EP0025852A1 - Hydraulic control for a double loadable adjusting cylinder of a continuous casting plant - Google Patents

Hydraulic control for a double loadable adjusting cylinder of a continuous casting plant Download PDF

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Publication number
EP0025852A1
EP0025852A1 EP80104703A EP80104703A EP0025852A1 EP 0025852 A1 EP0025852 A1 EP 0025852A1 EP 80104703 A EP80104703 A EP 80104703A EP 80104703 A EP80104703 A EP 80104703A EP 0025852 A1 EP0025852 A1 EP 0025852A1
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EP
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Prior art keywords
valve
line
main control
pressure
valves
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Granted
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EP80104703A
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German (de)
French (fr)
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EP0025852B1 (en
Inventor
Erich Maas
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SMS Siemag AG
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SMS Schloemann Siemag AG
Schloemann Siemag AG
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Priority to AT80104703T priority Critical patent/ATE4966T1/en
Publication of EP0025852A1 publication Critical patent/EP0025852A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
    • B22D11/16—Controlling or regulating processes or operations
    • B22D11/20—Controlling or regulating processes or operations for removing cast stock

Definitions

  • the invention relates to a hydraulic control for a double acting cylinder for positioning and securing the position of a guide roller in the strand guide of a continuous casting system, using directional valves within the two main control lines in the manner of electromagnetic valves with mechanical actuation by spring when the electromagnet is de-energized.
  • Hydraulic roller adjustment systems are preferably used in continuous casting plants. Compared to mechanical or electro-mechanical adjustment systems, the hydraulic system has the particular advantage that the contact pressure of the segments or the casters can be adjusted continuously against the mechanical stop that determines the strand thickness, whereby the force is limited by the hydraulic constant pressure system. In this way, a safety function against excessive mechanical stress is taken over, which, when a maximum roller force is exceeded, leads to the reeling of the employed rollers without any appreciable increase in force. Hydraulic adjustment cannot be dispensed with, in particular for the driven rollers of a strand guide, since functionally, retreating under constant force is absolutely necessary for these rollers, because the start-up or cold strand chain causes periodic lifting movements of the rollers when it is transported within the strand guide.
  • An essential criterion for the reliability of a continuous caster is the functionality of the hydraulically actuated positioning cylinders and thus the security against an undesired retraction of the positioning cylinders in the warm or cooling area of the strand guide.
  • the retraction of the strand guide in this area leads to strand bulges and breakthroughs, which usually results in the system being shut down for a long time.
  • the invention is therefore based on the object to improve the functional reliability of the hydraulically operated adjusting cylinders and to ensure the supply of the cylinders with hydraulic fluid even when the control voltage for the electromagnetically switched valves or the entire electrical system fails due to a current error, so that this fails If an emergency supply can be maintained over a longer period of time, which in particular makes it possible to hold the cylinders both in the upper end position and to carry out a downward movement without interruption and to keep the pressure, ie maintain the functions of the hydraulics in every switch position of the main control valves.
  • the check valves which can be influenced by the 4/2-way pilot valve are then opened or closed in such a way that the supply and discharge of the pressure fluid required for lifting takes place via the 4/2-way pilot valve, the supply with oil about the one in the power unit of the hydraulic Lische drive existing pressure accumulator, in which usually pressure-controlled pumps feed, takes place. Since the directional valves to avoid internal oil losses are designed as leak-free seat valves and an operation with regulated pressure via a pressure control valve, which has large leakage losses and would empty the pressure accumulator in the shortest possible time, is not carried out in an emergency, low oil losses only occur on the cylinder . However, these losses can be compensated for over several hours via the pressure accumulator.
  • an exemplary embodiment of the invention shows a circuit diagram for the control with emergency supply in connection with an adjusting cylinder for a guide roller of a continuous casting installation.
  • the hydraulic control is used to actuate pitch cylinders 1 with pistons 2 and piston rods 3 for a driven guide roller 4 in a continuous caster.
  • the piston rods 3 of both adjusting cylinders 1 press on schematically illustrated bearings 5 of the guide roller 4.
  • Each adjusting cylinder 1 is assigned such a control for the reversible adjusting movements of the piston rods 3.
  • the circuit diagram is designed with regard to the switching positions of the valves in the event of a power failure.
  • the cylinder piston 2 is, for example, in the upper end position, i.e. the guide roller 4 is lowered.
  • the control system consists of a high-pressure source (not shown in detail) with a regulating pump and pressure accumulator for supplying a constant hydraulic working pressure.
  • a high-pressure line 6 leads from the high-pressure source via a shut-off valve 7 to the 4/2-way valve 8, which can be actuated electrically against a spring force and to which the switching positions 1 and 11 are assigned.
  • Switch position I i.e.
  • the check valve 10 arranged in line 6 closes because it is relieved to the tank, not shown.
  • the check valve 12 arranged in line 6a is self-actuated.
  • the high-pressure line 6 branches into the two main control lines 13 and 14, which open into the two pressure chambers 1 a and 1 b of the adjusting cylinder 1.
  • Each main control line 13, 14 is assigned an electromagnetically operated 3/2-way valve 15, 16.
  • the directional control valve 15 can be brought into the switch positions from P to A and A to T, the directional control valve 16 into the switch positions from P to D and D to T.
  • the main control line 14 is under pressure, which opens into the pressure chamber 1b of the cylinder in order to keep the guide roller 4 pressed against the strand 17 with an adjustable, constant force.
  • a 4/2-way pilot valve 18 with electromagnetic actuation a, b is arranged for both switching positions III and IV. Electromagnet a is actuated when pressing the roller or while maintaining pressure, while electromagnet b is excited when lifting the guide roller 4.
  • the directional control valve 18 has a catch 18a, so that a switching position which has been set once remains even in the event of a power failure.
  • the inputs P, T of the directional control valve 18 communicate with the high-pressure line 6 and with the return line 19.
  • Another check valve 22 connects a control line 23 leading to the check valve 20 and coming from the check valve 21 to the return line 19 or 11 of the system, the check valve 22 being unlocked.
  • the check valves 21, 22 can namely be controlled via the 4/2-way pilot valve 18 for unlocking, the control pressure being removed via lines 32 and 33 from the outputs G and E of the pilot valve.
  • the magnet a of the directional control valve 18 should be energized, so that the switching position 111 and thus a passage from P to G or E to T is given.
  • the check valve 21 is opened by control pressure in the line 32 and at the same time opens the check valve 20 via line 23 by self-actuation, while the check valve 22 closes because of the pilot control unloaded to the tank and because the line 33 would be unloaded.
  • the circuit diagram also contains other valves, lines and devices, but these are not essential for the actual emergency supply, for example an overpressure regulator 24 and a pilot valve 25 for the overpressure regulator 24 as well as for the pressure control valve 9.
  • the pressure control valve 9, which has large leakage oil losses, is still connected to a leak line 26.
  • a throttle valve 27, 28 is provided in the main control line 13 as well as in the main control line 14.
  • the connections 29, 30 indicate the electrical lines for actuating the valves to be switched electrically.
  • the supply in the normal case and in the event of a power failure for lifting the guide roller is described in more detail below.
  • the directional control valve 8, which is not electrically controlled - and thus assumes a position that is also present in the event of a power failure, which is also absolutely necessary due to the necessary bypassing of the pressure control valve 9 due to the high leakage oil losses - is in the switching position II shown and opens from P to H.
  • the 3/2-way valve 15 is electrically controlled in the normal case (not shown) and opens from P to A, while the likewise electrically controlled 3/2-way valve 16 is opened from D to T.
  • the electromagnet b of the additional 4/2-way pilot valve 18 is actuated so that it takes the illustrated switching position IV, which is maintained by the catch 18a in the event of a power failure.
  • the connection P to E or G to T is established.
  • the check valve 22 is opened or unlocked, whereby the check valve 20 is relieved of the pilot control to the tank and can open by self-opening.
  • the cylinder chamber 1a of the actuating cylinder 1 is in the high-pressure line 6 with the check valve 10 self-actuated and the check valve 12 closed Oil is supplied in line 6a.
  • the displaced oil of the cylinder space 1b passes via the main control line 14 to the tank line 11 and from there into the tank, not shown.
  • the piston rod 3 of the drive cylinder 1 extends and lifts the guide roller 4.

