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EP0433791B1 - Actuator for a feeding valve - Google Patents

Actuator for a feeding valve Download PDF

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Publication number
EP0433791B1
EP0433791B1 EP90123496A EP90123496A EP0433791B1 EP 0433791 B1 EP0433791 B1 EP 0433791B1 EP 90123496 A EP90123496 A EP 90123496A EP 90123496 A EP90123496 A EP 90123496A EP 0433791 B1 EP0433791 B1 EP 0433791B1
Authority
EP
European Patent Office
Prior art keywords
valve
valves
line
pressure
test system
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.)
Expired - Lifetime
Application number
EP90123496A
Other languages
German (de)
French (fr)
Other versions
EP0433791A1 (en
Inventor
Rico Plangger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ABB Asea Brown Boveri Ltd
ABB AB
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Priority to AT90123496T priority Critical patent/ATE104014T1/en
Publication of EP0433791A1 publication Critical patent/EP0433791A1/en
Application granted granted Critical
Publication of EP0433791B1 publication Critical patent/EP0433791B1/en
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/20—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted
    • F01D17/22—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted the operation or power assistance being predominantly non-mechanical
    • F01D17/26—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted the operation or power assistance being predominantly non-mechanical fluid, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/16—Trip gear
    • F01D21/18—Trip gear involving hydraulic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/20—Checking operation of shut-down devices
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8158—With indicator, register, recorder, alarm or inspection means
    • Y10T137/8326—Fluid pressure responsive indicator, recorder or alarm

