passage 2a to form a hydraulic damping device. In particular, pressure regulating valves 16 and 17 using valve springs 16c and 17c having different spring forces are provided in the valve mechanism.
Moreover, the pressure regulating valve 18 using the valve spring 19c in which the spring force changes in a curve with respect to the compression length is provided in the valve mechanism.
Furthermore, an oil supply valve 12 and a low pressure valve 13 are provided in the communication path 2a between the oil reservoir 11 and the oil passage chamber 9, thereby eliminating excess or shortage of oil supply.
[0005]
DETAILED DESCRIPTION OF THE INVENTION
An embodiment of the present invention will be described with reference to the drawings. 1 is a longitudinal sectional view of a hydraulic damping device according to the present invention, FIG. 2 is a sectional view taken along line II-II in FIG. 1, FIG. 3 is a sectional view taken along line III-III in FIG. IV sectional view, FIG. 5 is a sectional view taken along line VV in FIG. 2, FIG. 6 is a longitudinal sectional view of the oil supply valve, FIG. 7A is a longitudinal sectional view of the oil absorbing valve, and FIG. FIG. 8A is a longitudinal sectional view of the first pressure regulating valve, FIG. 8B is a longitudinal sectional view of the second pressure regulating valve, and FIG. 9 is a longitudinal sectional view of the constant pressure valve.
In FIG. 1, the hydraulic vibration control device is connected to a support body or a supported body such as a structure (not shown) via a handle 4, and to a supported body or a support body via a handle 5. The piston rod 2 is inserted into the cylinder 1 so as to freely enter and exit in the axial direction. The piston 3 fixed to the piston rod 2 with a collar 6 partitions the inside of the cylinder 1 into first and second pressure chambers 7 and 8. A pair of the pistons 3 are provided to face each other with an interval in the axial direction, and are coupled to each other by bolts. An oil passage chamber 9 is formed between the pistons 3 and 3 and the cylinder 1.
[0006]
On the free end side of the piston rod 2, a communication passage 2 a passes through the inside in the axial direction. On the other hand, a cylindrical rod cover 10 that receives the end of the piston rod 2 in an airtight manner so as to freely enter and exit in the axial direction is fixed inside the closed end of the cylinder 1. One end of the rod cover 10 is fixed to the closed end wall of the cylinder 1, and the other end is hermetically fitted and fixed to the side wall of the cylinder 1. Therefore, the oil reservoir 11 is formed by the end of the rod cover 10 partitioning the closed end side of the cylinder 1 from the pressure chamber 7. The oil reservoir 11 communicates with the rod cover 10 through a communication hole 10 a that opens to the rod cover 10. The hydraulic oil filled in the first and second pressure chambers 7 and 8 and the oil passage chamber 9 is supplied from the oil reservoir 11 through the communication passage 2a. An oil supply valve 12 and a low pressure valve 13 for opening and closing the communication passage 2a are provided at the tip of the piston rod 2.
[0007]
As shown in FIG. 6, the oil supply valve 12 is configured to be pressed against a valve seat 12d on the oil reservoir 11 side through a valve spring 12c in which a valve body 12b is compressed in a valve chamber 12a. The valve body 12b is fitted to the valve chamber 12a so as to be slidable in the axial direction, but a valve body is formed by a communication hole 12e that forms an air gap between the small diameter portion on one end side and the valve chamber 12a and opens there. The oil passages before and after 12b communicate with each other. That is, the valve body 12b moves to the right in the figure against the valve spring 12c, opens the valve, supplies hydraulic oil from the oil reservoir 11, and compresses the valve spring 12c when the pressure on the communication path 2a side recovers. While returning to the original position, the valve is closed. The oil supply valve 12 is provided with an oil reservoir for preventing the supply of hydraulic oil to the other pressure chamber 8 (7) due to the elasticity of the hydraulic oil itself when one pressure chamber 7 (8) contracts. 11 to replenish hydraulic oil.