Abstract

1. A hydraulic control system for a double-acting setting cylinder (1), for positioning and securing the position of a guide roller (4) in the strand guideway of a continuous casting plant, including reversing valves (15, 16), which are in the form of solenoid valves which are mechanically actuated by a spring when the solenoid is de-energised, in the two main control lines (13, 14), characterised by : an additional 4/2-way pilot valve (18) which is actuated exclusively electro-mechanically for both its switching positions (III/IV), comprises detaining means for detaining the valve in the selected switching position and is connected in parallel with the alternately reversible 3/2-way valves (15, 16) such that the inputs (P, T) of the pilot valve respectively communicate with the high-pressure line (6) and the return line (19) upstream of the reversing valves ; a first pilot controlled nonreturn valve (20) in the first main control line (13) which leads to the cylinder pressure chamber (1a) (for raising) the guide roller (4), which nonreturn valve closes when this line is relieved of load and can be opened by a pressure in the other, second main control line (14) by means of a second pilot controlled nonreturn valve (21) which is connected to the second main control line and, when open, supplies control pressure for opening the first nonreturn valve (20) in the first main control line ; and a third pilot controlled valve (22), which when opened connects the control pressure line (23) between the second nonreturn valve (21) and the first nonreturn valve (20) to the return line (19, 11) of the control system, the second and the third controlled nonreturn valves (21, 22) being alternately actuated open by way of the pilot valve (18) and, on loss of power, being kept in the respective switching position by the pilot valve (18) detained in its selected position.

Description

Die Erfindung betrifft eine hydraulische Steuerung für einen doppelt beaufschlagbaren Anstellzylinder zum Positionieren und zur Lagesicherung einer Führungsrolle in der Strangführung einer Stranggießanlage, unter Verwendung von Wegeventilen innerhalb der beiden Hauptsteuerleitungen in der Art von Elektromagnetventilen mit mechanischer Betätigung durch Feder bei entregtem Elektromagnet.The invention relates to a hydraulic control for a double acting cylinder for positioning and securing the position of a guide roller in the strand guide of a continuous casting system, using directional valves within the two main control lines in the manner of electromagnetic valves with mechanical actuation by spring when the electromagnet is de-energized.