Definitions

  • the invention relates to a drive for a feed valve with a hydraulically pressurized actuation line and with a device for controlling the pressure in the actuation line, which has three valves connected to one another to form a hydraulic 2-by-3 circuit.
  • a drive for a feed valve is known from the patent specification CH 666 132.
  • This drive which is operated with oil at comparatively low pressure, actuates, for example, a quick-closing valve, which serves as a feed valve for the steam feed of a turbine.
  • the oil under pressure or another hydraulic fluid acts on the actuator via an actuation line so that it can open or close the feed valve.
  • the pressure in the actuation line is controlled by a device which has three valves connected to one another to form a hydraulic 2 by 3 circuit.
  • These valves are designed as electromagnetically operated slide valves and each is monitored separately for its functionality, so that three monitoring circuits are necessary. These monitoring circuits have mechanical contacts that require maintenance. This device is less suitable for use at higher pressures.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, solves the problem of creating a drive for a feed valve which is suitable for a comparatively high pressure of the driving oil and whose functionality can be monitored with simple means.
  • FIG. 1 shows a schematic diagram of a part of the drive, namely the part that includes a device for controlling the pressure in an actuation line 1.
  • Oil is generally used as the medium for transmitting this pressure, but another hydraulic fluid or a gaseous medium can also be used for this.
  • a cylinder-piston arrangement of the drive is actuated, which opens or closes the associated feed valve, also not shown.
  • this feed valve will be open when the pressure in the actuating line 1 is fully present and as soon as the pressure drops, it will close quickly.
  • This device for controlling the pressure has three identical valves 2, 3 and 4 which are interconnected to form a hydraulic 2 by 3 circuit.
  • the oil pressurized by a pump not shown, reaches this device. Pressures in the range around 160 bar are used.
  • oil is fed under pressure directly into the actuating line 1 via a line 10 provided with an orifice 9, the Aperture 9 determines the flow rate of the oil.
  • Another line 12 provided with an orifice 11 feeds a small amount of oil under pressure into a line 13 of a test system 14.
  • the line 13 feeds a pressure switch 16 via a shut-off device 15.
  • the shut-off device 15 is usually only closed when the pressure switch 16 is revised.
  • the pressure switch 16 can contain, for example, a piezoelectric measuring element which works without mechanical contact and therefore practically maintenance-free.
  • the pressure switch 16 responds when the pressure falls below a set minimum value and emits an electrical signal to a higher-level plant control system, not shown, where this signal is processed further.
  • solenoid valves 25, 26, 27 are fed from the inlet 8.
  • the solenoid valves 25, 26, 27 are shown magnetically excited, in the event of a failure of the electrical energy or a shutdown of the same, the solenoid valves 25, 26, 27 are each by a schematically indicated spring 28, 29 and 30 in a second position shown sketched pressed.
  • the oil flows under pressure through the solenoid valves 25, 26, 27 through in each case a line 31, 32 and 33 which leads into a schematically illustrated drive volume 34, 35 and 36 of the valves 2, 3, 4.
  • the drive volume 34 is assigned to the valve 2, the drive volume 35 to the valve 3 and the drive volume 36 to the valve 4.
  • another output 37, 38 and 39 of the solenoid valves 25, 26, 27 is connected to an outlet 41 via a common line 40. In the drawn valve position, however, the outlets 37, 38, 39 are not traversed by oil.
  • valves 2, 3, 4 are designed as double valves, each having a seat valve and a slide valve, the type will be explained in more detail later in connection with FIG. 5.
  • Valves 2, 3, 4 are shown in FIG. 1, each with pressurized drive volume 34, 35, 36; if the supply of oil under pressure through the respective lines 31, 32, 33 is omitted, valves 2, 3, 4 each pressed by strong springs 42, 43 and 44 into a second switching position shown in FIG. 1. This ensures that the valves always assume a defined switching position even in the event of a malfunction.
  • each of the valves 2, 3, 4 has four further connections for oil lines.
  • the valve 2 has the connections 45, 46, 47 and 48.
  • the valve 3 has the connections 49, 50, 51 and 52.
  • the valve 4 has the connections 53, 54, 55 and 56.