[0008]
Further, the low pressure valve 13 provided adjacent to the fuel supply valve 12 has substantially the same configuration as the fuel supply valve 12. That is, the valve body 13b is configured to be pressed against the valve seat 13d on the side of the communication passage 2a through the valve spring 13c compressed in the valve chamber 13a. The valve body 13b is fitted to the valve chamber 13a so as to be slidable in the axial direction, but a valve body is formed by a communication hole 13e that forms a gap between the small diameter portion on one end side and the valve chamber 13a and opens there. The oil passages before and after 13b communicate. That is, the hydraulic pressure on the side of the communication path 2a increases, the valve element 13b moves to the left in the figure against the valve spring 13c, opens the valve, discharges hydraulic oil to the oil reservoir 11, and discharges the hydraulic oil on the side of the communication path 2a. When the pressure decreases, the valve spring 13c is compressed while returning to the original position to close the valve. A valve spring 13c having a stronger spring force than that of the oil supply valve 12 is applied. When one of the pressure chambers 7 (8) contracts, the oil supply valve 12 opens to supply hydraulic oil to the other pressure chamber 8 (7). However, the supply of hydraulic oil becomes excessive and the oil passage chamber 9 When the hydraulic pressure on the side increases, the other valves, which will be described later, are in a state in which the spring force of the valve spring is increased, and the hydraulic pressure in the contraction side pressure chamber 7 (8) is increased from the initial setting. In order to avoid this, the low pressure valve 13 opens and discharges hydraulic oil to the oil reservoir 11. The refueling valve 12 is set to open at about 0.2 to 0.4 atm, and the low pressure valve 13 is set to open at about 2 to 4 atm.
[0009]
As shown in FIGS. 2 to 4, both pistons 3, 3 are provided with oil absorption valves 14 that open and close between the first and second pressure chambers 7, 8 and the oil passage chamber 9. As shown in FIG. 7, the oil absorbing valve 14 is provided with a valve body 14b in a valve chamber 14a formed in the piston 3 via a valve spring 14c. The valve body 14b is biased by the valve spring 14c in a direction to close the valve chamber 14a from the oil passage chamber 9. The oil suction valve 14 is operated via the oil passage chamber 9 from the other pressure chamber 8 (7) that contracts and discharges the hydraulic oil to the one pressure chamber 7 (8) whose volume has become negative due to expansion. Open to supply oil. The partition plate 15 between the oil absorption valve 14 and the pressure chambers 7 and 8 has a plurality of oil passage holes 15a, and the valve chamber 14a and the pressure chambers 7 and 8 are communicated with each other.
[0010]
As shown in FIGS. 2, 3, and 5, the pistons 3, 3 include first and second pressure regulating valves 16 that open and close between the first and second pressure chambers 7, 8 and the oil passage chamber 9. 17 are provided. As shown in FIG. 8, the first pressure regulating valve 16 includes a pair of oppositely facing valve bodies 16b and 16b that are connected to each other so as to be expandable and contractable in the axial direction. Each is energized to close the valve. The valve body 16b has a tapered taper in which an inclined contour line forms a straight line, and an end portion of the valve body 16b is inserted into the opening so that the tapered surface comes into contact with the valve seat 16a. Similarly to the first pressure regulating valve 16, the second pressure regulating valve 17 includes a pair of oppositely directed valve bodies 17b and 17b that are connected to each other so as to expand and contract in the axial direction and pass between the pistons 3 and 3, and a valve seat 17a by a valve spring 17c. Each side is energized to close the valve. The valve body 17b has a tapered taper and is inserted into the opening. As the valve spring 17c of the second pressure regulating valve 17, one having a spring force larger than that of the first pressure regulating valve 16c is applied. When one of the pressure chambers 7 (8) contracts to increase the hydraulic pressure, the valve body 16b, 16b of the first pressure regulating valve 16 begins to contract first. The valve bodies 17b, 17b begin to contract and are compressed together. Since the pressure regulating valves 16 and 17 have smaller opening diameters of the valve seats 16d