In Stranggießanlagen werden bevorzugt hydraulische Rollenanstellsysteme eingesetzt. Gegenüber mechanischen oder elektro-mechanischen Anstellsystemen besitzt die Hydraulik vor allem den Vorteil, daß die Anpreßkraft der Segmente bzw. der angestellten Rollen gegen den die Strangdicke bestimmenden mechanischen Anschlag stufenlos eingestellt werden kann, wobei über das Konstantdrucksystem der Hydraulik eine Kraftbegrenzung erfolgt. Damit wird eine Sicherheitsfunktion gegen überhöhte mechanische Belastung übernommen, die beim Überschreiten einer maximalen Rollenkraft zum Zurückweichen der angestellten Rollen ohne nennenswerten Kraftanstieg führt. Insbesondere für die angetriebenen Rollen einer Strangführung kann auf eine hydraulische Anstellung nicht verzichtet werden, da für diese Rollen ein Zurückweichen unter konstanter Kraft funktionstechnisch unbedingt erforderlich ist, weil die Anfahr- oder Kaltstrangkette periodische Hubbewegungen der Rollen verursacht, wenn sie innerhalb der Strangführung transportiert wird.Hydraulic roller adjustment systems are preferably used in continuous casting plants. Compared to mechanical or electro-mechanical adjustment systems, the hydraulic system has the particular advantage that the contact pressure of the segments or the casters can be adjusted continuously against the mechanical stop that determines the strand thickness, whereby the force is limited by the hydraulic constant pressure system. In this way, a safety function against excessive mechanical stress is taken over, which, when a maximum roller force is exceeded, leads to the reeling of the employed rollers without any appreciable increase in force. Hydraulic adjustment cannot be dispensed with, in particular for the driven rollers of a strand guide, since functionally, retreating under constant force is absolutely necessary for these rollers, because the start-up or cold strand chain causes periodic lifting movements of the rollers when it is transported within the strand guide.

Ein wesentliches Kriterium für die Zuverlässigkeit einer Stranggießanlage ist die Funktionstüchtigkeit der hydraulisch beaufschlagbaren Anstellzylinder und damit die Sicherheit gegen ein unerwünschtes Zurückweichen der Anstellzylinder im Warm- bzw. Kühlbereich der Strangführung. Das Zurückweichen der Strangführung in diesem Bereich führt zu Strangausbeulungen und Strangdurchbrüchen, was meist einen langzeitigen Stillstand der Anlage zur Folge hat.An essential criterion for the reliability of a continuous caster is the functionality of the hydraulically actuated positioning cylinders and thus the security against an undesired retraction of the positioning cylinders in the warm or cooling area of the strand guide. The retraction of the strand guide in this area leads to strand bulges and breakthroughs, which usually results in the system being shut down for a long time.

Der Erfindung liegt daher die Aufgabe zugrunde, die Funktionssicherheit der hydraulisch betriebenen Anstellzylinder zu verbessern und die Versorgung der Zylinder mit Hydraulikflüssigkeit auch dann zu gewährleisten, wenn bedingt durch einen Stromfehler die Steuerspannung für die elektromagnetisch geschalteten Ventile oder die gesamte Elektrik ausfällt, so daß in diesem Fall über längere Zeit eine Notversorgung aufrechterhalten werden kann, die es insbesondere ermöglicht, die Zylinder sowohl in der oberen Endstellung zu halten als auch eine Abwärtsbewegung ohne Unterbrechung durchzuführen und den Druck zu halten, d.h. die Funktionen der Hydraulik in jeder Schaltstellung der Haupt-Steuerventile aufrechtzuerhalten.The invention is therefore based on the object to improve the functional reliability of the hydraulically operated adjusting cylinders and to ensure the supply of the cylinders with hydraulic fluid even when the control voltage for the electromagnetically switched valves or the entire electrical system fails due to a current error, so that this fails If an emergency supply can be maintained over a longer period of time, which in particular makes it possible to hold the cylinders both in the upper end position and to carry out a downward movement without interruption and to keep the pressure, ie maintain the functions of the hydraulics in every switch position of the main control valves.

