JPH07308704A - Hydraulic screw-down device for rolling mills - Google Patents
Hydraulic screw-down device for rolling millsInfo
- Publication number
- JPH07308704A JPH07308704A JP6105214A JP10521494A JPH07308704A JP H07308704 A JPH07308704 A JP H07308704A JP 6105214 A JP6105214 A JP 6105214A JP 10521494 A JP10521494 A JP 10521494A JP H07308704 A JPH07308704 A JP H07308704A
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- JP
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- Prior art keywords
- pressure
- rod
- hydraulic
- cylinders
- reduction
- 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.)
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Links
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- Control Of Metal Rolling (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この出願に係る発明は、圧延機の
油圧圧下装置に関し、更に詳しくは、油圧圧下装置に装
備されている油圧シリンダを、高油柱で、且つ高応答で
制御しても、ハンチング現象を生じない圧延機用油圧圧
下装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic pressure reducing device for a rolling mill, and more specifically, it controls a hydraulic cylinder equipped in the hydraulic pressure reducing device with a high oil column and with high response. Also, the present invention relates to a hydraulic reduction device for a rolling mill that does not cause a hunting phenomenon.
【０００２】[0002]
【従来の技術と発明が解決しようとする課題】近年、圧
延機のロール圧下装置の多くが電動スクリュー式から油
圧シリンダ式となり、更に、種々寸法のロール組合せで
の使用を可能とするために、より長いストロークの油圧
圧下シリンダが採用される傾向にある。2. Description of the Related Art In recent years, most of the roll reduction devices of rolling mills have been changed from electric screw type to hydraulic cylinder type, and further, in order to enable use in roll combinations of various sizes, There is a tendency for hydraulic stroke cylinders with longer strokes to be adopted.
【０００３】そのため、多くの油圧圧下シリンダの所要
ストローク量が９０〜１５０ミリメートル程度（以下、
９０ミリメートル以上を高油注という。）で、最近では
２００〜２５０ミリメートル、又はそれを越える場合も
あり、従って、このような油注の高い範囲で圧下シリン
ダが制御される場合がある。Therefore, the required stroke amount of many hydraulic pressure reduction cylinders is about 90 to 150 mm (hereinafter,
90 mm or more is called high oil injection. ), More recently 200-250 millimeters, or even more, and thus the reduction cylinder may be controlled in such a high range of oiling.
【０００４】一方、圧延速度と圧延精度の向上に伴い、
一般的な油圧圧下装置の応答性は、シリンダ変位のステ
ップ応答の評価では、数％以内のオーバシュートに収ま
ること、また、周波数応答では２０Ｈｚ（−３ｄｂ）以
上の応答性（以下、高応答という。）を持つことが要求
される。On the other hand, with the improvement of rolling speed and rolling accuracy,
Responsiveness of a general hydraulic pressure reduction device is within a few% overshoot in the step response evaluation of cylinder displacement, and a frequency response of 20Hz (-3db) or more (hereinafter referred to as high response). .) Is required.
【０００５】以上に述べた油圧圧下装置に装備される油
圧圧下シリンダを制御するための油圧回路は、通常、図
５の回路図に示すように構成されている。すなわち、油
圧圧下装置は左右一対の圧下シリンダ１０Ａ，１０Ｂを
持ち、各々には独立した位置制御系が構成され、圧延機
の左右対象に配置されている。なお、圧下シリンダ１０
Ａ，１０Ｂは共に同一構成であり、図において左側の構
成にはＡを付し、右側の構成にはＢを付して説明する。
また、以下の説明においては、Ａを付した左側の構成を
例にして説明し、もう一方の構成にはＢを付して説明は
省略する。The hydraulic circuit for controlling the hydraulic pressure reduction cylinder provided in the hydraulic pressure reduction device described above is usually constructed as shown in the circuit diagram of FIG. That is, the hydraulic pressure reduction device has a pair of left and right pressure reduction cylinders 10A and 10B, each of which has an independent position control system and is disposed symmetrically with respect to the left and right sides of the rolling mill. The reduction cylinder 10
Both A and 10B have the same configuration. In the figure, the left configuration is denoted by A and the right configuration is denoted by B.
In the following description, the left side structure with A is described as an example, and the other structure is with B and the description thereof is omitted.
【０００６】図示するように、シリンダピストン１１Ａ
を有する圧下シリンダ１０Ａのヘッド側１１ａにはシリ
ンダ直付マニホールド１２Ａ（又はバルブブロック）が
設けられ、ロッド側１１ｂには油路１９ａ（通常は配
管）が連結されている。また、もう一方の圧下シリンダ
１０Ｂのロッド側１２ｂにも油路１９ｂ（通常は配管）
が連結されており、これらの油路１９ａ，１９ｂが合流
点２８で合流し、油路１９を介して圧力調整ユニット２
０に連結されている。なお、上記油路１９ａ，１９ｂの
合流点２８は、通常、圧延機上部の圧延ライン中心位置
に配されるので油路１９ａ，１９ｂの長さは各１０メー
トル前後で同一寸法となる。また、上記圧力調整ユニッ
ト２０は地下の油圧源室に配される場合が多く、油路１
９の長さは数十メートル前後となる場合が多い。As shown, the cylinder piston 11A
A cylinder direct attachment manifold 12A (or a valve block) is provided on the head side 11a of the pressure-reducing cylinder 10A having the above, and an oil passage 19a (usually a pipe) is connected to the rod side 11b. Further, the oil passage 19b (usually a pipe) is also provided on the rod side 12b of the other reduction cylinder 10B.
Are connected, and these oil passages 19 a and 19 b meet at a joining point 28, and the pressure adjusting unit 2 is connected via the oil passage 19.
It is linked to 0. Since the confluence point 28 of the oil passages 19a and 19b is usually arranged at the center of the rolling line above the rolling mill, the lengths of the oil passages 19a and 19b are about 10 meters and have the same dimension. Further, the pressure adjusting unit 20 is often arranged in a hydraulic pressure source chamber in the basement, and the oil passage 1
The length of 9 is often around tens of meters.
【０００７】上記シリンダ直付マニホールド１２Ａに
は、圧下シリンダ１０Ａのヘッド側１１ａ内圧を所定の
圧力に保って油柱高さｙを所定高さに保つためのヘッド
側油圧回路Ｈが設けられており、このヘッド側油圧回路
Ｈは、ヘッド側ライン１３ａと供給ライン１３ｂおよび
戻りライン１３ｃとを切換える３ウエイ型サーボ弁１４
Ａと、ヘッド側ライン１３ａに設けられたパイロット操
作逆止弁１５Ａとにより構成されている。なお、供給ラ
イン１３ｂは図示しない一定油圧源に連結されている。The cylinder-directly mounted manifold 12A is provided with a head side hydraulic circuit H for keeping the internal pressure of the head side 11a of the pressure reducing cylinder 10A at a predetermined pressure and keeping the oil column height y at a predetermined height. The head side hydraulic circuit H includes a three-way type servo valve 14 for switching the head side line 13a, the supply line 13b and the return line 13c.
A and a pilot operated check valve 15A provided on the head side line 13a. The supply line 13b is connected to a constant hydraulic pressure source (not shown).
【０００８】また、上記圧力調整ユニット２０は、通
常、図６の回路図に示すように構成されている。すなわ
ち、油路１９の端部には圧油供給ライン２０ａと圧力調
整ライン２０ｂとを切り換える切換弁２１が設けられて
おり、圧油供給ライン２０ａは油路２２により図５の１
３ｂに示す油圧源とは別の一定油圧源と連結されてい
る。The pressure adjusting unit 20 is usually constructed as shown in the circuit diagram of FIG. That is, a switching valve 21 for switching between the pressure oil supply line 20a and the pressure adjustment line 20b is provided at the end of the oil passage 19, and the pressure oil supply line 20a is connected by the oil passage 22 as shown in FIG.
It is connected to a constant oil pressure source different from the oil pressure source shown in 3b.
【０００９】一方、圧力調整ライン２０ｂは、上記圧油
供給ライン２０ａから分岐した油路２３に設けられた減
圧弁２４と、この減圧弁２４の設定圧力での圧油を蓄圧
するアキュムレータ２５と、このアキュムレータ２５の
圧力が所定圧力以上となった時に圧油を逃がすリリーフ
弁２６とから構成されている。なお、２５ａは可変絞り
で２５ｂは止め弁である。On the other hand, the pressure adjusting line 20b includes a pressure reducing valve 24 provided in an oil passage 23 branched from the pressure oil supply line 20a, and an accumulator 25 for accumulating the pressure oil at the pressure set by the pressure reducing valve 24. It is composed of a relief valve 26 that releases pressure oil when the pressure of the accumulator 25 becomes equal to or higher than a predetermined pressure. In addition, 25a is a variable throttle and 25b is a stop valve.
【００１０】そして、圧下シリンダ１０Ａのロッド側１
１ｂの圧力を圧力調整ユニット２０により、所定圧力範
囲内（上記減圧弁２４の設定圧力とリリーフ弁２６の設
定圧力の差、ただしリリーフ弁設定圧＜減圧弁設定圧）
に保持した状態で、上記ヘッド側油圧回路Ｈによりヘッ
ド側１１ａの圧力を調節して、シリンダピストン１１Ａ
の変位すなわちロール間隙を調整している。Then, the rod side 1 of the reduction cylinder 10A
The pressure of 1b is set within a predetermined pressure range by the pressure adjusting unit 20 (difference between the set pressure of the pressure reducing valve 24 and the set pressure of the relief valve 26, where relief valve setting pressure <pressure reducing valve setting pressure).
The pressure on the head side 11a is adjusted by the head side hydraulic circuit H while being held at
Is adjusted, that is, the roll gap is adjusted.
【００１１】一方、シリンダピストン１１Ａの変位は図
５に示す位置検出器１６Ａにより検出されて、演算アン
プ１７Ａにフィードバックされ、演算アンプ１７Ａでは
指令値１７ａと比較し、その差（制御偏差）に必要な調
整ゲイン（制御ゲイン）を乗じた制御信号をサーボアン
プ１８Ａに送り、サーボ弁１４Ａでシリンダピストン１
１Ａの変位が所定の値となるように制御する。なお、圧
下シリンダ１０Ｂ側も同様の機能を持っている。On the other hand, the displacement of the cylinder piston 11A is detected by the position detector 16A shown in FIG. 5 and fed back to the operational amplifier 17A. The operational amplifier 17A compares it with the command value 17a and needs the difference (control deviation). The control signal multiplied by the appropriate adjustment gain (control gain) is sent to the servo amplifier 18A, and the servo valve 14A causes the cylinder piston 1 to move.
The displacement of 1 A is controlled to a predetermined value. The reduction cylinder 10B side has the same function.
【００１２】このような油圧圧下装置の制御系としての
応答性（追従性）は、演算アンプ１７Ａの制御ゲインの
増加に対応して高くなり、制御ゲインを更に大きくして
いくと制御系は不安定となり最終的には発振現象を起こ
すが、この時の発振周波数は制御ゲインの増加に対応し
て高くなる。The responsiveness (following performance) of the control system of such a hydraulic pressure reducing device increases as the control gain of the operational amplifier 17A increases, and the control system becomes unusable as the control gain is further increased. It becomes stable and eventually causes an oscillation phenomenon, but the oscillation frequency at this time becomes higher in accordance with the increase of the control gain.
【００１３】以上のように構成された圧延機用油圧圧下
装置においては、上述したように高油柱で使用される場
合が多くなっているが、以下に述べるような現象によ
り、高油注になると、本来持っている性能、つまり、高
応答性を落として使用せざるを得ない状況が生じてしま
う。In the hydraulic rolling down device for a rolling mill constructed as described above, it is often used in a high oil column as described above. However, due to the phenomenon described below, high oil injection is possible. In that case, there arises a situation in which the original performance, that is, the high responsiveness, is reduced and the device cannot be used.