  • connection 45 of the valve 2 is connected to the actuation line 1 and separated from the connection 46 by a schematically indicated slide valve.
  • the connection 46 is connected to the line 13 of the test system 14 via a line 60, in which a check valve 61 is attached.
  • the check valve 61 is arranged such that an oil flow out of the test system 14 is possible.
  • the connection 47 is connected to the outlet 41. Between the connections 47 and 48, the switching symbol for a seat valve is drawn inside the valve 2. In this switching position, no oil passage is possible between the two connections 47 and 48 in both directions, since there is always a lower pressure on the side of the drain 41.
  • the connection 48 is connected to the line 13 of the test system 14 via a check valve 62. Check valve 62 allows oil flow out of test system 14.
  • connection 49 of the valve 3 is connected to the actuation line 1 and it is separated from the connection 50 by an indicated slide valve.
  • the connection 50 is connected to the connection 48 of the valve 2 and at the same time to the test system 14 via the check valve 62.
  • the connection 51 is connected to the outlet 41. In this switching position, the connection between the connections 51 and 52 is blocked by an indicated seat valve.
  • the connection 52 is connected to the line 13 of the test system 14 via a check valve 63.
  • the check valve 63 allows an oil flow out of the test system 14.
  • connection 53 of the valve 4 is connected to the actuation line 1 and it is separated from the connection 54 by an indicated slide valve.
  • the connection 54 is connected to the connection 52 of the valve 3 and at the same time to the test system 14 via the check valve 63.
  • the connection 55 is connected to the outlet 41. In this switching position, the connection between the connections 55 and 56 is blocked by an indicated seat valve.
  • the connection 56 opens before the check valve 61 into the line 60, so that the connection 56 is operatively connected to the test system 14 via this check valve 61.
  • the schematic diagram according to FIG. 2 differs from FIG. 1 only in that the line 10 and the cover 9 are replaced by three lines 70, 71 and 72.
  • the line 70 connects the line 31 to the connection 45 of the valve 2 and at the same time to the actuating line 1.
  • a check valve 73 is installed in the line 70, which allows an oil flow from the line 31 in the direction of the actuating line 1, the amount of the flowing Oil is limited by an aperture 74 also provided in line 70.
  • Line 71 connects the line 32 with the connection 49 of the valve 3 and at the same time with the actuation line 1.
  • a check valve 75 and an orifice 76 are installed in the line 71, so that an oil flow from the line 32 in the direction of the actuation line 1 is possible.
  • the line 72 connects the line 33 to the connection 53 of the valve 4 and at the same time to the actuation line 1.
  • a check valve 77 and an orifice 78 are installed in the line 72, so that an oil flow from the line 33 in the direction of the actuation line 1 is possible.
  • FIG. 3 corresponds to the sketch according to FIG. 2, only the solenoid valves 25, 26, 27 have a second switching position and consequently also the valves 2, 3 and 4 actuated by them.
  • the solenoid valves 25, 26, 27 are here shown in the switch position in which they are pressed by the respective springs 28, 29, 30 when the electrical energy for the magnetic excitation fails or is deactivated.
  • the three lines 31, 32 and 33 are relieved of the oil pressure by the solenoid valves 25, 26, 27 and the line 40 to the outlet 41 and thus the three drive volumes 34, 35, 34 are emptied and the springs 42, 43, 44 press the valves 2, 3, 4 in the switching position shown in Fig. 3.
  • FIG. 4 shows a possible operating state of the device.
  • the valves 3 and 4 are switched as in FIG. 2, the valve 2 is switched analogously to FIG. 3.
  • This position of the valve 2 may have been deliberately created by controlling the energy for the magnetic excitation of the associated solenoid valve 25, as a result of which, as already described, the drive volume 34 is relieved of pressure, with the result that the spring 42 pushes the valve 2 into the presses the switch position shown, but it is also possible that there is a real malfunction which, for example, has interrupted the energy supply.
  • a conscious one The energy would be cut off if, for example, a functional check of the valve 2 is to be carried out.
  • FIG. 5 shows a schematic diagram of the valve 2, the valves 3 and 4 being constructed identically, the switching position being the same as that shown in FIG. 2.