and 17d than those of the constant pressure valve 18 to be described later, and the spring force of both valve springs 16c and 17f is small, the operation start set for the constant pressure valve 18 is started. When the piston 3 moves in a range below the pressure, a pressure proportional to the moving speed of the piston 3 is applied to the flow of hydraulic oil. Further, within this speed range, the first pressure regulating valve 16 adjusts the pressure of the hydraulic oil with the weak spring force of the valve spring 16c with respect to the movement of the low-speed piston 3 below a certain speed, and the piston 3 above the certain speed. The second pressure regulating valve 17 together with the valve spring 16c of the first pressure regulating valve 16 adjusts the pressure of the hydraulic oil with a force obtained by adding the strong spring force of the valve spring 17c to give a pressure proportional to the moving speed. The valve seats 16a and 17a are fixed to the piston 3 by screwing fixing screws 16d and 17d to the adjusting nuts 16e and 17e. A plurality of screw holes of the fixing screws 16d and 17d are provided in an arc shape in the adjusting nuts 16e and 17e, and the positions of the valve seats 16a and 17a can be moved back and forth by appropriately changing the screw holes to be coupled to the fixing screws 16d and 17d. Instead, the compression lengths of the valve springs 16c and 17c can be adjusted.
[0011]
As shown in FIGS. 2 to 4, the pistons 3 and 3 are provided with two constant pressure valves 18 that open and close between the first and second pressure chambers 7 and 8 and the oil passage chamber 9. As shown in FIG. 9, each constant pressure valve 18 has a pair of oppositely directed valve bodies 18b and 18b that are connected to each other so as to expand and contract in the axial direction, extend between the pistons 3 and 3, and are extended by a compressed valve spring 18c. The valve seat 18a is urged in the direction. The valve seat 18a is fixed to the piston 3 by screwing a fixing screw 18d into the adjustment nut 18e. A plurality of screw holes of the fixing screw 18d are provided in the adjusting nut 18e, and the position of the valve seat 18a can be adjusted back and forth by appropriately changing the screw hole coupled to the fixing screw 18d, and the compression length of the valve spring 18c is adjusted. can do. This constant pressure valve 18 increases when the speed of the piston 3 increases, and the pressure adjusted by the pressure regulating valves 16 and 17 increases. When the pressure reaches a constant pressure, the constant pressure valve 18 opens to prevent the pressure increase and allow the piston 3 to move. .
[0012]
This hydraulic vibration control device is interposed between structural materials of high-rise buildings, for example. When a relative displacement due to vibration occurs between them, the piston rod 2 is pushed into the cylinder 1 or pulled out therefrom. Now, when the piston 3 moves to the left due to slow vibration below a certain speed applied to the high-rise building due to wind or the like, the pressure regulating valve 16 on the pressure chamber 7 side is opened, and the moving speed of the piston 3 is adjusted with respect to the flow of hydraulic oil. Give proportional resistance to damp vibrations. At this time, in the case of vibration in the low speed range, the pressure of the hydraulic oil is adjusted by the weak spring force of the valve spring 16c of the first pressure regulating valve 16 accompanying the movement of the piston 3. In the case of vibration in the high speed range, the hydraulic spring pressure is increased by applying the strong spring force of the valve spring 17c of the second pressure regulating valve 17 to the weak spring force of the valve spring 16c of the first pressure regulating valve 16 accompanying the movement of the piston 3. adjust. Accordingly, pressure proportional to the speed is generated from the low speed range to the high speed range, so that an appropriate damping force against vibration can be obtained.
[0013]
On the other hand, when the piston 3 suddenly moves to the left due to a vibration of a certain speed or more applied to the high-rise building due to an earthquake or the like, the pressure generated by the pressure regulating valve 16.17 reaches the operation start pressure of the constant pressure valve 18, and the constant pressure valve 18 Opens and discharges hydraulic oil into the oil passage chamber 9 to suppress excessive resistance and prevent damage to buildings and the like.