【００１４】すなわち、例えば５０〜７０ミリメートル
程度の低油柱時には、２０Ｈｚの高応答を持つまで制御
系の制御ゲインを大きくしても、制御系としては安定
（ステップ応答特性上にオーバーシュートは無く、ま
た、外乱等の重畳もなく安定）であったものが、例えば
９０ミリメートル近傍の油柱では、ステップ応答上に、
振幅が数μｍで周波数が２０Ｈｚ以下の外乱（時間と共
に減衰する）が重畳する現象を生じる。That is, for example, in the case of a low oil column of about 50 to 70 mm, even if the control gain of the control system is increased until it has a high response of 20 Hz, the control system is stable (there is no overshoot on the step response characteristic). , And stable without superimposition of disturbances, etc.), for example, in the case of an oil column near 90 mm, on the step response,
A phenomenon in which a disturbance (attenuation with time) having an amplitude of several μm and a frequency of 20 Hz or less is superposed occurs.
【００１５】この状態より制御系の制御ゲインを増加さ
せていくと、上記の外乱の周波数は殆ど変化しないで外
乱振幅の減衰が悪くなり、最終的には持続振動（以下、
この現象をハンチング現象という。）に至る現象を生じ
てしまう。When the control gain of the control system is increased from this state, the frequency of the disturbance hardly changes, the attenuation of the disturbance amplitude deteriorates, and finally the continuous vibration (hereinafter, referred to as
This phenomenon is called a hunting phenomenon. ) Will occur.
【００１６】また、上述した外乱が重畳する現象は、油
柱が高い位置で使用する時ほど顕著に現れるので、この
現象が生じ始める油柱近傍およびそれ以上の油柱では、
所要の応答（例えば、２０Ｈｚ以上）を得るまで制御系
の制御ゲインを上げることができず、結局、高油注（例
えば、９０ミリメートル以上）になればなるほど応答性
を落として使用せざるを得なくなり、応答性を犠牲にし
た使用に制限され、最終的には、圧延精度が低下すると
いう問題につながる。Further, the above-mentioned phenomenon in which the disturbance is superposed appears more prominently when the oil column is used at a higher position. Therefore, in the vicinity of the oil column where this phenomenon begins and at oil columns above it,
The control gain of the control system cannot be increased until a desired response (for example, 20 Hz or more) is obtained, and eventually, the higher the oil injection (for example, 90 mm or more), the lower the responsiveness and the more unavoidable the use. It is no longer available and is limited to use at the expense of responsiveness, eventually leading to the problem of reduced rolling accuracy.
【００１７】一方、このように外乱重畳現象を生じる
と、両圧下シリンダのロッド側が油路を介して連通して
いるため、一方の圧下シリンダが上がれば他方が下がる
方向に、丁度、位相が１８０度ずれた状態で各々の制御
系が発振する現象（以下、シーソー現象という。）を生
じてしまう。このシーソー現象は、圧延中に時折発生
し、この現象を生じると幅方向の圧延精度が大幅に低下
してしまう。On the other hand, when the disturbance superposition phenomenon occurs in this way, since the rod sides of both reduction cylinders communicate with each other through the oil passage, the phase is exactly 180 in the direction in which one reduction cylinder goes up and the other goes down. A phenomenon (hereinafter, seesaw phenomenon) in which each control system oscillates in a deviated state occurs. This seesaw phenomenon occasionally occurs during rolling, and if this phenomenon occurs, rolling accuracy in the width direction is significantly reduced.
【００１８】上述した外乱重畳現象を実測データに基づ
いて以下に説明すると、図７(a) は上記の外乱重畳現象
が生じている状態の実測オシロデータの一例を示すもの
であり、この条件としては、上述した図５および図６に
示す油圧回路においてアキュムレータ止め弁２５ｂを全
開とし、制御ゲインを所要の３０％程度まで下げ、指令
値１７ａに５０μｍ相当のステップ状信号を入れた時の
シリンダピストン１１Ａの位置の応答である。この応答
例より、周波数≒１０Ｈｚを主成分とした外乱が重畳
し、次第に減衰していることが解る。The above-mentioned disturbance superposition phenomenon will be described below based on the measured data. FIG. 7A shows an example of the measured oscilloscope data in the state where the disturbance superposition phenomenon occurs. Is a cylinder piston when the accumulator stop valve 25b is fully opened in the hydraulic circuits shown in FIGS. 5 and 6 described above, the control gain is reduced to about 30% of the required value, and a step signal equivalent to 50 μm is input to the command value 17a. 11A is the position response. From this response example, it can be seen that a disturbance having a frequency of approximately 10 Hz as a main component is superimposed and gradually attenuated.
【００１９】また、図７(b) は同様の条件で、アキュム
レータ止め弁２５ａのみ全閉とした時のデータであり、
この応答例より、周波数≒５．７Ｈｚの外乱が重畳して
おり、上記図７(a) の約１／２の周波数となっている。Further, FIG. 7 (b) shows data when only the accumulator stop valve 25a is fully closed under the same conditions.
From this response example, the disturbance of frequency ≅5.7 Hz is superimposed, which is about half the frequency of FIG. 7 (a).
【００２０】これら図７(a),(b) の外乱重畳現象は、ス
テップ応答によりシリンダピストン１１Ａが油柱が増加
する側に変化（変化後は一定値に保つ制御が働く）し、
ロッド側１１ｂの圧力が上昇して圧力波を生じ、この圧
力波は油路１９ａ，１９中を伝播して管端の圧力調整ユ
ニット２０まで達し、ここでアキュムレータ２５（又は
止め弁２５ｂ）で反射され、ロッド側１１ｂに戻り、再
び反射されるという一連の圧力伝播が繰り返され、この
時の圧力波が制御系への外乱として働き、シリンダピス
トン１１Ａに変化外乱が生じたものと考えられる。In the disturbance superposition phenomenon shown in FIGS. 7 (a) and 7 (b), the cylinder piston 11A changes to the side where the oil column increases by the step response (control to keep the constant value after the change works),
The pressure on the rod side 11b rises to generate a pressure wave, which propagates through the oil passages 19a, 19 and reaches the pressure adjusting unit 20 at the pipe end, where it is reflected by the accumulator 25 (or stop valve 25b). It is considered that a series of pressure propagations, in which the pressure wave is returned to the rod side 11b and is reflected again, is repeated, and the pressure wave at this time acts as a disturbance to the control system, causing a change disturbance to the cylinder piston 11A.
【００２１】つまり、従来の圧延機用油圧圧下装置にあ
っては、シリンダロッド側の圧力を所定圧力内に保持し
た状態で圧下シリンダ１０Ａが使用され、且つ、油圧源
室に設ける圧力調整ユニット２０が圧下シリンダ１０Ａ
から数十メートルも離れて設置されるため、このような
外乱重畳現象を生じ、高油注，高応答にあってはこの外
乱重畳現象の減衰が悪くなり、最終的には持続振動、す
なわちハンチング現象を生じてしまう。従って、高油注
で使用される圧下シリンダは高応答で制御して圧延精度
を向上させることができない。That is, in the conventional hydraulic pressure reducing device for a rolling mill, the pressure reducing cylinder 10A is used while the pressure on the cylinder rod side is kept within a predetermined pressure, and the pressure adjusting unit 20 provided in the hydraulic pressure source chamber is used. Is a reduction cylinder 10A
Since it is installed several tens of meters away from this, such disturbance superposition phenomenon occurs, and in the case of high oil injection and high response, this disturbance superposition phenomenon is poorly damped, and finally it is a continuous vibration, that is, hunting. It causes a phenomenon. Therefore, the reduction cylinder used for high oil injection cannot be controlled with high response to improve rolling accuracy.
【００２２】このことは以下の説明から明らかである。
すなわち、管内の流体柱の固有振動数（自由振動の周
期）は、公知の如く下記の数式で表される。This will be apparent from the following description.
That is, the natural frequency (period of free vibration) of the fluid column in the pipe is represented by the following mathematical formula as is well known.
【００２３】両端開あるいは両端閉の時は、同じ圧力波
が時間ｔ毎に繰り返す、つまり、時間ｔを基本周期とす
る振動系となり、固有振動数Ｎp1は下記〔数１〕とな
る。そして、一端開、一端閉の時は、２ｔを基本周期と
する振動系となり、固有振動数Ｎp2は下記〔数２〕とな
る。When both ends are open or both ends are closed, the same pressure wave repeats every time t, that is, a vibrating system having a basic period of time t, and the natural frequency N p1 becomes the following [ Equation 1]. When the one end is opened and the one end is closed, the vibration system has a basic period of 2t, and the natural frequency N p2 becomes the following [ Formula 2].
【００２４】[0024]
【数１】 [Equation 1]
【００２５】[0025]
【数２】 [Equation 2]
【００２６】上式において、管端が大きな水タンクある
いは空気だめ等の定圧力源に結合されているときは「開
端」とみなされ、また、容積型の流体機器等のように機
械的に閉鎖されているときは、「閉端」として取り扱わ
れる。従って、図５の油路１９の圧力調整ユニット２０
側の管端条件としては、図６の止め弁２５ｂが開いてい
るときはアキュムレータ２５が定圧源として機能するの
で「開端」、逆に止め弁２５ｂを全閉とするときは「閉
端」として取り扱われる。In the above equation, when the pipe end is connected to a constant pressure source such as a large water tank or an air reservoir, it is regarded as "open end", and it is mechanically closed like a positive displacement type fluid device. If it is, it is treated as “closed end”. Therefore, the pressure adjusting unit 20 of the oil passage 19 of FIG.
As the pipe end condition on the side, the accumulator 25 functions as a constant pressure source when the stop valve 25b of FIG. 6 is open, and conversely, when the stop valve 25b is fully closed, it is “closed end”. Be treated.
【００２７】一方、シリンダピストン１１Ａはヘッド側
１１ａおよび油路１３ａ内に閉じ込められている作動油
により剛性支持されるが、作動油は圧縮性流体であるの
で、シリンダロッド側１１ｂの圧力が仮にΔＰR だけ増
加すると、ヘッド側１１ａの作動油は圧縮され、油柱Δ
Ｌy だけ減少する。即ち、油路１９の管端条件は上記ア
キュムレータに近い特性となる。On the other hand, the cylinder piston 11A is rigidly supported by the working oil confined in the head side 11a and the oil passage 13a. However, since the working oil is a compressible fluid, the pressure on the cylinder rod side 11b is assumed to be ΔP. When R is increased, the hydraulic oil on the head side 11a is compressed and the oil column Δ
Decrease by L y . That is, the pipe end condition of the oil passage 19 has characteristics close to those of the accumulator.
【００２８】ここで、各条件を以下の通りとすると、油
柱の減少ΔＬy は、以下の〔数３〕となり、この値は上
述した重畳外乱の振幅と同等の値となる。Here, assuming that each condition is as follows, the decrease ΔL y of the oil column becomes the following [Equation 3], and this value becomes a value equivalent to the amplitude of the above-mentioned superposed disturbance.
【００２９】[0029]
【数３】 [Equation 3]
【００３０】以上のことから、少なくとも、全体の外乱
現象が生じるシリンダピストン位置変化範囲（近傍）に
おいては、管路１９のシリンダ側の管端条件は開端とし
て機能していると考えられる。From the above, it is considered that at least in the cylinder piston position change range (the vicinity) where the disturbance phenomenon occurs, the pipe end condition on the cylinder side of the pipe line 19 functions as an open end.