Die Lösung dieser Aufgabe besteht aus den im Patentanspruch angegebenen Merkmalen. Dadurch, daß zusätzlich zu dem in jeder Hauptsteuerleitung vorgesehenen Wegeventil als Hauptsteuerventil noch ein im Nebenstrom angeordnetes Vorsteuerventil als Wegeventil mit Raste über Rückschlagventile in den Hydraulikkreislauf für die Versorgung eines Anstellzylinders geschaltet wird, kann der Anstellzylinder unabhängig von der jeweiligen Schaltstellung der Haupt-Wegeventile die eingeleitete Funktion erfüllen, selbst dann, wenn die zum Heben der Strangführungsrolle in den beiden Hauptsteuerleitungen elektrisch betätigten Haupt-Wegeventile, bedingt durch die Federkraft bei Spannungsausfall, in ihre Ausgangslage zurückgestellt werden. Es werden dann nämlich die von dem 4/2-Wege-Vorsteuerventil beeinflußbaren Rückschlagventile so aufgesteuert oder geschlossen, daß die zum Heben erforderliche Zu- bzw. Abfuhr der Druck Flüssigkeit über das 4/2-Wege-Vorsteuerventil erfolgt, wobei die Versorgung mit Öl über den/die in der Krafteinheit des hydrau- Lischen Antriebes vorhandenen Druckspeicher, in welchen üblicherweise druckgeregelte Pumpen einspeisen, erfolgt. Da die Wegeventile zur Vermeidung von internen Ölverlusten als leckölfreie Sitzventile ausgeführt sind und eine Betriebsweise mit geregeltem Druck über ein Druckregelventil, welches große Leckageverluste aufweist und den Druckspeicher in kürzester Frist leeren würde, in einem Notfall nicht durchgeführt wird, treten geringe Ölverluste lediglich am Zylinder auf. Diese Verluste können aber über mehrere Stunden über den Druckspeicher kompensiert werden.The solution to this problem consists of the features specified in the claim. The fact that in addition to the directional valve provided in each main control line as the main control valve, a pilot valve arranged in the bypass flow as a directional valve with detent is switched into the hydraulic circuit for the supply of an adjusting cylinder via check valves via check valves, the starting cylinder can be initiated regardless of the respective switching position of the main directional valves Fulfill the function, even if the main directional control valves, which are electrically operated to lift the strand guide roller in the two main control lines, are returned to their starting position due to the spring force in the event of a power failure. The check valves which can be influenced by the 4/2-way pilot valve are then opened or closed in such a way that the supply and discharge of the pressure fluid required for lifting takes place via the 4/2-way pilot valve, the supply with oil about the one in the power unit of the hydraulic Lische drive existing pressure accumulator, in which usually pressure-controlled pumps feed, takes place. Since the directional valves to avoid internal oil losses are designed as leak-free seat valves and an operation with regulated pressure via a pressure control valve, which has large leakage losses and would empty the pressure accumulator in the shortest possible time, is not carried out in an emergency, low oil losses only occur on the cylinder . However, these losses can be compensated for over several hours via the pressure accumulator.

In der Zeichnung ist als Ausführungsbeispiel der Erfindung ein Schaltplan für die Steuerung mit Notversorgung in Verbindung mi t einem Anstellzylinder für eine Führungsrolle einer Stranggießanlage dargestellt. Die hydraulische Steuerung dient zum Betätigen von Anstellzylindern 1 mit Kolben 2 und Kolbenstangen 3 für eine angetriebene Führungsrolle 4 in einer Stranggießanlage. Die Kolbenstangen 3 beider Anstellzylinder 1 drücken auf schematisch dargestellte Lager 5 der Führungsrolle 4. Jedem Anstellzylinder 1 ist solch eine Steuerung für die reversierbaren Anstellbewegungen der Kolbenstangen 3 zugeordnet.In the drawing, an exemplary embodiment of the invention shows a circuit diagram for the control with emergency supply in connection with an adjusting cylinder for a guide roller of a continuous casting installation. The hydraulic control is used to actuate pitch cylinders 1 with pistons 2 and piston rods 3 for a driven guide roller 4 in a continuous caster. The piston rods 3 of both adjusting cylinders 1 press on schematically illustrated bearings 5 of the guide roller 4. Each adjusting cylinder 1 is assigned such a control for the reversible adjusting movements of the piston rods 3.

Der Schaltplan ist hinsichtlich der Schaltstellungen der Ventile für den Fall des Stromausfalles entworfen. Der Zylinderkolben 2 befindet sich beispielsweise in der oberen Endstellung, d.h. die Führungsrolle 4 ist abgesenkt. Die Steuerung besteht aus einer nicht näher dargestellten Hochdruckquelle mit Regelpumpe und Druckspeicher zur Lieferung eines konstanten hydraulischen Arbeitsdruckes. Von der Hochdruckquelle führt eine Hochdruckleitung 6 über ein Absperrventil 7 zu dem gegen eine Federkraft elektrisch betätigbaren 4/2-Wege-Ventil 8, dem die Schaltstellungen 1 und 11 zugeordnet sind. Die Schaltstellung I, d.h. mit erregetem Elektromagneten, wird immer dann zu wählen sein, wenn der Antriehszylinder 1 mittels geregeltem Druck über das Druckregelventil 9 gefahren werden soll. In diesem Fall schließt das in der Leitung 6 angeordnete Rückschlagventil 10, weil es zum nicht dargestellten Tank entlastet ist. Dafür wird das in der Leitung 6a angeordnete Rückschlagventil 12 eigenaufgesteuert.The circuit diagram is designed with regard to the switching positions of the valves in the event of a power failure. The cylinder piston 2 is, for example, in the upper end position, i.e. the guide roller 4 is lowered. The control system consists of a high-pressure source (not shown in detail) with a regulating pump and pressure accumulator for supplying a constant hydraulic working pressure. A high-pressure line 6 leads from the high-pressure source via a shut-off valve 7 to the 4/2-way valve 8, which can be actuated electrically against a spring force and to which the switching positions 1 and 11 are assigned. Switch position I, i.e. with energized electromagnet, it will always have to be selected when the drive cylinder 1 is to be driven by means of regulated pressure via the pressure regulating valve 9. In this case, the check valve 10 arranged in line 6 closes because it is relieved to the tank, not shown. For this purpose, the check valve 12 arranged in line 6a is self-actuated.