[0014]
When one of the pressure chambers 7 (8) contracts due to the movement of the piston during vibration, the oil supply valve 12 opens, and hydraulic oil is replenished from the oil reservoir 11 through the communication path 2a. Accordingly, insufficient supply of hydraulic oil to the other pressure chamber 8 (7) due to the elasticity of the hydraulic oil itself is prevented. At this time, when the hydraulic pressure on the oil passage 2a increases to a certain level or more by supplying hydraulic oil to the other pressure chamber 8 (7), the low pressure valve 13 is opened, and the operation of the pressure regulating valve 16.17 and the constant pressure valve 18 is started. The pressure will not go wrong from the initial setting.
[0015]
Another embodiment is shown in FIGS. In the present embodiment, instead of the first and second pressure regulating valves, a spring force variation type pressure regulating valve 19 is provided. As the valve spring 19c of the pressure regulating valve 19, an unequal pitch spring having a non-uniform pitch is applied. The spring force of the valve spring 19c does not change proportionally with the compression length as in a normal spring, but shows a curved change in which the spring force is weak in a small compression length range and strong in a large range. Therefore, in the case of vibration in the low speed range, the hydraulic oil pressure is adjusted by the weak spring force of the valve spring 19c of the pressure regulating valve 19 accompanying the movement of the piston 3, and in the case of vibration in the high speed range, the movement of the piston 3 is adjusted. The pressure of the hydraulic oil is adjusted by the strong spring force of the pressure regulating valve 19 associated therewith. Therefore, sufficient pressure adjustment can be performed in the low speed range from the low speed range to the high speed range, and an appropriate damping force can be obtained.
[0016]
【The invention's effect】
As described above, in the hydraulic vibration damping device of the present invention, since a vibration damping force proportional to the piston speed is generated from the low speed range, it effectively acts on fine vibrations such as wind. Vibration damping force can be obtained in a wide range.
In addition, since the structure is integrated into the cylinder and the piston, the apparatus is compact, the entire apparatus can be downsized, the manufacture is easy, and the apparatus can be provided at low cost.
Furthermore, the hydraulic oil can be appropriately supplied without excess or deficiency during the movement of the piston, and the valve mechanism can be reliably operated according to the initial setting, so that there is an effect of exhibiting a stable damping action.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a hydraulic vibration damping device according to the present invention.
2 is a cross-sectional view taken along line II-II in FIG.
3 is a cross-sectional view taken along line III-III in FIG.
4 is a cross-sectional view taken along line IV-IV in FIG.
5 is a cross-sectional view taken along line VV in FIG.
FIG. 6 is a longitudinal sectional view of an oil supply valve.
7A is a longitudinal sectional view of an oil absorbing valve, and FIG. 7B is a front view of the oil absorbing valve.
FIG. 8 is a longitudinal sectional view of a pressure regulating valve.
FIG. 9 is a longitudinal sectional view of a constant pressure valve.
10 is a cross-sectional view taken along line VIII-VIII in FIG.