【００３１】次に、圧力調整ユニット２０とロッド側１
１ｂ油路の合流点２８とを結ぶ油路１９の長さは、通常
の圧延設備にあっては、図６の圧力調整ユニット２０が
地下の油圧源室（セラー）に配置されているため、５０
〜９０メートルと長い油路が必要となり、図７(a),(b)
の実測データに対応する油路１９の長さも総延長で約７
５メートルあり、この時の油路の流体柱の固有振動数Ｎ
p1, Ｎp2は以下の〔数４〕のようになり、この固有振動
数は、上述した図７(a),(b) の実測データとほぼ一致し
ている。Next, the pressure adjusting unit 20 and the rod side 1
The length of the oil passage 19 that connects the confluence point 28 of the 1b oil passage is the same as that of the normal rolling equipment because the pressure adjusting unit 20 of FIG. 6 is arranged in the underground hydraulic source chamber (cellar). Fifty
A long oil passage of ~ 90 meters is required, and Fig. 7 (a), (b)
The total length of the oil passage 19 corresponding to the actual measurement data is about 7
There is 5 meters, the natural frequency N of the fluid column of the oil passage at this time
p1 and N p2 are as shown in the following [ Equation 4], and this natural frequency substantially agrees with the measured data of FIGS. 7 (a) and 7 (b) described above.
【００３２】[0032]
【数４】 [Equation 4]
【００３３】以上のことより、シリンダ側の管端条件は
開端として作用していること、また、図７(a),(b) に重
畳している外乱現象は、シリンダロッド側油路１９ａ，
１９ｂ，１９における流体柱の固有振動（自由振動）の
影響であることが解る。From the above, the pipe end condition on the cylinder side acts as an open end, and the disturbance phenomenon superimposed on FIGS. 7 (a) and 7 (b) is due to the oil passage 19a on the cylinder rod side.
It is understood that this is due to the natural vibration (free vibration) of the fluid column in 19b and 19.
【００３４】一般的に、この固有振動（特性）による圧
力波は、管路抵抗により、又は両端条件が完全反射では
ない（反射率＜１）ので、時間と共にその振幅が減衰す
る特性を示す。Generally, the pressure wave due to this natural vibration (characteristic) exhibits a characteristic that its amplitude attenuates with time because of the pipe resistance or because both end conditions are not perfect reflection (reflectance <1).
【００３５】図７(a),(b) に示す状態から、制御系の制
御ゲインを増加させていくと、上述した如くハンチング
現象を生じるが、これが単なる閉ループ制御系での発振
現象であれば、その発振周波数は制御系の調整ゲインに
対応して変化するが、周波数は殆ど変化しないで一定で
ある。When the control gain of the control system is increased from the states shown in FIGS. 7 (a) and 7 (b), the hunting phenomenon occurs as described above. If this is a mere oscillation phenomenon in the closed loop control system, , Its oscillation frequency changes in accordance with the adjustment gain of the control system, but the frequency is almost unchanged and constant.
【００３６】また、制御系の応答性が重畳外乱の周波
数、すなわち、油路の固有振動数より充分に低い範囲で
は、ハンチング現象を生じることはない。In the range where the response of the control system is sufficiently lower than the frequency of the superposed disturbance, that is, the natural frequency of the oil passage, the hunting phenomenon does not occur.
【００３７】以上２つの事由より、上述したハンチング
現象は、ロッド側油路内の流体柱の固有振動（自由振
動）、即ち、油路の動特性とシリンダ位置制御系の共振
現象又はそれに類する現象であると判断できる。From the above two reasons, the above-mentioned hunting phenomenon is the natural vibration (free vibration) of the fluid column in the oil passage on the rod side, that is, the dynamic characteristic of the oil passage and the resonance phenomenon of the cylinder position control system or a phenomenon similar thereto. Can be determined.
【００３８】従って、上述したように、高油注の圧下シ
リンダにおいては、圧延精度を向上させるために高応答
で制御することができずに圧延精度を低下させている。Therefore, as described above, in the high-oil pouring reduction cylinder, the rolling precision cannot be controlled with high response in order to improve the rolling precision, and the rolling precision is lowered.
【００３９】なお、この種の従来技術として特開昭52−
138464号公報記載の発明があるが、この発明は圧延条件
の変動に関係なく応答性を一定に保持するためにロッド
側圧力を負荷に対応して変更させることで、系ループゲ
インを一定として安定した制御系を実現しようとするも
のであるため、このようなロッド側圧力を変更させる構
成では、この出願に係る発明が対象とする高油注におけ
る高応答では安定した制御を実現することはできない。As a conventional technique of this type, Japanese Patent Laid-Open No. 52-
Although there is an invention described in Japanese Patent No. 138464, this invention stabilizes the system loop gain by keeping the system loop gain constant by changing the rod side pressure in accordance with the load in order to keep the responsiveness constant regardless of changes in rolling conditions. Since it is intended to realize the above-mentioned control system, it is not possible to realize stable control with high response in high oil injection, which is the subject of the invention of this application, with such a configuration that changes the rod side pressure. .
【００４０】また、他の従来技術として、特開昭49− 6
4793号公報記載の発明や特開平３−189008号公報記載の
発明があるが、これらの発明は、この出願に係る発明が
対象とするような高応答に適用できるものではない。Further, as another prior art, Japanese Patent Laid-Open No. 49-6
There are inventions described in Japanese Patent No. 4793 and Japanese Patent Application Laid-Open No. 3-189008, but these inventions cannot be applied to the high response that is intended by the invention according to this application.
【００４１】この出願に係る発明は上記課題に鑑みて、
高油注で使用される圧下シリンダであっても高応答の制
御を実現することができる圧延機用油圧圧下装置を提供
することを目的とする。In view of the above problems, the invention of this application is
An object of the present invention is to provide a hydraulic pressure reduction device for a rolling mill, which can realize high response control even for a pressure reduction cylinder used for high oil injection.
【００４２】[0042]
【課題を解決するための手段】上記目的を達成するため
に、請求項１に係る圧延機用油圧圧下装置は、一対の油
圧圧下シリンダを有し、該両圧下シリンダのヘッド側を
３ウエイサーボ弁にて各々所定圧力に保つと共に、該両
圧下シリンダのロッド側を同一且つ所定圧力に保つため
に、各々のロッド側油路を合流させて圧力調整ユニット
に導く油圧回路を有する油圧圧下装置において、上記圧
力調整ユニットと上記ロッド側油路の合流点との間を連
通させる油路に、可変絞り又は固定絞りと開閉切換弁と
を並列に設けたことを特徴とするものである。In order to achieve the above object, a rolling mill hydraulic reduction device according to a first aspect of the present invention has a pair of hydraulic reduction cylinders, and the head side of both the reduction cylinders is a 3-way servo valve. In order to keep the pressure on each rod at the same pressure pressure on both rod sides of the both pressure reduction cylinders, the hydraulic pressure reduction device having a hydraulic circuit that joins the rod-side oil passages and guides them to the pressure adjustment unit, A variable throttle or a fixed throttle and an open / close switching valve are provided in parallel in an oil passage communicating between the pressure adjusting unit and the confluence of the rod-side oil passage.
【００４３】請求項２に係る圧延機用油圧圧下装置は、
一対の油圧圧下シリンダを有し、該両圧下シリンダのヘ
ッド側を３ウエイサーボ弁にて各々所定圧力に保つと共
に、該両圧下シリンダのロッド側を同一且つ所定圧力に
保つために、各々のロッド側油路を合流させて圧力調整
ユニットに導く油圧回路を有する油圧圧下装置におい
て、上記ロッド側油路の合流点と圧下シリンダのロッド
側との間を連通させる油路の各々に、可変絞り又は固定
絞りと開閉切換弁とを並列に設けたことを特徴とするも
のである。A hydraulic rolling down device for a rolling mill according to claim 2 is
A pair of hydraulic pressure reduction cylinders are provided, and the head sides of both pressure reduction cylinders are kept at predetermined pressures by three-way servo valves, and the rod sides of both pressure reduction cylinders are kept at the same and predetermined pressures. In a hydraulic pressure reducing device having a hydraulic circuit that joins oil passages and guides them to a pressure adjusting unit, a variable throttle or a fixed throttle is provided for each of the oil passages that communicate between the confluence of the rod-side oil passages and the rod side of the reduction cylinder. The throttle and the on-off switching valve are provided in parallel.
【００４４】請求項３に係る圧延機用油圧圧下装置は、
一対の油圧圧下シリンダを有し、該両圧下シリンダのヘ
ッド側を３ウエイサーボ弁にて各々所定圧力に保つと共
に、該両圧下シリンダのロッド側を同一且つ所定圧力に
保つために、各々のロッド側油路を合流させて圧力調整
ユニットに導く油圧回路を有する油圧圧下装置におい
て、上記ロッド側油路の合流点と圧下シリンダのロッド
側との間を連通させる油路の各々に開閉切換弁を設けた
ことを特徴とするものである。A hydraulic rolling down device for a rolling mill according to claim 3 is
A pair of hydraulic pressure reduction cylinders are provided, and the head sides of both pressure reduction cylinders are kept at predetermined pressures by three-way servo valves, and the rod sides of both pressure reduction cylinders are kept at the same and predetermined pressures. In a hydraulic pressure reducing device having a hydraulic circuit that joins oil passages and guides them to a pressure adjusting unit, an opening / closing switching valve is provided in each of the oil passages that communicate between the confluence point of the rod side oil passages and the rod side of the reduction cylinder. It is characterized by that.
【００４５】請求項４に係る圧延機用油圧圧下装置は、
上記請求項３の油圧圧下装置において、両開閉切換弁を
両圧下シリンダのロッド側油路出口に直付け又は近接配
置されるマニホールドに組込んだことを特徴とするもの
である。The hydraulic pressure reducing device for a rolling mill according to claim 4
In the hydraulic pressure reducing device of the third aspect of the present invention, both on-off switching valves are incorporated in a manifold that is directly attached to or close to the rod-side oil passage outlets of both pressure reducing cylinders.
【００４６】請求項５に係る圧延機用油圧圧下装置は、
一対の油圧圧下シリンダを有し、該両圧下シリンダのヘ
ッド側を３ウエイサーボ弁にて各々所定圧力に保つと共
に、該両圧下シリンダのロッド側を同一且つ所定圧力に
保つために、各々のロッド側油路を合流させて圧力調整
ユニットに導く油圧回路を有する油圧圧下装置におい
て、上記ロッド側油路の合流点と圧下シリンダのロッド
側との間を連通させる油路の各々に圧力調整ユニットを
設けると共に、該両圧力調整ユニットと前記両圧下シリ
ンダとの間の各油路に可変絞り又は固定絞りと開閉切換
弁とを並列に設けたことを特徴とするものである。A hydraulic rolling down device for a rolling mill according to claim 5 is
A pair of hydraulic pressure reduction cylinders are provided, and the head sides of both pressure reduction cylinders are kept at predetermined pressures by three-way servo valves, and the rod sides of both pressure reduction cylinders are kept at the same and predetermined pressures. In a hydraulic pressure reducing device having a hydraulic circuit that joins oil passages and guides them to a pressure adjusting unit, a pressure adjusting unit is provided in each of the oil passages that communicate between the joining point of the rod side oil passages and the rod side of the reduction cylinder. At the same time, a variable throttle or a fixed throttle and an open / close switching valve are provided in parallel in each oil passage between the both pressure adjusting units and the both pressure reducing cylinders.
【００４７】請求項６に係る圧延機用油圧圧下装置は、
上記請求項５の油圧圧下装置において、両圧力調整ユニ
ットを両圧下シリンダのロッド側油路出口に直付け又は
近接配置されるマニホールドに組込んだことを特徴とす
るものである。A hydraulic rolling down device for a rolling mill according to claim 6 is
In the hydraulic pressure reducing device according to the fifth aspect, both pressure adjusting units are incorporated in a manifold that is directly attached to or adjacent to the rod-side oil passage outlets of both pressure reducing cylinders.