Die Hochdruckleitung 6 zweigt sich in die beiden Hauptsteuerleitungen 13 und 14, die in die beiden Druckräume 1a und 1b des Anstellzylinders 1 einmünden. Jeder Hauptsteurleitung 13, 14 ist ein elektromagnetisch zu betätigendes 3/2-Wege-Ventil 15, 16 zugeordnet. Das Wegeventil 15 kann in die Schaltstellungen von P nach A und A nach T, das Wegeventil 16 in die Schaltstellungen von P nach D und D nach T gebracht werden. In der dargestellten Schaltung steht die HauptsteuerlEitung 14 unter Druck, die in den Druckraum 1b des Zylinders einmündet, um die Führungsrolle 4 mit einer einstellbaren, konstanten Kraft gegen den Strang 17 gedrückt zu halten.The high-pressure line 6 branches into the two main control lines 13 and 14, which open into the two pressure chambers 1 a and 1 b of the adjusting cylinder 1. Each main control line 13, 14 is assigned an electromagnetically operated 3/2-way valve 15, 16. The directional control valve 15 can be brought into the switch positions from P to A and A to T, the directional control valve 16 into the switch positions from P to D and D to T. In the circuit shown, the main control line 14 is under pressure, which opens into the pressure chamber 1b of the cylinder in order to keep the guide roller 4 pressed against the strand 17 with an adjustable, constant force.

Im Nebenschluß zu den wechselweise umsteuerbaren 3/2-Wege-Ventilen 15, 16 ist ein 4/2-Wege-Vorsteuerventil 18 mit elektromagnetischer Betätigung a, b für beide Schaltstellungen III und IV angeordnet. Elektromagnet a wird dabei beim Andrücken der Rolle bzw. bei der Druckhaltung betätigt, während Elektromagnet b beim Heben der Führungsrolle 4 erregt ist. Das Wegeventil 18 weist eine Raste 18a auf, so daß eine einmal eingestellte Schaltstellung auch bei Stromausfall bestehen bleibt. Die Eingäng P, T des Wegeventils 18 kommunizieren mit der Hochdruckleitung 6 bzw. mit der Rücklaufleitung 19. Weiterhin ist in der zum Zylinderraum 1a für das Heben der Führungsrolle 4 führenden Hauptsteuerleitung 13 ein Rückschlagventil 20 und in einem Abzweig der zweiten Hauptsteuerleitung 14 ein Rückschlagventil 21 vorgesehen. Ein weiteres Rückschlagventil 22 verbindet eine zum Rückschlagventil 20 führende und vom Rückschlagventil 21 kommende Steuerleitung 23 mit der Rücklaufleitung 19 bzw. 11 des Systems, wobei das Rückschlagventil 22 entsperrt ist. Die Rückschlagventile 21, 22 sind nämlich über das 4/2-Wege-Vorsteuerventil 18 wahlweise zum Entsperren ansteuerbar, wobei der Steuerdruck über die Leitungen 32 bzw. 33 von den Ausgängen G bzw. E des Vorsteuerventils abgenommen wird. Für die abgebildete Schaltung zum Andrücken oder Senken der Führungsrolle 4 mit Hochdruck gilt, daß der Magnet a des Wegeventils 18 erregt sein müßte, womit die Schaltstellung 111 und damit ein Durchgang von P nach G bzw. E nach T gegeben ist.In addition to the alternately reversible 3/2-way valves 15, 16, a 4/2-way pilot valve 18 with electromagnetic actuation a, b is arranged for both switching positions III and IV. Electromagnet a is actuated when pressing the roller or while maintaining pressure, while electromagnet b is excited when lifting the guide roller 4. The directional control valve 18 has a catch 18a, so that a switching position which has been set once remains even in the event of a power failure. The inputs P, T of the directional control valve 18 communicate with the high-pressure line 6 and with the return line 19. Furthermore, there is a check valve 20 in the main control line 13 leading to the cylinder space 1a for lifting the guide roller 4 and a check valve 21 in a branch of the second main control line 14 intended. Another check valve 22 connects a control line 23 leading to the check valve 20 and coming from the check valve 21 to the return line 19 or 11 of the system, the check valve 22 being unlocked. The check valves 21, 22 can namely be controlled via the 4/2-way pilot valve 18 for unlocking, the control pressure being removed via lines 32 and 33 from the outputs G and E of the pilot valve. For the illustrated circuit for pressing or lowering the guide roller 4 at high pressure, the magnet a of the directional control valve 18 should be energized, so that the switching position 111 and thus a passage from P to G or E to T is given.

Das Rückschlagventil 21 wird dabei durch Steuerdruck in der Leitung 32 geöffnet und öffnet gleichzeitig über die Leitung 23 durch Eigenaufsteuerung das Rückschlagventil 20, während das Rückschlagventil 22 wegen der zum Tank entlasteten Vorsteuerung und weil die Leitung 33 entlastet wäre, schließt.The check valve 21 is opened by control pressure in the line 32 and at the same time opens the check valve 20 via line 23 by self-actuation, while the check valve 22 closes because of the pilot control unloaded to the tank and because the line 33 would be unloaded.