  • the valve 2 is arranged in a cylindrical bore 80 of a hydraulic block, which also includes the valves 3 and 4.
  • the line 31 leads into the cylindrical drive volume 34.
  • the pressure of the oil in the drive volume 34 acts on a piston 81 which is arranged displaceably in the bore 80.
  • the piston 81 is formed in one piece, it has two sealing points, namely a sealing edge 82 which cooperates with an edge 83 of the bore 80 when the piston 81 moves upwards, and a sealing seat 84.
  • the valve 2 accordingly has in the upper part a slide valve with the sealing edge 82 between the connections 45 and 46 and in the lower part it has a seat valve with the sealing seat 84 between the connections 47 and 48.
  • the valve 2 When the valve 2 is opened, i.e. when the piston 81 moves upward, it has an advantageous effect that passing the edge 83 through the sealing edge 82 brings about a valve opening of the slide valve without causing a significant change in volume that occurs in the adjacent volumes and lines could lead to impermissible pressure fluctuations and the resulting incorrect actuation of the drive.
  • the spring 42 is indicated, which pushes the piston 81 upwards into a defined open position after a pressure drop in the drive volume 34.
  • the spring 42 is supported against a support 85.
  • FIG. 1 is considered in more detail.
  • the valves 2, 3, 4 and the solenoid valves 25, 26, 27 work perfectly and the actuating line 1 is under pressure, so that the feed valve is kept open. Trouble-free normal operation is guaranteed.
  • Oil is kept under pressure in the actuation line 1 from the inlet 8 via the line 10.
  • the pressure occurring there is in the range around 160 bar. Sealing of the actuating line 1 against the outlet 41 is ensured, namely two sealing points connected in series are used for this.
  • the first sealing point is always a slide valve, for example between connections 45 and 46 in valve 2, and the second sealing point connected in series, for example between connections 56 and 55 in valve 4, is always a seat valve.
  • the poppet valve must also withstand the full pressure applied by the test system 14.
  • the actuation line 1 is supplied with oil under pressure via the lines 70, 71 and 72.
  • This arrangement has the advantage that no oil is lost in the drain 41 when the oil pressure is raised in this hydraulic device.
  • the lines 70, 71, 72 can advantageously be accommodated inside the valves 2, 3, 4, so that additional lines, screw connections and sealing points are omitted, which increases safety.
  • the other function of the device according to FIG. 2 corresponds to that of the device according to FIG. 1.
  • FIG. 3 shows the so-called "fail safe” position of the device.
  • the solenoid valves 25, 26, 27 and the valves 2, 3, 4 have reached their rest position. In this position, the oil flows under pressure from the actuation line 1 into the outlet 41, both through the line that connects the actuation line 1 to the connection 45 of the valve 2 and through the corresponding lines that lead to the connections 49 or 53 of the valves 3 or 4 and through the second valve seat connected in series.
  • the feed valve closes with great certainty, so that the turbine fed by this feed valve cannot reach an uncontrollable operating state.
  • the check valves 61, 62, 63 the pressure escapes from the test system 14 at the same time, so that the pressure switch 16 also reports to the higher-level system control system that this unit has shut down.
  • the device works properly when all valves 2, 3, 4 and all solenoid valves 25, 26, 27 are fully functional, as previously described. However, it can now happen that a module of this unit fails. In this case, as shown in FIG. 4, proper functioning of the drive is also ensured.
  • the pressure in the actuation line 1 is maintained even after the valve 2 has been shut off, so that the feed valve remains open. Only the pressure in the test system 14 is somewhat reduced by the check valve 62, since the make-up through line 12 is too weak to maintain the full pressure when one of the check valves 61, 62, 63 opens.
  • the pressure switch 16 reports in In this case, a pressure drop in the test system 14, which is to be regarded as an indication of a malfunction in the device. A control of the device and its components is necessary, which leads to the finding of the defective parts and their repair. Continuous, trouble-free operation of the drive is guaranteed during this maintenance period.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
  • Fluid-Driven Valves (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Control Of Fluid Pressure (AREA)