【００４８】[0048]
【作用】請求項１に係る圧延機用油圧圧下装置によれ
ば、圧延中のように高応答を必要とするときのみ開閉切
換弁を閉側に切り換えることにより、圧下シリンダのロ
ッド側に生じた圧力波を可変絞り又は固定絞り回路によ
り減衰させることができるので、圧延に必要な高応答を
得るまで制御ゲインを上げて使用しても圧力波の周期と
圧下シリンダの制御周期との間に大きな差を設けること
ができるためハンチング現象を生じない。また、ハンチ
ング現象にまで至らない外乱重畳現象が残るような場合
には、この現象が無くなるまで、又は実用上問題となら
ない程度まで上記可変絞りを絞り込んで行けば減衰させ
ることができる。According to the hydraulic rolling reduction device for a rolling mill according to the first aspect, the switching valve is switched to the closed side only when high response is required, such as during rolling. Since the pressure wave can be attenuated by the variable throttle or the fixed throttle circuit, even if the control gain is increased and used until the high response required for rolling is obtained, there is a large gap between the pressure wave cycle and the control cycle of the reduction cylinder. Since the difference can be provided, the hunting phenomenon does not occur. Further, in the case where a disturbance superposition phenomenon that does not reach the hunting phenomenon remains, it can be attenuated by eliminating the phenomenon or by narrowing down the variable diaphragm to such an extent that there is no practical problem.
【００４９】請求項２に係る圧延機用油圧圧下装置によ
れば、両圧下シリンダのロッド側が連通する油路の各々
に可変絞り又は固定絞りと開閉切換弁とが並列に存在す
る構成となるので、各々の圧下シリンダに対して、個々
に上記請求項１に係る油圧圧下装置の作用を奏すること
ができるため、両シリンダ特性（両制御系構成機器特
性）の違いによって絞り効果が異なる場合には各々異な
った制御をすることができる。従って、上記油路を介し
ての両油圧シリンダ間の相互干渉を抑えることができ
る。また、開閉切換弁が開時の作用については、請求項
１に係る発明の場合と同様である。In the rolling mill hydraulic pressure reducing device according to the second aspect of the invention, the variable throttle or the fixed throttle and the open / close switching valve are arranged in parallel in each of the oil passages communicating with the rod sides of the both reduction cylinders. Since the action of the hydraulic pressure reducing device according to the above-described claim 1 can be individually exerted on each of the pressure reducing cylinders, when the throttling effect is different due to the difference between both cylinder characteristics (both control system constituent device characteristics). Each can be controlled differently. Therefore, mutual interference between the two hydraulic cylinders via the oil passage can be suppressed. Further, the operation when the open / close switching valve is opened is the same as in the case of the invention according to claim 1.
【００５０】請求項３に係る圧延機用油圧圧下装置によ
れば、圧延中のように高応答を必要とする時のみ油路の
各々に設けた開閉切換弁を閉側に切り換えれば、圧下シ
リンダのロッド側に生じた圧力波は上記開閉切換弁で反
射するが、圧下シリンダと圧力調整ユニットとの間の距
離に比べて圧下シリンダと開閉切換弁との距離は充分に
短くなるため、油路の固有振動数は制御系の応答性より
充分に高くなり、圧延に必要な高応答を得るまで制御ゲ
インを上げて使用してもハンチング現象は生じない。ま
た、開閉切換弁が開時の作用については、請求項１に係
る発明の場合と同様である。According to the hydraulic reduction device for a rolling mill of the third aspect, the rolling reduction valve provided in each of the oil passages is switched to the closed side only when high response is required, such as during rolling. The pressure wave generated on the rod side of the cylinder is reflected by the on-off switching valve, but the distance between the pressure-reducing cylinder and the on-off switching valve is sufficiently shorter than the distance between the pressure-reducing cylinder and the pressure adjustment unit. The natural frequency of the road is sufficiently higher than the response of the control system, and the hunting phenomenon does not occur even if the control gain is increased and used until the high response required for rolling is obtained. Further, the operation when the open / close switching valve is opened is the same as in the case of the invention according to claim 1.
【００５１】請求項４に係る圧延機用油圧圧下装置によ
れば、上記請求項３に係る油圧圧下装置における作用を
奏するとともに、特に開閉切換弁が圧下シリンダ直付け
又は近接配置されるマニホールドに組み込まれるので、
圧下シリンダのロッド側と開閉切換弁との距離が短くな
り、油路の固有振動数を高くして制御系の応答性と比較
して充分に大きくすることができるためハンチング現象
は生じない。According to the hydraulic pressure reducing device for a rolling mill of the fourth aspect, the operation of the hydraulic pressure reducing device of the third aspect is achieved, and in particular, the open / close switching valve is incorporated in the manifold directly attached to the pressure reducing cylinder or arranged in proximity thereto. So,
Since the distance between the rod side of the pressure reduction cylinder and the open / close switching valve is shortened and the natural frequency of the oil passage can be increased to be sufficiently large compared with the response of the control system, the hunting phenomenon does not occur.
【００５２】請求項５に係る圧延機用油圧圧下装置によ
れば、各々の圧下シリンダに対して個々にロッド側圧力
を所定圧力範囲に保つための圧力調整ユニットを持つの
で、ロッド側と圧力調整ユニットとの間の油路の長さが
充分に短くなるため、油路の固有振動数を制御系の応答
性に比較して充分に大きくすることができ、ハンチング
現象を防止することができる。また、両圧下シリンダの
ロッド側が連通する油路間は圧力調整ユニットの挿入に
より常時完全に遮断されるので、両圧下シリンダ間にシ
ーソー現象を生じることはない。更に、各々の油路に可
変絞り又は固定絞りを持つので、請求項２に係る発明と
同様の作用を奏することができる。According to the rolling mill hydraulic pressure reducing device of the present invention, each pressure reducing cylinder has a pressure adjusting unit for maintaining the rod side pressure within a predetermined pressure range. Since the length of the oil passage between the unit and the unit is sufficiently short, the natural frequency of the oil passage can be made sufficiently large compared to the response of the control system, and the hunting phenomenon can be prevented. Further, since the oil passages communicating with the rod sides of both the pressure reducing cylinders are always completely shut off by the insertion of the pressure adjusting unit, the seesaw phenomenon does not occur between the pressure reducing cylinders. Furthermore, since each oil passage has a variable throttle or a fixed throttle, it is possible to achieve the same effect as the invention according to claim 2.
【００５３】請求項６に係る圧延機用油圧圧下装置によ
れば、上記請求項５に係る油圧圧下装置における作用を
奏するとともに、特に圧力調整ユニットおよび可変絞り
又は固定絞りが圧下シリンダ直付け又は近接配置される
マニホールドに組み込まれるので、圧下シリンダのロッ
ド側と圧力調整ユニットおよび可変絞り又は固定絞りと
の距離が短くなり、油路の固有振動数を高くして制御系
の応答性と比較して充分に大きくすることができるため
ハンチング現象は生じない。According to the hydraulic reduction device for a rolling mill of claim 6, the operation of the hydraulic reduction device of claim 5 is achieved, and in particular, the pressure adjusting unit and the variable throttle or the fixed throttle are directly attached to or close to the reduction cylinder. Since it is built into the manifold to be placed, the distance between the rod side of the pressure reduction cylinder and the pressure adjustment unit and variable throttle or fixed throttle becomes shorter, and the natural frequency of the oil passage is increased to compare with the response of the control system. Since it can be made sufficiently large, the hunting phenomenon does not occur.
【００５４】[0054]
【実施例】以下、この出願に係る発明の一実施例を図面
に基づいて説明する。なお、上述した図５および図６に
示す従来の技術と同一の構成には同一符号を付して説明
する。なお、以下の説明でも左右一対に設けられた圧下
シリンダ１０Ａ，１０Ｂの内、図においてＡを付した左
側の構成を例にして説明し、もう一方の構成にはＢを付
して説明は省略する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the invention according to this application will be described below with reference to the drawings. The same components as those of the conventional technique shown in FIGS. 5 and 6 described above will be denoted by the same reference numerals. In the following description as well, among the pair of left and right pressure-reducing cylinders 10A and 10B, the left side configuration with A in the figure will be described as an example, and the other configuration will be denoted with B and description thereof will be omitted. To do.
【００５５】図１は第１実施例に係る油圧圧下装置Ｐ1
の油圧回路を示す回路図であり、図示するように、圧下
シリンダ１０Ａのヘッド側１１ａには上述した従来と同
一のヘッド側油圧回路Ｈが設けられており、このヘッド
側油圧回路Ｈのシリンダ直付マニホールド１２Ａには、
ヘッド側ライン１３ａと供給ライン１３ｂおよび戻りラ
イン１３ｃとを切換える３ウエイ（方向）サーボ弁１４
Ａと、ヘッド側ライン１３ａに設けられたパイロット操
作逆止弁１５Ａとが設けられている。FIG. 1 shows a hydraulic pressure reducing device P 1 according to the first embodiment.
FIG. 7 is a circuit diagram showing a hydraulic circuit of the head side hydraulic circuit H, which is the same as the above-described conventional head side hydraulic circuit H provided on the head side 11a of the reduction cylinder 10A. In the attached manifold 12A,
Three-way (direction) servo valve 14 for switching the head side line 13a, the supply line 13b, and the return line 13c.
A and a pilot operated check valve 15A provided on the head side line 13a are provided.
【００５６】そして、圧下シリンダ１０Ａの変位検出も
上述した従来の構成と同一であり、シリンダ位置検出器
１６Ａにより検出されて、演算アンプ１７Ａにフィード
バックされ、制御信号によりサーボアンプ１８Ａがサー
ボ弁１４Ａを介してシリンダピストン１１Ａを所定の位
置に制御する。すなわち、ヘッド側１１ａの圧力を調節
することにより圧下シリンダ１０Ａのシリンダ位置を制
御している。なお、この制御系は通常の圧延機において
採用されているA.G.C.、いわゆるオートマチック・ゲー
ジ・コントロール装置であれば、他の構成であってもよ
い。The displacement detection of the pressure reduction cylinder 10A is also the same as that of the conventional structure described above, and is detected by the cylinder position detector 16A and fed back to the operational amplifier 17A. The servo amplifier 18A controls the servo valve 14A by the control signal. The cylinder piston 11A is controlled to a predetermined position via the. That is, the cylinder position of the reduction cylinder 10A is controlled by adjusting the pressure on the head side 11a. Note that this control system may have other configurations as long as it is an AGC used in a normal rolling mill, that is, a so-called automatic gauge control device.
【００５７】一方、圧下シリンダ１０Ａのロッド側１１
ｂには油路１９ａが連結されており、もう一方の圧下シ
リンダ１０Ｂに連結された油路１９ｂとの合流点２８が
油路１９を介して圧力調整ユニット２０と連結されてい
る。そして、この油路１９には絞り回路１が設けられて
おり、この実施例では合流点２８に近接して設けられて
いる。なお、この絞り回路１を設ける位置は、この圧力
波の周期と圧下シリンダの制御周期との差が、通常３〜
４倍であれば共振現象を生じないため、ロッド側１１ｂ
の油量，油路１９ａ，１９ｂ，１９の油量等を考慮して
所定位置を設定して設ければよく、ほぼ中間位置で圧力
波波長の腹の位置が好ましい。On the other hand, the rod side 11 of the reduction cylinder 10A
An oil passage 19a is connected to b, and a confluence point 28 with the oil passage 19b connected to the other pressure reduction cylinder 10B is connected to the pressure adjusting unit 20 via the oil passage 19. A throttle circuit 1 is provided in the oil passage 19, and in this embodiment, is provided close to the confluence 28. At the position where the throttle circuit 1 is provided, the difference between the cycle of this pressure wave and the control cycle of the pressure reduction cylinder is usually 3 to.