Der Schaltplan enthält noch andere Ventile, Leitungen und Einrichtungen, die aber für die eigentliche Notversorgung nicht wesentlich sind.So sind noch ein Uberdruckregler 24 und ein Vorsteuerventil 25 für den Überdruckregler 24 wie auch für das Druckregelventil 9 zu erkennen. Das Druckregelventil 9, welches große Leckölverluste aufweist, ist noch mit einer Leckleitung 26 verbunden. In der Hauptsteuerleitung 13 ist ebenso wie in der Hauptsteuerleitung 14 ein Drosselventil 27, 28 vorgesehen. Die Verbindungen 29, 30 geben die elektrischen Leitungen zur Betätigung der elektrisch zu schaltenden Ventile an.The circuit diagram also contains other valves, lines and devices, but these are not essential for the actual emergency supply, for example an overpressure regulator 24 and a pilot valve 25 for the overpressure regulator 24 as well as for the pressure control valve 9. The pressure control valve 9, which has large leakage oil losses, is still connected to a leak line 26. A throttle valve 27, 28 is provided in the main control line 13 as well as in the main control line 14. The connections 29, 30 indicate the electrical lines for actuating the valves to be switched electrically.

Im folgenden wird die Versorgung im Normalfall und bei Spannungsausfall für das Heben der Führungsrolle näher beschrieben. Das Wegeventil 8, welches nicht elektrisch angesteuert ist - und damit eine Position einnimmt, die auch bei Spannungsausfall vorliegt, was wegen des durch die hohen Leckölverluste bedingten notwendigen Umgehens des Druckregelventils 9 auch unbedingt erforderlich ist - befindet sich in der abgebildeten Schaltstellung II und öffnet von P nach H. Das 3/2-Wege-Ventil 15 ist im nicht dargestellten Normalfall elektrisch angesteuert und öffnet von P nach A, während das ebenfalls elektrisch angesteuerte 3/2-Wege-Ventil 16 von D nach T geöffnet ist. Der Elektromagnet b des zusätzlichen 4/2-Wege-Vorsteuerventils 18 ist betätigt, so daß dieses die dargestellte Schaltstellung IV cinnimmt, die durch die Raste 18a bei Stromausfall eingehalten wird. Die Verbindung P nach E bzw. G nach T ist hergestellt. Das Rückschlagventil 22 wird aufgesteuert bzw. entsperrt, wodurch das Rückschlagventil 20 von der Vorsteuerung zum Tank entlastet ist und durch Eigenaufsteuerung öffnen kann. Dem Zylinderraum 1a des Anstellzylinders 1 wird bei eigenaufgesteuertem Rückschlagventil 10 in der Hochdruckleitung 6 und geschlossenem Rückschlagventil 12 in der Leitung 6a Öl zugeführt. Das verdrängte Öl des Zylinderaums 1b gelangt über die Hauptsteuerleitung 14 zur Tankleitung 11 und von dort in den nicht dargestellten Tank. Die Kolbenstange 3 des Antriebszylinders 1 fährt aus und hebt die Führungsrolle 4 . Durch das in der Schaltstellung IV eingerastete 4/2-Wege-Ventil 18 und der damit verbundenen Vorsteuerung der Rückschlagventile (Rückschlagventil 22 ist entsperrt, Rückschlagventil 20 daher geschlossen, weil von der Vorsteuerung zum Tank entlastet) ist gewährleistet, daß auch bei Ausfall der Elektrik - wobei dann die Wegeventile 15, 16 durch die Federkraft in die Ausgangslage mit den Durchgängen von A nach T bzw. P nach D gestellt sind - während der Aufwärtsbewegung des Zylinderkolbens 2 diese Betriebsweise durchgeführt werden kann und die Führungsrolle 4 danach in der oberen Endstellung gehalten wird.The supply in the normal case and in the event of a power failure for lifting the guide roller is described in more detail below. The directional control valve 8, which is not electrically controlled - and thus assumes a position that is also present in the event of a power failure, which is also absolutely necessary due to the necessary bypassing of the pressure control valve 9 due to the high leakage oil losses - is in the switching position II shown and opens from P to H. The 3/2-way valve 15 is electrically controlled in the normal case (not shown) and opens from P to A, while the likewise electrically controlled 3/2-way valve 16 is opened from D to T. The electromagnet b of the additional 4/2-way pilot valve 18 is actuated so that it takes the illustrated switching position IV, which is maintained by the catch 18a in the event of a power failure. The connection P to E or G to T is established. The check valve 22 is opened or unlocked, whereby the check valve 20 is relieved of the pilot control to the tank and can open by self-opening. The cylinder chamber 1a of the actuating cylinder 1 is in the high-pressure line 6 with the check valve 10 self-actuated and the check valve 12 closed Oil is supplied in line 6a. The displaced oil of the cylinder space 1b passes via the main control line 14 to the tank line 11 and from there into the tank, not shown. The piston rod 3 of the drive cylinder 1 extends and lifts the guide roller 4. The 4/2-way valve 18 engaged in the switching position IV and the associated pilot control of the check valves (check valve 22 is unlocked, check valve 20 is therefore closed because the pilot control relieves the load on the tank) ensures that even if the electrical system fails - Then the directional valves 15, 16 are set by the spring force in the starting position with the passages from A to T or P to D - during the upward movement of the cylinder piston 2, this mode of operation can be carried out and the guide roller 4 is then held in the upper end position becomes.