FIG. 11 is a longitudinal sectional view of a pressure regulating valve according to another embodiment.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Cylinder 2 Piston rod 2a Communication path 3 Piston 7 Pressure chamber 8 Pressure chamber 9 Oil passage chamber 10 Oil supply valve 11 Oil reservoir 14 Oil absorption valve 16 1st pressure regulation valve 16c Valve spring 17 2nd pressure regulation valve 17c Valve spring 18 Constant pressure valve 19 Pressure regulating valve 19c Valve spring

Claims

A cylinder connected to one of the support or the supported body and containing hydraulic oil therein;
A piston rod connected to the other and inserted into and out of the cylinder;
A pair of pistons fixed to the piston rod, partitioning the inside of the cylinder into first and second pressure chambers, facing each other at an interval in the axial direction, and forming an oil passage chamber in both spaces;
A valve mechanism that is provided in each of the pistons so as to be interposed between the first and second pressure chambers and the oil passage chamber, and that opens and closes a flow passage of hydraulic oil;
The valve mechanism is a pair of valve bodies opposite to each other, each having a tapered taper that opens and closes to a pair of valve seats that are open to the oil passage chamber and are opposed to each other with an interval in the axial direction. And a valve spring that is locked between both valve bodies and biased with a weak spring force in the direction of closing the valve body, and opens and closes between the first and second pressure chambers and the oil passage chamber A first pressure regulating valve,
Similarly, a pair of valve elements opposite to each other with a tapered taper that opens and closes to a pair of valve seats that are opened to the oil passage chamber and face each other with an interval in the axial direction, and both valves The first and second pressure chambers and the oil passage chamber, each having a valve spring that is locked between the bodies and that is biased by a spring force stronger than that of the first pressure regulating valve in the direction of closing the valve body. A second pressure regulating valve that opens and closes between ,
Opening and closing between the oil passage chamber and the first and second pressure chambers, the hydraulic fluid that has flowed into the oil passage chamber from the pressure chamber side that contracts as the piston moves through the pressure regulating valve to the other pressure chamber An oil-absorbing valve that is opened to let it flow out ,
The hydraulic pressure is adjusted by the weak spring force of the valve spring of the first pressure regulating valve for the low speed hydraulic oil, and the hydraulic pressure is adjusted by the strong spring force of the valve spring of the second pressure regulating valve for the high speed hydraulic oil. Thus, the vibration damping device is characterized in that the vibration velocity is effectively damped by bringing the fluid velocity-pressure relationship from the low speed region to the high speed region close to a continuous proportional relationship.

A cylinder connected to one of the support or the supported body and containing hydraulic oil therein;
A piston rod connected to the other and inserted into and out of the cylinder;
A pair of pistons fixed to the piston rod, partitioning the inside of the cylinder into first and second pressure chambers, facing each other at an interval in the axial direction, and forming an oil passage chamber in both spaces;
A valve mechanism that is provided in each of the pistons so as to be interposed between the first and second pressure chambers and the oil passage chamber, and that opens and closes a flow passage of hydraulic oil;
The valve mechanism is a pair of valve bodies opposite to each other, each having a tapered taper that opens and closes to a pair of valve seats that are open to the oil passage chamber and are opposed to each other with an interval in the axial direction. And an unequal pitch valve spring that is locked between the two valve bodies and biases the valve body in a closing direction, and opens and closes between the first and second pressure chambers and the oil passage chamber. A pressure regulating valve ,
Opening and closing between the oil passage chamber and the first and second pressure chambers, the hydraulic fluid that has flowed into the oil passage chamber from the pressure chamber side that contracts as the piston moves through the pressure regulating valve to the other pressure chamber An oil-absorbing valve that is opened to let it flow out ,
By adjusting the hydraulic pressure with the weak spring force of the valve spring of the pressure regulating valve for low speed hydraulic fluid and adjusting the hydraulic pressure with the strong spring force of the valve spring of the pressure regulating valve for high speed hydraulic fluid, A hydraulic damping device that effectively damps vibration by bringing the velocity-pressure relationship of the fluid up to a region close to a continuous proportional relationship.

The valve mechanism opens by the pressure increase of the first or second pressure chamber that contracts due to vibration in a high speed region, and discharges hydraulic oil to the oil passage chamber while maintaining a predetermined pressure, thereby excessively damping the vibration. It further comprises a constant pressure valve that prevents the generation of force,
The cylinder has an oil reservoir inside ,
The piston rod has an oil passage for communicating the oil reservoir and the oil passage chamber,
The oil passage, the oil reservoir excessive working oil to prevent the oil supply valve for replenishment of the hydraulic oil from the oil reservoir, the oil pressure increase of the oil communication chamber in order to prevent the hydraulic pressure drop in the oil communication chamber hydraulic damping device according to claim 1 or 2, characterized in that it comprises a low-pressure valve to return to.