If it is 4 times, the resonance phenomenon does not occur, so the rod side 11b
It is sufficient to set a predetermined position in consideration of the amount of oil, the amount of oil in the oil passages 19a, 19b, 19 and the like, and it is preferable that the antinode position of the pressure wave wavelength is approximately at the intermediate position.
【００５８】上記絞り回路１は、開閉切換弁２と可変絞
り３とが並列に設けられたもので、開閉切換弁２を切り
換えることにより油路１９を連通させるか、可変絞り３
を介して連通させるかを選択できるように構成されてい
る。そして、上記構成によりロッド側油圧回路Ｒを形成
している。なお、上記可変絞り３に代えて固定絞りを設
けてもよい。The throttling circuit 1 has an open / close switching valve 2 and a variable throttle 3 arranged in parallel. Switching the open / close switching valve 2 allows the oil passage 19 to communicate, or the variable throttle 3 is used.
It is configured so that it is possible to select whether or not to communicate via. The rod-side hydraulic circuit R is formed by the above configuration. A fixed diaphragm may be provided instead of the variable diaphragm 3.
【００５９】上記ヘッド側１１ａに設けられたヘッド側
油圧回路Ｈは、圧延機の左右に設けられた圧下シリンダ
１０Ａ，１０Ｂにそれぞれ設けられており、ロッド側１
１ｂに設けられたロッド側油圧回路Ｒは、圧延機の左右
に設けられた圧下シリンダ１０Ａ，１０Ｂを合流点２８
で合流させた１系統が設けられている。The head side hydraulic circuit H provided on the head side 11a is provided on each of the pressure reducing cylinders 10A and 10B provided on the left and right of the rolling mill, and the rod side 1
The rod side hydraulic circuit R provided in 1b connects the reduction cylinders 10A and 10B provided on the left and right of the rolling mill to the confluence point 28.
There is one system merged in.
【００６０】また、この絞り回路１が設けられた油路１
９に連結された圧力調整ユニット２０は、上述した図６
の回路図に示すように構成されている。すなわち、油路
１９の端部には圧油供給ライン２０ａと圧力調整ライン
２０ｂとを切り換える切換弁２１が設けられ、圧油供給
ライン２０ａは油路２２により油圧源と連結されてお
り、圧力調整ライン２０ｂは油路２３により減圧弁２４
と、この減圧弁２４の設定圧力で圧油を蓄圧するアキュ
ムレータ２５と、このアキュムレータ２５が設定圧力以
上となった時に圧油を逃がすリリーフ弁２６とに連結さ
れている。そして、リリーフ弁２６の設定圧力と減圧弁
２４の設定圧力とによりアキュムレータ２５の蓄圧力を
調節している。なお、この蓄圧力は圧延機の大きさや圧
延材料等により適宜設定すればよい。Further, the oil passage 1 provided with the throttle circuit 1
The pressure adjusting unit 20 connected to the 9 is the same as that shown in FIG.
Is configured as shown in the circuit diagram. That is, a switching valve 21 that switches between the pressure oil supply line 20a and the pressure adjustment line 20b is provided at the end of the oil passage 19, and the pressure oil supply line 20a is connected to the hydraulic pressure source by the oil passage 22 and the pressure adjustment is performed. The line 20b is provided with an oil passage 23 and a pressure reducing valve
An accumulator 25 that stores pressure oil at the set pressure of the pressure reducing valve 24 and a relief valve 26 that releases the pressure oil when the accumulator 25 becomes equal to or higher than the set pressure. Then, the accumulated pressure of the accumulator 25 is adjusted by the set pressure of the relief valve 26 and the set pressure of the pressure reducing valve 24. The accumulated pressure may be appropriately set depending on the size of the rolling mill, rolling material, and the like.
【００６１】以上のように構成された第１実施例の油圧
圧下装置Ｐ1 によれば、圧延時にロッド側油路内の流体
柱の固有振動数を大幅に高くすることができるため、圧
下シリンダの制御周期との差を大きくしてハンチング現
象を生じることなく圧下シリンダ１０Ａ，１０Ｂを高応
答で制御することを可能としている。According to the hydraulic pressure reducing device P 1 of the first embodiment configured as described above, since the natural frequency of the fluid column in the rod side oil passage can be significantly increased during rolling, the pressure reducing cylinder It is possible to control the reduction cylinders 10A and 10B with a high response by increasing the difference from the control cycle of 1) without causing a hunting phenomenon.
【００６２】すなわち、ロッド側１１ｂを、油路１９の
端部に設けられた切換弁２１を圧力調整ライン２０ｂ側
に切り換えることにより、アキュムレータ２５の圧力に
より保持した状態とし、この状態で絞り回路１の開閉切
換弁２を切り換えて可変絞り３を介して連通するように
すれば、この可変絞り３によりロッド側１１ｂにおいて
生じた圧力波を減衰させることができるので、圧下シリ
ンダ１０Ａ，１０Ｂのロッド側１１ｂに生じる圧力波の
周期と圧下シリンダの制御周期との間に大きな差を付け
ることができる。従って、これらの間に共振現象又はそ
れに類する現象を生じることはなく、圧下シリンダ１０
Ａ，１０Ｂを高応答で制御してもハンチング現象を生じ
ることなく圧延することが可能となる。That is, the rod side 11b is held by the pressure of the accumulator 25 by switching the switching valve 21 provided at the end of the oil passage 19 to the pressure adjusting line 20b side, and in this state, the throttle circuit 1 If the open / close switching valve 2 is switched to communicate with the variable throttle 3 through the variable throttle 3, the pressure wave generated on the rod side 11b can be attenuated by the variable throttle 3, so that the rod side of the pressure reducing cylinders 10A, 10B can be reduced. It is possible to make a large difference between the cycle of the pressure wave generated in 11b and the control cycle of the reduction cylinder. Therefore, the resonance phenomenon or a phenomenon similar thereto does not occur between them, and the reduction cylinder 10
Even if A and 10B are controlled with high response, rolling can be performed without causing a hunting phenomenon.
【００６３】また、ハンチング現象にまで至らないが上
述したような外乱重畳現象が残るような場合は、この現
象が無くなるまで、又は実用上問題とならない程度まで
上記可変絞り３を絞り込んで行けばよく、従って圧延機
又は油圧圧下装置の特性が季節変化あるいは経年変化す
るような場合にも可変絞り３を有効に作用させることが
できる。When the hunting phenomenon is not reached but the disturbance superposition phenomenon as described above remains, it is sufficient to narrow down the variable diaphragm 3 until the phenomenon disappears or to such a degree that there is no practical problem. Therefore, the variable throttle 3 can be effectively operated even when the characteristics of the rolling mill or the hydraulic pressure reducing device change seasonally or with time.
【００６４】なお、可変絞り３に代えて固定絞りを設け
る場合には、実績等により必要な絞り量（絞り抵抗）が
既知の場合に使用され、簡単に絞り部分を交換できるよ
うな機構のものを採用すればよい。When a fixed diaphragm is provided instead of the variable diaphragm 3, the fixed diaphragm is used when the necessary diaphragm amount (diaphragm resistance) is known based on actual results and the like, so that the diaphragm portion can be easily replaced. Should be adopted.
【００６５】更に、圧延機では圧延操作以外にロール組
み替え操作、緊急開放等の操作があり、この場合には圧
下シリンダはサーボ弁の能力一杯又はそれに近い流量を
受けて高速で動作（制御）させる必要があるが、上記の
絞り効果が働いた状態では、これが抵抗となって圧下シ
リンダ速度が制限されるため、こうした操作では、一時
開閉切換弁２を開側に切り換え、絞り効果が働かない状
態とすればよい。Further, in the rolling mill, there are operations such as roll changing operation and emergency opening in addition to the rolling operation. In this case, the reduction cylinder is operated (controlled) at a high speed by receiving the flow rate at or near the capacity of the servo valve. Although necessary, when the above throttling effect works, this acts as a resistance and limits the pressure reduction cylinder speed. Therefore, in such an operation, the temporary opening / closing switching valve 2 is switched to the open side, and the throttling effect does not work. And it is sufficient.
【００６６】次に、第２実施例を図２に示す油圧圧下装
置Ｐ2 の油圧回路図に基づいて説明する。この第２実施
例は、上記第１実施例における絞り回路１を油路１９
ａ，１９ｂに各々設けた実施例である。なお、この第２
実施例では、上述した第１実施例におけるヘッド側油圧
回路Ｈは省略してロッド側油圧回路Ｒのみを説明し、同
一の構成には同一符号を付して説明は省略する。Next, a second embodiment will be described with reference to the hydraulic circuit diagram of the hydraulic pressure reducing device P 2 shown in FIG. In the second embodiment, the throttle circuit 1 of the first embodiment is replaced with an oil passage 19.
This is an example provided in each of a and 19b. In addition, this second
In the embodiment, the head-side hydraulic circuit H in the above-described first embodiment is omitted, and only the rod-side hydraulic circuit R is described. The same components are designated by the same reference numerals and description thereof is omitted.
【００６７】図示するように、圧下シリンダ１０Ａ，１
０Ｂのロッド側１１ｂに連通した油路１９ａ，１９ｂに
は、上述した第１実施例と同じ開閉切換弁２Ａ，２Ｂと
可変絞り３Ａ，３Ｂとを有する絞り回路１Ａ，１Ｂが各
々設けられており、この第２実施例の油圧圧下装置Ｐ2
によれば、以下のようにしてハンチング現象を生じるこ
となく、また、シーソー現象も未然に抑えて圧下シリン
ダを高応答で制御することを可能としている。As shown, the reduction cylinders 10A, 1
The oil passages 19a and 19b communicating with the rod side 11b of 0B are respectively provided with throttle circuits 1A and 1B having the same switching valves 2A and 2B and variable throttles 3A and 3B as in the above-described first embodiment. The hydraulic pressure reducing device P 2 of the second embodiment
According to this, it is possible to control the reduction cylinder with high response without causing the hunting phenomenon and suppressing the seesaw phenomenon in the following manner.
【００６８】すなわち、絞り回路１Ａ，１Ｂの開閉切換
弁２Ａ，２Ｂを切り換えることにより、上述した第１実
施例と同様に可変絞り３Ａ，３Ｂでロッド側１１ｂに生
じた圧力波を減衰させてハンチング現象を生じることな
く高応答で制御することが可能となるとともに、この第
２実施例では、油路１９ａ，１９ｂの各々において絞り
率を変更することにより、両油路１９ａ，１９ｂにおけ
る流量を変化させて圧下シリンダ１０Ａ，１０Ｂ間の直
接的な干渉を縁切りしてシーソー現象を未然に抑えるこ
とができる。That is, by switching the open / close switching valves 2A, 2B of the throttle circuits 1A, 1B, the pressure wave generated on the rod side 11b is attenuated by the variable throttles 3A, 3B as in the first embodiment described above, and hunting is performed. It is possible to control with high response without causing a phenomenon, and in the second embodiment, the flow rate in both oil passages 19a and 19b is changed by changing the throttle ratio in each of the oil passages 19a and 19b. As a result, the seesaw phenomenon can be suppressed in advance by cutting off the direct interference between the reduction cylinders 10A and 10B.