Wenn dagegen zum Druckhalten die Hauptsteuerleitung 14 Hochdruck führt und das Vorsteuerventil 18 in Schaltstellung III fixiert ist, gelangt die Steuerleitung 32 unter Druck, wodurch das Rückschlagventil 21 entsperrt wird und der sich aus der Hauptsteuerleitung 14 in die Steuerleitung 23 fortpflanzende Druck das Rückschlagven- til 20 entsperrt und Ventil 22 schließt. Der Druck im Zylinderraum 1b wird unter Entlastung der Hauptsteuerleitung 13 (Ventil 20 offengehalten) über lange Zeit gehalten.On the other hand, if the main control line 14 leads to high pressure and the pilot valve 18 is fixed in switch position III, the control line 32 comes under pressure, whereby the check valve 21 is unlocked and the pressure propagating from the main control line 14 into the control line 23 causes the check valve 20 unlocked and valve 22 closes. The pressure in the cylinder space 1b is maintained for a long time while relieving the main control line 13 (valve 20 kept open).

Claims (1)

Hydraulische Steuerung für einen doppelt beaufschlagbaren Anstellzylinder zum Positionieren und zur Lagesicherung einer Führungsrolle in der Strangführung einer Stranggießanlage, unter Verwendung von Wegeventilen innerhalb der beiden Hauptsteuerleitungen in der Bauart von Elektromagnetventilen mit mechanischer Betätigung durch Feder bei entregtem Elektromagnet, gekennzeichnet durch ein zusätzliches 4/2-Wege-Vorsteuerventil (18) mit ausschließlich elektromagnetischer Betätigung für beide Schaltstellungen (III / IV) und mit Raste zum Fixieren einer jeden Schaltstellung, das im Nebenfluß zu den wechselweise umsteuerbaren 3/2-Wege-Ventilen (15, 16) angeordnet ist derart, daß die Eingänge (P, T) des Vorsteuerventils jeweils mit der Hochdruckleitung (6) und der Rücklaufleitung (19) vor den Umsteuerventilen kommunizieren, durch ein erstes entsperrbares Rückschlagventil (20) in der zum Zylinderdruckraum (1a) für das Heben der Führungsrolle (4) führenden ersten Hauptsteuerleitung (13), das bei Entlastung dieser Leitung schließt und durch einen in der anderen, zweiten Hauptsteuerleitung (14) vorhandenen Druck entsperrbar ist, indem an die zweite liauptsteuerleitung ein zweites entsperrbares Rückschlagventil (21) angeschlossen ist, das in entsperrter Offenstellung den Steuerdruck zum Entsperren des ersten Rückschlagventils (20) in der ersten Hauptsteuerleitung liefert, und durch ein drittes entsperrbares Rückschlagventil (22), das die den Steuerdruck führende Leitung (23) zwischen dem ersten Rückschlagventil (20) und dem zweiten Rückschlagventil (21) mit der Rücklaufleitung (19, 11) des Systems verbindet, wenn das dritte Rückschlagventil (22) entsperrt ist, wobei das zweite und das dritte entsperrbare Rückschlagventil (21, 22) über das Vorsteuerventil (18) wechselweise zum Entsperren angesteuert sind und bei Stromausfall durch das eingerastete Vorsteuerventil (18) in der jewciligen Schaltstellung verbleiben. Hydraulic control for a double acting actuating cylinder for positioning and securing the position of a guide roller in the strand guide of a continuous caster, using directional valves within the two main control lines in the form of electromagnetic valves with mechanical actuation by spring when the electromagnet is de-energized, characterized by an additional 4/2-way pilot valve (18) with exclusively electromagnetic actuation for both switching positions (III / IV) and with detent for fixing each switching position, which, in addition to the alternately reversible 3/2-way valves (15, 16) is arranged such that the inputs (P, T) of the pilot valve communicate with the high pressure line (6) and the return line (19) in front of the changeover valves a first unlockable check valve (20) in the first main control line (13) leading to the cylinder pressure chamber (1a) for lifting the guide roller (4), which closes when this line is relieved and can be unlocked by a pressure present in the other, second main control line (14) is connected to the second main control line, a second unlockable check valve (21) which, in the unlocked open position, the control pressure for unlocking the first check valve (20) in the first Main control line supplies, and by a third unlockable check valve (22) which connects the line (23) carrying the control pressure between the first check valve (20) and the second check valve (21) to the return line (19, 11) of the system when the third check valve (22) is unlocked, whereby the second and the third unlockable check valve (21, 22) are alternately controlled to unlock via the pilot valve (18) and remain in the respective switching position in the event of a power failure by the engaged pilot valve (18).
EP80104703A 1979-09-07 1980-08-09 Hydraulic control for a double loadable adjusting cylinder of a continuous casting plant Expired EP0025852B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80104703T ATE4966T1 (en) 1979-09-07 1980-08-09 HYDRAULIC CONTROL FOR A DOUBLE ACTUATION CYLINDER IN A CONTINUOUS CASTING PLANT.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19792936146 DE2936146A1 (en) 1979-09-07 1979-09-07 HYDRAULIC CONTROL FOR A DOUBLE PRESSURABLE TURNING CYLINDER IN A CONTINUOUS CASTING SYSTEM
DE2936146 1979-09-07