Abstract

This drive for a supply valve has an operating line (1) and a device for controlling the pressure in the operating line (1). The device comprises three valves (2, 3, 4) which are connected to one another to form a hydraulic 2-of-3 circuit. <??>It is intended to create a drive for a supply valve, which is suitable for a comparatively high oil pressure and whose functional capability can be monitored by simple means. This is achieved by it being possible to apply pressure to a test system (14) via the device, and by it being possible to detect a pressure drop in the test system by means of a sensor. <IMAGE>

Description

TECHNISCHES GEBIETTECHNICAL AREA

Die Erfindung geht aus von einem Antrieb für ein Speiseventil mit einer hydraulisch druckbeaufschlagten Betätigungsleitung und mit einer Einrichtung zur Steuerung des Drucks in der Betätigungsleitung, welche drei miteinander zu einer hydraulischen 2 von 3-Schaltung verbundene Ventile aufweist.The invention relates to a drive for a feed valve with a hydraulically pressurized actuation line and with a device for controlling the pressure in the actuation line, which has three valves connected to one another to form a hydraulic 2-by-3 circuit.

STAND DER TECHNIKSTATE OF THE ART

Aus der Patentschrift CH 666 132 ist ein Antrieb für ein Speiseventil bekannt. Dieser Antrieb, der mit Öl unter vergleichsweise niedrigem Druck betrieben wird, betätigt beispielsweise ein Schnellschlussventil, welches als Speiseventil für die Dampfeinspeisung einer Turbine dient. Das Öl unter Druck oder eine andere hydraulische Flüssigkeit wirkt über eine Betätigungsleitung auf den Antrieb ein, sodass dieser das Speiseventil öffnen oder schliessen kann. Der Druck in der Betätigungsleitung wird über eine Einrichtung gesteuert, welche drei miteinander zu einer hydraulischen 2 von 3-Schaltung verbundene Ventile aufweist. Diese Ventile sind als elektromagnetisch betätigte Schieberventile ausgebildet und jedes wird separat auf seine Funktionsfähigkeit überwacht, sodass drei Überwachungskreise nötig sind. Diese Überwachungskreise weisen mechanische Kontakte auf, die der Wartung bedürfen. Für den Einsatz bei höheren Drücken ist diese Einrichtung weniger geeignet.A drive for a feed valve is known from the patent specification CH 666 132. This drive, which is operated with oil at comparatively low pressure, actuates, for example, a quick-closing valve, which serves as a feed valve for the steam feed of a turbine. The oil under pressure or another hydraulic fluid acts on the actuator via an actuation line so that it can open or close the feed valve. The pressure in the actuation line is controlled by a device which has three valves connected to one another to form a hydraulic 2 by 3 circuit. These valves are designed as electromagnetically operated slide valves and each is monitored separately for its functionality, so that three monitoring circuits are necessary. These monitoring circuits have mechanical contacts that require maintenance. This device is less suitable for use at higher pressures.

DARSTELLUNG DER ERFINDUNGPRESENTATION OF THE INVENTION

Hier will die Erfindung Abhilfe schaffen. Die Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, löst die Aufgabe, einen Antrieb für ein Speiseventil zu schaffen, der für vergleichsweise hohen Druck des antreibenden Öls geeignet ist und dessen Funktionsfähigkeit mit einfachen Mitteln überwacht werden kann.The invention seeks to remedy this. The invention, as characterized in the claims, solves the problem of creating a drive for a feed valve which is suitable for a comparatively high pressure of the driving oil and whose functionality can be monitored with simple means.

Die durch die Erfindung erreichten Vorteile sind im wesentlichen darin zu sehen, dass mit höheren Öldrücken eine bessere Dynamik des Antriebs erreicht werden kann. Ein kompakter Aufbau des Antriebs ist möglich. Die Überwachung der Funktionsfähigkeit kann einfacher und weniger störungsanfällig erfolgen, da hierfür keine mechanischen Kontakte benötigt werden.The advantages achieved by the invention are essentially to be seen in the fact that better drive dynamics can be achieved with higher oil pressures. A compact structure of the drive is possible. The functionality can be monitored more easily and less prone to failure, since no mechanical contacts are required for this.

Die weiteren Ausgestaltungen der Erfindung sind Gegenstände der abhängigen Ansprüche.The further developments of the invention are the subject of the dependent claims.

Die Erfindung, ihre Weiterbildung und die damit erzielbaren Vorteile werden nachstehend anhand der Zeichnung, welche lediglich einen möglichen Ausführungsweg darstellt, näher erläutert.The invention, its further development and the advantages which can be achieved thereby are explained in more detail below with reference to the drawing, which only represents one possible embodiment.

KURZE BESCHREIBUNG DER ZEICHNUNGBRIEF DESCRIPTION OF THE DRAWING

Es zeigen:

Fig.1
eine erste Prinzipskizze eines Teiles des Antriebs,
Fig.2
eine zweite Prinzipskizze eines Teiles des Antriebs,
Fig.3
eine dritte Prinzipskizze eines Teiles des Antriebs,
Fig.4
eine vierte Prinzipskizze eines Teiles des Antriebs, und
Fig. 5
eine Prinzipskizze eines Ventils.
Show it:
Fig. 1
a first schematic diagram of part of the drive,
Fig. 2
a second schematic diagram of part of the drive,
Fig. 3
a third schematic diagram of part of the drive,
Fig. 4
a fourth sketch of a part of the drive, and
Fig. 5
a schematic diagram of a valve.

Bei allen Figuren sind gleich wirkende Elemente mit gleichen Bezugszeichen versehen.Elements with the same effect are provided with the same reference symbols in all the figures.