【００６９】なお、この第２実施例の場合、絞り回路１
を上述した第１実施例よりもロッド側１１ｂに近接させ
ることができるため、例えば、絞り回路１Ａ，１Ｂをマ
ニホールド又はバルブブロックに組込めば、特別な設置
スペースを要することなく圧下シリンダ１０Ａのロッド
側１１ｂに近接して設けることが可能であり、油路内の
圧力波周期と圧下シリンダの制御周期との差を３〜４倍
以上に大きくすることが容易に可能となる。In the case of the second embodiment, the diaphragm circuit 1
Can be made closer to the rod side 11b than in the above-described first embodiment. Therefore, for example, if the throttle circuits 1A and 1B are incorporated in a manifold or a valve block, the rod of the reduction cylinder 10A can be installed without requiring a special installation space. It can be provided close to the side 11b, and it is possible to easily increase the difference between the pressure wave period in the oil passage and the control period of the pressure reduction cylinder by 3 to 4 times or more.
【００７０】次に、第３実施例を図３に示す油圧圧下装
置Ｐ3 の油圧回路図に基づいて説明する。この第３実施
例は、圧下シリンダ１０Ａ，１０Ｂのロッド側１１ｂに
連通した油路１９ａ，１９ｂに開閉切換弁４Ａ，４Ｂを
各々設けた実施例である。なお、この第３実施例でも、
上述した第１実施例におけるヘッド側油圧回路Ｈは省略
してロッド側油圧回路Ｒのみを説明し、同一の構成には
同一符号を付して説明は省略する。Next, a third embodiment will be described with reference to the hydraulic circuit diagram of the hydraulic pressure reducing device P 3 shown in FIG. The third embodiment is an embodiment in which opening / closing switching valves 4A, 4B are provided in oil passages 19a, 19b communicating with the rod side 11b of the pressure reduction cylinders 10A, 10B, respectively. Incidentally, in this third embodiment,
The head side hydraulic circuit H in the above-described first embodiment will be omitted, and only the rod side hydraulic circuit R will be described. The same components will be denoted by the same reference numerals and description thereof will be omitted.
【００７１】図示するように、圧下シリンダ１０Ａ，１
０Ｂのロッド側１１ｂに連通した油路１９ａ，１９ｂの
各々に開閉切換弁４Ａ，４Ｂが設けられており、この油
路１９ａ，１９ｂに開閉切換弁４Ａ，４Ｂを設けること
によりロッド側１１ｂとの距離を長くて２〜３メートル
にすることが可能となる。そして、この第３実施例の油
圧圧下装置Ｐ3 によれば、以下のようにしてハンチング
現象を生じることなく、また、シーソー現象も未然に抑
えて圧下シリンダを高応答で制御することが可能とな
る。As shown, the reduction cylinders 10A, 1
Open / close switching valves 4A, 4B are provided respectively in oil passages 19a, 19b communicating with the rod side 11b of 0B, and by providing open / close switching valves 4A, 4B in these oil passages 19a, 19b, It is possible to increase the distance to 2-3 meters. Further, according to the hydraulic pressure reducing device P 3 of the third embodiment, it is possible to control the pressure reducing cylinder with high response without causing the hunting phenomenon and suppressing the seesaw phenomenon in the following manner. Become.
【００７２】すなわち、油路１９ａ，１９ｂに設けられ
た開閉切換弁４Ａ，４Ｂを閉鎖させることにより、ロッ
ド側１１ｂに近接した位置で油路１９ａ，１９ｂを閉鎖
させるため、ロッド側１１ｂに生じた圧力波は近接した
切換弁４Ａ，４Ｂで反射するので圧力波の周期は高くな
り、圧下シリンダ１０Ａ，１０Ｂの制御周期との間に大
きな差が生じて共振現象、すなわちハンチング現象を生
じることなく高応答の制御が可能となる。また、この第
３実施例でも、開閉切換弁４Ａ，４Ｂにより油路１９
ａ，１９ｂ間を完全に遮断することができるため、両圧
下シリンダ１０Ａ，１０Ｂ間のシーソー現象を未然に抑
えることができる。That is, by closing the open / close switching valves 4A, 4B provided in the oil passages 19a, 19b, the oil passages 19a, 19b are closed at a position close to the rod side 11b. Since the pressure wave is reflected by the switching valves 4A and 4B which are close to each other, the cycle of the pressure wave becomes high, and a large difference occurs between the pressure wave and the control cycle of the pressure reduction cylinders 10A and 10B, so that the resonance phenomenon, that is, the hunting phenomenon does not occur. It is possible to control the response. Also in this third embodiment, the oil passage 19 is opened by the open / close switching valves 4A and 4B.
Since it is possible to completely shut off between a and 19b, the seesaw phenomenon between the both pressure reducing cylinders 10A and 10B can be suppressed in advance.
【００７３】なお、この第３実施例において、開閉切換
弁４Ａ，４Ｂを例えばマニホールド又はバルブブロック
に組込めば、特別な設置スペースを要することなく圧下
シリンダ１０Ａのロッド側１１ｂに近接して設けること
が可能となり、この場合、ロッド側１１ｂと開閉切換弁
４との距離を２〜３メートルにすることも可能となるの
で、前述の計算例に従えば油路の固有振動数は１００Ｈ
ｚ以上となり、制御系の応答性と比較して充分に大きく
することができる。In the third embodiment, if the on-off switching valves 4A and 4B are incorporated in, for example, a manifold or a valve block, they should be provided close to the rod side 11b of the pressure reduction cylinder 10A without requiring a special installation space. In this case, the distance between the rod side 11b and the open / close switching valve 4 can be set to 2 to 3 meters. Therefore, according to the above calculation example, the natural frequency of the oil passage is 100H.
It becomes z or more and can be made sufficiently large as compared with the response of the control system.
【００７４】次に、第４実施例を図４に示す油圧圧下装
置Ｐ4 の油圧回路図に基づいて説明する。この第４実施
例は、圧下シリンダ１０Ａ，１０Ｂのロッド側１１ｂに
連通した油路１９ａ，１９ｂに上述した圧力調整ユニッ
ト２０と絞り回路１とを各々設けた実施例である。な
お、この第４実施例における絞り回路１は上述した第１
実施例における可変絞り３に代えて固定絞り５を設けて
いる。また、この第４実施例でも、上述した第１実施例
におけるヘッド側油圧回路Ｈは省略してロッド側油圧回
路Ｒのみを説明し、同一の構成には同一符号を付して説
明は省略する。Next, a fourth embodiment will be described with reference to the hydraulic circuit diagram of the hydraulic pressure reducing device P 4 shown in FIG. The fourth embodiment is an embodiment in which the above-described pressure adjusting unit 20 and the throttle circuit 1 are provided in the oil passages 19a and 19b communicating with the rod side 11b of the reduction cylinders 10A and 10B, respectively. The diaphragm circuit 1 in the fourth embodiment is the same as the first embodiment described above.
A fixed diaphragm 5 is provided instead of the variable diaphragm 3 in the embodiment. Also in this fourth embodiment, the head side hydraulic circuit H in the above-described first embodiment is omitted and only the rod side hydraulic circuit R is described, and the same components are denoted by the same reference numerals and the description thereof is omitted. .
【００７５】図示するように、圧下シリンダ１０Ａ，１
０Ｂのロッド側１１ｂに連通した油路１９ａ，１９ｂの
各々に絞り回路１Ａ，１Ｂと圧力調整ユニット２０Ａ，
２０Ｂとが設けられており、この第４実施例の油圧圧下
装置Ｐ4 によれば、以下のようにしてハンチング現象を
生じることなく、また、シーソー現象も未然に抑えて圧
下シリンダを高応答で制御することが可能となる。As shown, the reduction cylinders 10A, 1
Each of the oil passages 19a and 19b communicating with the rod side 11b of 0B has a throttle circuit 1A, 1B and a pressure adjusting unit 20A,
20B is provided, and according to the hydraulic pressure reducing device P 4 of the fourth embodiment, the hunting phenomenon does not occur and the seesaw phenomenon is also suppressed in the following manner, and the pressure reducing cylinder has a high response. It becomes possible to control.
【００７６】すなわち、両絞り回路１Ａ，１Ｂに設けら
れた開閉切換弁２Ａ，２Ｂを連通させた状態では、ロッ
ド側１１ｂに生じた圧力波が油路１９ａ，１９ｂの各々
に設けられた圧力調整ユニット２０Ａ，２０Ｂへと伝わ
ってアキュムレータ２５で反射するが、この圧力調整ユ
ニット２０Ａ，２０Ｂをロッド側１１ｂに近接した油路
１９ａ，１９ｂに設けているため、圧力波の周期は高く
なり、圧下シリンダ１０Ａ，１０Ｂの制御周期との間に
大きな差が生じて共振現象、すなわちハンチング現象を
生じることなく高応答の制御が可能となる。That is, in a state in which the open / close switching valves 2A, 2B provided in both throttle circuits 1A, 1B are in communication with each other, the pressure wave generated on the rod side 11b adjusts the pressure provided in each of the oil passages 19a, 19b. Although transmitted to the units 20A and 20B and reflected by the accumulator 25, since the pressure adjusting units 20A and 20B are provided in the oil passages 19a and 19b close to the rod side 11b, the cycle of the pressure wave becomes high and the pressure reducing cylinder A large difference occurs between the control cycles of 10A and 10B, and a high response control is possible without causing a resonance phenomenon, that is, a hunting phenomenon.
【００７７】また、開閉切換弁２Ａ，２Ｂを閉鎖させれ
ば、固定絞り５Ａ，５Ｂで圧力波を減衰させて圧力調整
ユニット２０Ａ，２０Ｂへと伝えることができ、更に、
圧力調整ユニット２０Ａ，２０Ｂの止め弁２５ｂを閉鎖
させれば油路１９ａ，１９ｂ間を完全に遮断することが
できるため、ロッド側１１ｂに生じる圧力波に応じてこ
れらを適宜使い分け、又は組合せて使うことにより、圧
力波の周期と制御周期との間に大きな差を生じさせるこ
とができ、共振現象、すなわちハンチング現象を生じる
ことなく高応答の制御をすることが可能となる。しか
も、油路１９ａ，１９ｂ間を完全に遮断することができ
るため、両圧下シリンダ１０Ａ，１０Ｂ間のシーソー現
象を未然に抑えることもできる。なお、油路１９は図示
しない一定圧力源に連結されている。Further, by closing the switching valves 2A and 2B, the pressure waves can be attenuated by the fixed throttles 5A and 5B and transmitted to the pressure adjusting units 20A and 20B.
Since the oil passages 19a and 19b can be completely shut off by closing the stop valves 25b of the pressure adjusting units 20A and 20B, these are appropriately used or combined depending on the pressure wave generated on the rod side 11b. As a result, a large difference can be generated between the pressure wave cycle and the control cycle, and high-response control can be performed without causing a resonance phenomenon, that is, a hunting phenomenon. Moreover, since the oil passages 19a and 19b can be completely shut off, the seesaw phenomenon between the both pressure reducing cylinders 10A and 10B can be suppressed in advance. The oil passage 19 is connected to a constant pressure source (not shown).
【００７８】更に、上記圧力調整ユニット２０Ａ，２０
Ｂを圧延機のマニホールド又はバルブブロックに組込め
ば、圧下シリンダ１０Ａ，１０Ｂのロッド側１１ｂと圧
力調整ユニット２０Ａ，２０Ｂとの距離、つまりアキュ
ムレータ２５との距離を近接させることができるため、
圧力波の周期と圧下シリンダの制御周期との差を３〜４
倍以上に高くしてハンチング現象を防止することができ
る。その上、この圧力調整ユニット２０Ａ，２０Ｂを設
けるためのスペースも容易に確保することができる。Further, the pressure adjusting units 20A, 20
If B is incorporated in the manifold or valve block of the rolling mill, the distance between the rod side 11b of the reduction cylinders 10A, 10B and the pressure adjustment units 20A, 20B, that is, the distance between the accumulator 25, can be reduced.
The difference between the pressure wave cycle and the control cycle of the pressure reduction cylinder is 3 to 4
The hunting phenomenon can be prevented by increasing the height more than twice. In addition, a space for installing the pressure adjusting units 20A and 20B can be easily secured.