Publications (2)

Publication Number Publication Date
EP0025852A1 true EP0025852A1 (en) 1981-04-01
EP0025852B1 EP0025852B1 (en) 1983-10-12

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EP80104703A Expired EP0025852B1 (en) 1979-09-07 1980-08-09 Hydraulic control for a double loadable adjusting cylinder of a continuous casting plant

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EP (1) EP0025852B1 (en)
AT (1) ATE4966T1 (en)
DE (1) DE2936146A1 (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2226290A (en) * 1988-10-14 1990-06-27 Rexroth Mannesmann Gmbh A device for supporting and guiding the billet discharging from a continuous casting plant
EP0383066A2 (en) * 1989-02-13 1990-08-22 Sms Schloemann-Siemag Aktiengesellschaft Conduit rupture protection valve
WO1997041983A1 (en) * 1996-05-08 1997-11-13 Voest-Alpine Industrieanlagenbau Gmbh Adjusting device for setting the position of billet-support elements
WO2009115174A1 (en) * 2008-03-19 2009-09-24 Sms Siemag Ag Strand guiding device and method for the operation thereof
CN109108241A (en) * 2018-10-30 2019-01-01 中国重型机械研究院股份公司 A kind of hydraulic control system for conticaster production
CN110541860A (en) * 2019-09-24 2019-12-06 中国重型机械研究院股份公司 Online thermal width-adjusting hydraulic control system and method for crystallizer

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10044064B4 (en) * 2000-08-31 2004-02-05 Mannesmannröhren-Werke Ag Method and device for adjusting the mouth width of a segment of a support roller frame
CN110594210B (en) * 2019-09-24 2021-08-24 中冶南方连铸技术工程有限责任公司 Hydraulic control system for press roll of withdrawal and straightening machine based on position and pressure double-control mode

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DE1426501B2 (en) * 1964-02-11 1971-08-12 Guttropf, Walter, Dipl. Ing , Brugg (Schweiz) SAFETY CONTROL SYSTEM FOR A PNEUMATIC OR HYDRAULIC CYLINDER
DE2734851A1 (en) * 1977-08-02 1979-02-15 Textron Inc Redundant pressure medium control system - has several control channels each with individual medium source control valve and monitor valve

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1426501B2 (en) * 1964-02-11 1971-08-12 Guttropf, Walter, Dipl. Ing , Brugg (Schweiz) SAFETY CONTROL SYSTEM FOR A PNEUMATIC OR HYDRAULIC CYLINDER
DE2734851A1 (en) * 1977-08-02 1979-02-15 Textron Inc Redundant pressure medium control system - has several control channels each with individual medium source control valve and monitor valve

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2226290A (en) * 1988-10-14 1990-06-27 Rexroth Mannesmann Gmbh A device for supporting and guiding the billet discharging from a continuous casting plant
GB2226290B (en) * 1988-10-14 1992-08-05 Rexroth Mannesmann Gmbh A device for supporting and guiding the billet discharging from a continuous casting plant
EP0383066A2 (en) * 1989-02-13 1990-08-22 Sms Schloemann-Siemag Aktiengesellschaft Conduit rupture protection valve
EP0383066A3 (en) * 1989-02-13 1991-07-10 Sms Schloemann-Siemag Aktiengesellschaft Conduit rupture protection valve
WO1997041983A1 (en) * 1996-05-08 1997-11-13 Voest-Alpine Industrieanlagenbau Gmbh Adjusting device for setting the position of billet-support elements
AT404807B (en) * 1996-05-08 1999-03-25 Voest Alpine Ind Anlagen ACTUATING DEVICE FOR SETTING THE LOCATION OF STRAND SUPPORT ELEMENTS
US6176297B1 (en) 1996-05-08 2001-01-23 Voest-Alpine Industrieanlagenbau Gmbh Adjusting device for setting the position of billet-support elements
WO2009115174A1 (en) * 2008-03-19 2009-09-24 Sms Siemag Ag Strand guiding device and method for the operation thereof
CN109108241A (en) * 2018-10-30 2019-01-01 中国重型机械研究院股份公司 A kind of hydraulic control system for conticaster production
CN109108241B (en) * 2018-10-30 2024-02-20 中国重型机械研究院股份公司 Hydraulic control system for continuous casting machine production
CN110541860A (en) * 2019-09-24 2019-12-06 中国重型机械研究院股份公司 Online thermal width-adjusting hydraulic control system and method for crystallizer
CN110541860B (en) * 2019-09-24 2023-06-23 中国重型机械研究院股份公司 Crystallizer on-line thermal width adjustment hydraulic control system and method

Also Published As

Publication number Publication date
EP0025852B1 (en) 1983-10-12
DE2936146A1 (en) 1981-03-19
ATE4966T1 (en) 1983-10-15

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