WEGE ZUR AUSFÜHRUNG DER ERFINDUNGWAYS OF CARRYING OUT THE INVENTION

Die Figur 1 zeigt eine Prinzipskizze eines Teiles des Antriebs, und zwar ist der Teil dargestellt, welcher eine Einrichtung zur Steuerung des Drucks in einer Betätigungsleitung 1 umfasst. Als Medium zur Übertragung dieses Druckes wird in der Regel Öl verwendet, es kann jedoch auch eine andere Hydraulikflüssigkeit oder auch ein gasförmiges Medium hierfür eingesetzt werden. Über diese Betätigungsleitung 1 wird eine nicht dargestellte Zylinder-Kolbenanordnung des Antriebs betätigt, welche das zugehörige, ebenfalls nicht dargestellte Speiseventil öffnet oder schliesst. In der Regel wird bei voll anstehendem Druck in der Betätigungsleitung 1 dieses Speiseventil offen sein und sobald der Druck abfällt, wird es rasch schliessen.FIG. 1 shows a schematic diagram of a part of the drive, namely the part that includes a device for controlling the pressure in an actuation line 1. Oil is generally used as the medium for transmitting this pressure, but another hydraulic fluid or a gaseous medium can also be used for this. Via this actuation line 1, a cylinder-piston arrangement of the drive, not shown, is actuated, which opens or closes the associated feed valve, also not shown. As a rule, this feed valve will be open when the pressure in the actuating line 1 is fully present and as soon as the pressure drops, it will close quickly.

Diese Einrichtung zur Steuerung des Drucks weist drei zu einer hydraulischen 2 von 3-Schaltung zusammengeschaltete, baugleiche Ventile 2, 3 und 4 auf. Durch einen Zulauf 8 gelangt das durch eine nicht dargestellte Pumpe mit Druck beaufschlagte Öl in diese Einrichtung. Dabei werden Drücke im Bereich um 160 bar angewendet. Vom Zulauf 8 wird hier über eine mit einer Blende 9 versehene Leitung 10 Öl unter Druck direkt in die Betätigungsleitung 1 eingespeist, wobei die Blende 9 die Durchflussmenge des Öls bestimmt. Eine weitere, mit einer Blende 11 versehene Leitung 12 speist eine geringe Menge Öl unter Druck in eine Leitung 13 eines Prüfsystems 14 ein. Die Leitung 13 speist über ein Absperrorgan 15 einen Druckwächter 16 an. Das Absperrorgan 15 wird in der Regel nur geschlossen, wenn der Druckwächter 16 revidiert wird. Der Druckwächter 16 kann beispielsweise ein piezoelektrisches Messglied enthalten, welches ohne mechanische Kontaktgabe und deshalb praktisch wartungsfrei arbeitet. Der Druckwächter 16 spricht bei Unterschreitung eines eingestellten Mindestdruckwertes an und gibt ein elektrisches Signal an eine nicht dargestellte, übergeordnete Anlagenleittechnik ab, wo dieses Signal weiterverarbeitet wird.This device for controlling the pressure has three identical valves 2, 3 and 4 which are interconnected to form a hydraulic 2 by 3 circuit. Through an inlet 8, the oil pressurized by a pump, not shown, reaches this device. Pressures in the range around 160 bar are used. From the inlet 8, oil is fed under pressure directly into the actuating line 1 via a line 10 provided with an orifice 9, the Aperture 9 determines the flow rate of the oil. Another line 12 provided with an orifice 11 feeds a small amount of oil under pressure into a line 13 of a test system 14. The line 13 feeds a pressure switch 16 via a shut-off device 15. The shut-off device 15 is usually only closed when the pressure switch 16 is revised. The pressure switch 16 can contain, for example, a piezoelectric measuring element which works without mechanical contact and therefore practically maintenance-free. The pressure switch 16 responds when the pressure falls below a set minimum value and emits an electrical signal to a higher-level plant control system, not shown, where this signal is processed further.