【００７９】ところで、上記圧力調整ユニット２０Ａ，
２０Ｂに設けられたアキュムレータ２５は上述したよう
に定圧源として機能する開端となるため、上記したよう
に止め弁２５ｂを閉鎖して閉端として使用する場合があ
る。従って、上記圧力調整ユニット２０Ａ，２０Ｂには
必ずしもアキュムレータ２５を設ける必要はない。つま
り、この圧力調整ユニット２０を切換弁２１と減圧弁２
４とリリーフ弁２６とから構成してもよい。By the way, the pressure adjusting unit 20A,
Since the accumulator 25 provided in 20B has an open end that functions as a constant pressure source as described above, the stop valve 25b may be closed and used as a closed end as described above. Therefore, it is not always necessary to provide the accumulator 25 in the pressure adjusting units 20A and 20B. That is, the pressure adjusting unit 20 is connected to the switching valve 21 and the pressure reducing valve 2.
4 and the relief valve 26.
【００８０】この場合にも、ロッド側１１ｂに生じた圧
力波を油路１９ａ，１９ｂの各々に設けられた圧力調整
ユニット２０Ａ，２０Ｂで反射させて圧力波の周期を高
くすることが可能となるため、圧下シリンダ１０Ａ，１
０Ｂの制御周期との間に大きな差が生じてハンチング現
象を生じることなく高応答で制御することが可能とな
る。Also in this case, the pressure wave generated on the rod side 11b can be reflected by the pressure adjusting units 20A and 20B provided in the oil passages 19a and 19b, respectively, to increase the period of the pressure wave. Therefore, the reduction cylinders 10A, 1
It is possible to perform control with high response without causing a hunting phenomenon due to a large difference from the control cycle of 0B.
【００８１】なお、上述した第１〜第４実施例の構成を
組合せて使用することも容易に可能であり、この場合に
は、上述した第１〜第４実施例におけるいずれかの作用
効果を奏することができる。It is also possible to easily combine and use the configurations of the above-described first to fourth embodiments. In this case, any one of the effects of the above-described first to fourth embodiments can be obtained. Can play.
【００８２】以上説明したように、この出願に係る油圧
圧下装置によれば、３ウエイ型サーボ弁の出力ポートに
通じる圧下シリンダのヘッド側油柱が、９０ミリメート
ルを越えるような高油柱で、且つ、２０Ｈｚを越えるよ
うな高応答で制御しても、シリンダロッド側油路内の流
体柱の固有振動数又はそれに近い周波数でのハンチング
現象を生じない圧延機用油圧圧下装置が可能となる。As described above, according to the hydraulic pressure reduction device of the present application, the oil column on the head side of the pressure reduction cylinder leading to the output port of the 3-way type servo valve is a high oil column exceeding 90 mm. Moreover, even if the control is performed with a high response exceeding 20 Hz, it is possible to provide a rolling mill hydraulic pressure reduction device that does not cause a hunting phenomenon at the natural frequency of the fluid column in the cylinder rod side oil passage or at a frequency close thereto.
【００８３】[0083]
【発明の効果】この出願に係る発明は、以上説明したよ
うに構成しているので、以下に記載するような効果を奏
する。Since the invention according to this application is configured as described above, it has the following effects.
【００８４】請求項１に係る圧延機用油圧圧下装置によ
れば、圧延中のように高応答を必要とするときのみ開閉
切換弁を閉側に切り換えることにより、圧下シリンダの
ロッド側に生じた圧力波を可変絞り又は固定絞り回路に
より減衰させることができるので、圧延に必要な高応答
を得るまで制御ゲインを上げて使用しても圧力波の周期
と圧下シリンダの制御周期との間に大きな差を設けるこ
とができるためハンチング現象を生じることはなく、ま
た、ハンチング現象にまで至らない外乱重畳現象が残る
ような場合には、この現象が無くなるまで、又は実用上
問題とならない程度まで上記可変絞りを絞り込んで行け
ば減衰させることができるため、高油注であっても高応
答の制御により、精度の高い圧延を行うことが可能とな
る。According to the rolling mill hydraulic pressure reduction device of the first aspect, the switching valve is switched to the closed side only when high response is required, such as during rolling. Since the pressure wave can be attenuated by the variable throttle or the fixed throttle circuit, even if the control gain is increased and used until the high response required for rolling is obtained, there is a large gap between the pressure wave cycle and the control cycle of the reduction cylinder. A hunting phenomenon does not occur because a difference can be provided, and when a disturbance superposition phenomenon that does not reach the hunting phenomenon remains, the above variable can be used until this phenomenon disappears or it does not pose a practical problem. Since it is possible to reduce the damping by narrowing the throttle, it is possible to perform highly accurate rolling even with high oil pouring by controlling the response.
【００８５】請求項２に係る圧延機用油圧圧下装置によ
れば、両圧下シリンダのロッド側が連通する油路の各々
に可変絞り又は固定絞りと開閉切換弁とが並列に存在す
る構成となるので、各々の圧下シリンダに対して、個々
に上記請求項１に係る油圧圧下装置の効果を奏すること
ができると共に、両シリンダ特性の違いによって絞り効
果が異なる場合には各々異なった制御をすることがで
き、上記油路を介しての両油圧シリンダ間の相互干渉を
抑えてシーソー現象を防止した高精度な圧延が可能とな
る。According to the rolling mill hydraulic pressure reducing device of the present invention, the variable throttle or the fixed throttle and the open / close switching valve are arranged in parallel in each of the oil passages communicating with the rod sides of the both rolling cylinders. The effect of the hydraulic pressure reducing device according to the above-mentioned claim 1 can be individually exerted on each of the pressure reducing cylinders, and different control can be performed when the throttling effect is different due to the difference in both cylinder characteristics. Therefore, it is possible to suppress the mutual interference between the two hydraulic cylinders via the oil passage and prevent the seesaw phenomenon, thereby performing high-precision rolling.
【００８６】請求項３に係る圧延機用油圧圧下装置によ
れば、圧延中のように高応答を必要とする時のみ油路の
各々に設けた開閉切換弁を閉側に切り換えれば、圧下シ
リンダのロッド側に生じた圧力波は充分に近い距離に設
けられた上記開閉切換弁で反射するため、油路の固有振
動数は制御系の応答性より充分に高くなり、圧延に必要
な高応答を得るまで制御ゲインを上げて使用してもハン
チング現象を生じることなく、高油注であっても高応答
の制御により、精度の高い圧延を行うことが可能とな
る。According to the hydraulic pressure reducing device for a rolling mill of the third aspect, when the open / close switching valve provided in each oil passage is switched to the closed side only when high response is required such as during rolling, the rolling reduction is performed. Since the pressure wave generated on the rod side of the cylinder is reflected by the on-off switching valve provided at a sufficiently short distance, the natural frequency of the oil passage is sufficiently higher than the response of the control system, and the high frequency required for rolling is high. Even if the control gain is increased and used until a response is obtained, the hunting phenomenon does not occur, and even in the case of high oil pouring, highly responsive control enables highly accurate rolling.
【００８７】請求項４に係る圧延機用油圧圧下装置によ
れば、上記請求項３に係る油圧圧下装置における効果を
奏するとともに、特に開閉切換弁が圧下シリンダ直付け
又は近接配置されるマニホールドに組込まれているの
で、圧下シリンダのロッド側と開閉切換弁との距離が短
くなり、油路の固有振動数を高くして制御系の応答性と
比較して充分に大きくすることができるため、ハンチン
グ現象は生じることなく、高油注であっても高応答の制
御により、精度の高い圧延を行うことが可能となる。According to the hydraulic pressure reducing device for a rolling mill of the fourth aspect, the hydraulic pressure reducing device of the third aspect exhibits the effect, and in particular, the open / close switching valve is incorporated in the manifold directly attached to the pressure reducing cylinder or arranged in the vicinity thereof. Since the distance between the rod side of the pressure reduction cylinder and the open / close switching valve is shortened and the natural frequency of the oil passage can be increased to be sufficiently large compared to the response of the control system, hunting is possible. Phenomena do not occur, and even with high oil pouring, high-response control enables highly accurate rolling.
【００８８】請求項５に係る圧延機用油圧圧下装置によ
れば、各々の圧下シリンダの油路に対して各々ロッド側
圧力を所定圧力範囲に保つための圧力調整ユニットを持
つので、ロッド側と圧力調整ユニットとの間の油路の長
さが充分に短くなるため、油路の固有振動数を制御系の
応答性に比較して充分に大きくし、高油注であっても高
応答の制御により、精度の高い圧延を行うことが可能と
なる。また、両圧下シリンダのロッド側が連通する油路
間は圧力調整ユニットの挿入により常時完全に遮断され
るので、両圧下シリンダ間に生じるシーソー現象を防止
することができる。According to the hydraulic pressure reducing device for a rolling mill of the fifth aspect, since there is a pressure adjusting unit for keeping the rod side pressure within a predetermined pressure range with respect to the oil passages of the respective reduction cylinders, Since the length of the oil passage between the pressure adjustment unit and the pressure adjustment unit is sufficiently short, the natural frequency of the oil passage is made sufficiently large compared to the response of the control system, and high response is achieved even with high oil injection. The control enables highly accurate rolling. Further, since the oil passages communicating with the rod sides of both the pressure reducing cylinders are always completely shut off by inserting the pressure adjusting unit, it is possible to prevent the seesaw phenomenon between the both pressure reducing cylinders.
【００８９】請求項６に係る圧延機用油圧圧下装置によ
れば、上記請求項５に係る油圧圧下装置における効果を
奏するとともに、特に圧力調整ユニットおよび可変絞り
又は固定絞りが圧下シリンダ直付け又は近接配置される
マニホールドに組み込まれているので、圧下シリンダの
ロッド側と圧力調整ユニットおよび可変絞り又は固定絞
りとの距離を短くして、油路の固有振動数を制御系の応
答性と比較して充分に大きくし、高油注であっても高応
答の制御により、精度の高い圧延を行うことが可能とな
る。According to the hydraulic reduction device for a rolling mill of claim 6, the effect of the hydraulic reduction device of claim 5 is obtained, and in particular, the pressure adjustment unit and the variable throttle or the fixed throttle are directly attached to or close to the reduction cylinder. Since it is built into the manifold to be placed, the distance between the rod side of the pressure reduction cylinder and the pressure adjustment unit and variable throttle or fixed throttle is shortened to compare the natural frequency of the oil passage with the response of the control system. It is possible to perform rolling with high accuracy by making the size sufficiently large and controlling high response even with high oil injection.
【図１】この出願に係る圧延機用油圧圧下装置の第１実
施例を示す油圧回路図である。FIG. 1 is a hydraulic circuit diagram showing a first embodiment of a hydraulic pressure reducing device for a rolling mill according to the present application.
【図２】この出願に係る圧延機用油圧圧下装置の第２実
施例を示す油圧回路図である。FIG. 2 is a hydraulic circuit diagram showing a second embodiment of the hydraulic reduction device for a rolling mill according to this application.
【図３】この出願に係る圧延機用油圧圧下装置の第３実
施例を示す油圧回路図である。FIG. 3 is a hydraulic circuit diagram showing a third embodiment of the hydraulic pressure reducing device for a rolling mill according to this application.
【図４】この出願に係る圧延機用油圧圧下装置の第４実
施例を示す油圧回路図である。FIG. 4 is a hydraulic circuit diagram showing a fourth embodiment of the hydraulic pressure reducing device for a rolling mill according to the present application.
【図５】従来の油圧圧下装置における油圧回路を示す回
路図である。FIG. 5 is a circuit diagram showing a hydraulic circuit in a conventional hydraulic pressure reducing device.
【図６】従来の油圧圧下装置における圧力調整ユニット
を示す油圧回路図である。FIG. 6 is a hydraulic circuit diagram showing a pressure adjusting unit in a conventional hydraulic pressure reducing device.
【図７】従来の油圧圧下装置において生じる外乱重畳現
象の実測オシロデータ一例を示す線図である。FIG. 7 is a diagram showing an example of actually measured oscilloscope data of a disturbance superposition phenomenon that occurs in a conventional hydraulic pressure reduction device.
１，１Ａ，１Ｂ…絞り回路 ２，２Ａ，２Ｂ…開閉切換弁 ３，３Ａ，３Ｂ…可変絞り ４Ａ，４Ｂ…開閉切換弁 ５Ａ，５Ｂ…固定絞り １０Ａ，１０Ｂ…圧下シリンダ １１ａ…ヘッド側 １１ｂ…ロッド側 １２Ａ，１２Ｂ…マニホールド １３…油圧回路 １３ａ…ヘッド側ライン １３ｂ…供給ライン １３ｃ…戻りライン １４Ａ，１４Ｂ…サーボ弁 １５Ａ，１５Ｂ…パイロット操作逆止弁 １６Ａ，１６Ｂ…シリンダ位置検出器 １７Ａ，１７Ｂ…演算アンプ １８Ａ，１８Ｂ…サーボ弁用増幅アンプ １９…油路 １９ａ，１９ｂ…油路 ２０，２０Ａ，２０Ｂ…圧力調整ユニット ２０ａ…圧油供給ライン ２０ｂ…圧力調整ライン ２１…切換弁 ２２，２３…油路 ２４…減圧弁 ２５…アキュムレータ ２６…リリーフ弁 Ｐ1,Ｐ2,Ｐ3,Ｐ4 …油圧圧下装置 Ｈ…ヘッド側油圧回路 Ｒ…ロッド側油圧回路1, 1A, 1B ... Throttle circuit 2, 2A, 2B ... Open / close switching valve 3, 3A, 3B ... Variable throttle 4A, 4B ... Open / close switching valve 5A, 5B ... Fixed throttle 10A, 10B ... Reduction cylinder 11a ... Head side 11b ... Rod side 12A, 12B ... Manifold 13 ... Hydraulic circuit 13a ... Head side line 13b ... Supply line 13c ... Return line 14A, 14B ... Servo valve 15A, 15B ... Pilot operated check valve 16A, 16B ... Cylinder position detector 17A, 17B Computational amplifiers 18A, 18B ... Amplification amplifiers for servo valves 19 ... Oil passages 19a, 19b ... Oil passages 20, 20A, 20B ... Pressure adjusting unit 20a ... Pressure oil supply line 20b ... Pressure adjusting line 21 ... Switching valve 22, 23 ... Oil passage 24 ... Pressure reducing valve 25 ... Accumulator 26 ... Relief valve P 1 , P 2 , P 3 , P 4 ... Hydraulic pressure reduction Device H ... Head side hydraulic circuit R ... Rod side hydraulic circuit
フロントページの続き (72)発明者 谷口 武史 和歌山県和歌山市湊1850番地 住友金属工 業株式会社和歌山製鉄所内 (72)発明者 高橋 昌範 兵庫県神戸市中央区東川崎町３丁目１番１ 号 川崎重工業株式会社神戸工場内 (72)発明者 曽我 一利 兵庫県神戸市中央区東川崎町３丁目１番１ 号 川崎重工業株式会社神戸工場内Front page continued (72) Inventor Takeshi Taniguchi 1850 Minato, Wakayama, Wakayama Sumitomo Metal Industries, Ltd. Wakayama Works (72) Inventor Masanori Takahashi 3-1-1 Higashikawasaki-cho, Chuo-ku, Hyogo Prefecture Kawasaki Heavy Industries Inside the Kobe Factory (72) Inventor Kazutoshi Soga 3-1-1 Higashikawasaki-cho, Chuo-ku, Kobe City, Hyogo Prefecture Inside Kawasaki Heavy Industries, Ltd. Kobe Factory
Claims (6)
下シリンダのヘッド側を３ウエイサーボ弁にて各々所定
圧力に保つと共に、該両圧下シリンダのロッド側を同一
且つ所定圧力に保つために、各々のロッド側油路を合流
させて圧力調整ユニットに導く油圧回路を有する油圧圧
下装置において、 上記圧力調整ユニットと上記ロッド側油路の合流点との
間を連通させる油路に、可変絞り又は固定絞りと開閉切
換弁とを並列に設けたことを特徴とする圧延機用油圧圧
下装置。1. A pair of hydraulic pressure-reducing cylinders are provided, in order to maintain the head side of both pressure-reducing cylinders at a predetermined pressure by a 3-way servo valve, and to maintain the rod sides of both pressure-reduction cylinders at the same pressure pressure. In a hydraulic pressure reducing device having a hydraulic circuit that joins the rod-side oil passages and guides them to the pressure adjusting unit, a variable throttle is provided in the oil passage that communicates between the pressure adjusting unit and the confluence of the rod-side oil passages. Alternatively, a hydraulic reduction device for a rolling mill, wherein a fixed throttle and an open / close switching valve are provided in parallel.
下シリンダのヘッド側を３ウエイサーボ弁にて各々所定
圧力に保つと共に、該両圧下シリンダのロッド側を同一
且つ所定圧力に保つために、各々のロッド側油路を合流
させて圧力調整ユニットに導く油圧回路を有する油圧圧
下装置において、 上記ロッド側油路の合流点と圧下シリンダのロッド側と
の間を連通させる油路の各々に、可変絞り又は固定絞り
と開閉切換弁とを並列に設けたことを特徴とする圧延機
用油圧圧下装置。2. A pair of hydraulic pressure reduction cylinders are provided, wherein the head sides of both pressure reduction cylinders are kept at a predetermined pressure by a 3-way servo valve, and the rod sides of both pressure reduction cylinders are kept at the same and predetermined pressure. , In a hydraulic pressure reducing device having a hydraulic circuit that joins the rod-side oil passages and guides them to the pressure adjustment unit, in each of the oil passages that communicate between the confluence point of the rod-side oil passages and the rod side of the reduction cylinder. , A variable throttle or a fixed throttle and an open / close switching valve provided in parallel with each other.
下シリンダのヘッド側を３ウエイサーボ弁にて各々所定
圧力に保つと共に、該両圧下シリンダのロッド側を同一
且つ所定圧力に保つために、各々のロッド側油路を合流
させて圧力調整ユニットに導く油圧回路を有する油圧圧
下装置において、 上記ロッド側油路の合流点と圧下シリンダのロッド側と
の間を連通させる油路の各々に、開閉切換弁を設けたこ
とを特徴とする圧延機用油圧圧下装置。3. A pair of hydraulic pressure reduction cylinders are provided, wherein the head sides of both pressure reduction cylinders are kept at predetermined pressures by three-way servo valves, and the rod sides of both pressure reduction cylinders are kept at the same pressure pressure. , A hydraulic pressure reducing device having a hydraulic circuit that joins the rod-side oil passages and guides them to the pressure adjustment unit, in each of the oil passages that communicate between the confluence point of the rod-side oil passages and the rod side of the reduction cylinder. A hydraulic pressure reducing device for a rolling mill, which is provided with an open / close switching valve.
側油路出口に直付け又は近接配置されるマニホールドに
組込んだことを特徴とする請求項３記載の圧延機用油圧
圧下装置。4. The hydraulic pressure reducing device for a rolling mill according to claim 3, wherein the on-off switching valve is incorporated in a manifold which is directly attached to or close to the rod-side oil passage outlets of both reduction cylinders.
下シリンダのヘッド側を３ウエイサーボ弁にて各々所定
圧力に保つと共に、該両圧下シリンダのロッド側を同一
且つ所定圧力に保つために、各々のロッド側油路を合流
させて圧力調整ユニットに導く油圧回路を有する油圧圧
下装置において、 上記ロッド側油路の合流点と圧下シリンダのロッド側と
の間を連通させる油路の各々に圧力調整ユニットを設け
ると共に、該両圧力調整ユニットと前記両圧下シリンダ
との間の各油路に可変絞り又は固定絞りと開閉切換弁と
を並列に設けたことを特徴とする圧延機用油圧圧下装
置。5. A pair of hydraulic pressure reduction cylinders are provided, wherein the head sides of both pressure reduction cylinders are kept at a predetermined pressure by a three-way servo valve, and the rod sides of both pressure reduction cylinders are kept at the same and predetermined pressure. , In a hydraulic pressure reducing device having a hydraulic circuit that joins the rod-side oil passages and guides them to the pressure adjustment unit, in each of the oil passages that communicate between the confluence point of the rod-side oil passages and the rod side of the reduction cylinder. A hydraulic pressure reduction for a rolling mill, characterized in that a pressure adjusting unit is provided, and a variable throttle or a fixed throttle and an open / close switching valve are provided in parallel in each oil passage between the both pressure adjusting units and the both pressure reducing cylinders. apparatus.
ロッド側油路出口に直付け又は近接配置されるマニホー
ルドに組込んだことを特徴とする請求項５記載の圧延機
用油圧圧下装置。6. The hydraulic pressure reducing device for a rolling mill according to claim 5, wherein the both pressure adjusting units are incorporated in a manifold which is directly mounted on or close to the rod side oil passage outlets of the both pressure reducing cylinders.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6105214A JP2820887B2 (en) | 1994-05-19 | 1994-05-19 | Hydraulic rolling device for rolling mill |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6105214A JP2820887B2 (en) | 1994-05-19 | 1994-05-19 | Hydraulic rolling device for rolling mill |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07308704A true JPH07308704A (en) | 1995-11-28 |
| JP2820887B2 JP2820887B2 (en) | 1998-11-05 |
Family
ID=14401426
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6105214A Expired - Fee Related JP2820887B2 (en) | 1994-05-19 | 1994-05-19 | Hydraulic rolling device for rolling mill |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2820887B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008180389A (en) * | 2008-04-07 | 2008-08-07 | Toshiba Corp | Piping system having throttling element and manufacturing method for this piping system |
| KR100957943B1 (en) * | 2003-05-16 | 2010-05-13 | 주식회사 포스코 | Air vent apparatus of roll bender cylinder |
| CN105080978A (en) * | 2015-09-14 | 2015-11-25 | 太原科技大学 | Design of novel rolling mill hydraulic system |
| CN105090144A (en) * | 2015-09-14 | 2015-11-25 | 太原科技大学 | Pre-loaded large-applied-force hydraulic system |
| CN107387507A (en) * | 2017-08-22 | 2017-11-24 | 天津市中重科技工程有限公司 | A kind of hydraulic system of AWC servomechanism installations |
-
1994
- 1994-05-19 JP JP6105214A patent/JP2820887B2/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100957943B1 (en) * | 2003-05-16 | 2010-05-13 | 주식회사 포스코 | Air vent apparatus of roll bender cylinder |
| JP2008180389A (en) * | 2008-04-07 | 2008-08-07 | Toshiba Corp | Piping system having throttling element and manufacturing method for this piping system |
| CN105080978A (en) * | 2015-09-14 | 2015-11-25 | 太原科技大学 | Design of novel rolling mill hydraulic system |
| CN105090144A (en) * | 2015-09-14 | 2015-11-25 | 太原科技大学 | Pre-loaded large-applied-force hydraulic system |
| CN107387507A (en) * | 2017-08-22 | 2017-11-24 | 天津市中重科技工程有限公司 | A kind of hydraulic system of AWC servomechanism installations |
| CN107387507B (en) * | 2017-08-22 | 2023-06-23 | 中重科技(天津)股份有限公司 | Hydraulic system of AWC servo device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2820887B2 (en) | 1998-11-05 |
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