Über drei weitere, mit jeweils einer durchflussbegrenzenden Blende 17, 18 und 19 versehenen, Leitungen 20, 21 und 22 werden vom Zulauf 8 her jeweils drei Magnetventile 25, 26 und 27 angespeist. In Fig. 1 sind die Magnetventile 25, 26, 27 magnetisch erregt dargestellt, bei einem Ausfall der elektrischen Energie oder bei einer Absteuerung derselben, werden die Magnetventile 25, 26, 27 durch jeweils eine schematisch angedeutete Feder 28, 29 und 30 in eine zweite skizzenhaft dargestellte Stellung gedrückt. Als Magnetventile 25, 26, 27 können beispielsweise Sitzventile vom Typ M-SEW6 der Firma Mannesmann Rexroth G.m.b.H., D 8770 Lohr a.M., eingesetzt werden. In der gezeichneten Stellung fliesst das Öl unter Druck durch die Magnetventile 25, 26, 27 durch in jeweils eine Leitung 31, 32 und 33, welche in jeweils ein schematisch dargestelltes Antriebsvolumen 34, 35 und 36 der Ventile 2, 3, 4 führt. Das Antriebsvolumen 34 ist dem Ventil 2, das Antriebsvolumen 35 dem Ventil 3 und das Antriebsvolumen 36 dem Ventil 4 zugeordnet. Jeweils ein weiterer Ausgang 37, 38 und 39 der Magnetventile 25, 26, 27 ist über eine gemeinsame Leitung 40 mit einem Ablauf 41 verbunden. In der gezeichneten Ventilstellung werden die Ausgänge 37, 38, 39 jedoch nicht von Öl durchflossen.Via three further lines 20, 21 and 22, each provided with a flow-restricting orifice 17, 18 and 19, three solenoid valves 25, 26 and 27 are fed from the inlet 8. In Fig. 1, the solenoid valves 25, 26, 27 are shown magnetically excited, in the event of a failure of the electrical energy or a shutdown of the same, the solenoid valves 25, 26, 27 are each by a schematically indicated spring 28, 29 and 30 in a second position shown sketched pressed. Solenoid valves 25, 26, 27, for example, seat valves of the type M-SEW6 from Mannesmann Rexroth GmbH, D 8770 Lohr aM, can be used. In the position shown, the oil flows under pressure through the solenoid valves 25, 26, 27 through in each case a line 31, 32 and 33 which leads into a schematically illustrated drive volume 34, 35 and 36 of the valves 2, 3, 4. The drive volume 34 is assigned to the valve 2, the drive volume 35 to the valve 3 and the drive volume 36 to the valve 4. In each case another output 37, 38 and 39 of the solenoid valves 25, 26, 27 is connected to an outlet 41 via a common line 40. In the drawn valve position, however, the outlets 37, 38, 39 are not traversed by oil.

Die Ventile 2, 3, 4 sind als Doppelventile ausgebildet, und zwar weisen sie jeweils ein Sitzventil und ein Schieberventil auf, die Bauart wird später im Zusammenhang mit Fig. 5 näher erläutert. Die Ventile 2, 3, 4 sind in Fig. 1 mit jeweils druckbeaufschlagten Antriebsvolumen 34, 35, 36 dargestellt, sollte die Versorgung mit Öl unter Druck durch die jeweiligen Leitungen 31, 32, 33 entfallen, so werden die Ventile 2, 3, 4 jeweils durch starke Federn 42, 43 und 44 in eine zweite, in Fig. 1 dargestellte Schaltstellung gedrückt. Damit ist sichergestellt, dass die Ventile auch im Falle einer etwaigen Störung stets eine definierte Schaltstellung einnehmen. Jedes der Ventile 2, 3, 4 weist neben der das jeweilige Antriebsvolumen 34, 35, 36 speisenden Leitung 31, 32, 33 vier weitere Anschlüsse für Ölleitungen auf. Das Ventil 2 weist die Anschlüsse 45, 46, 47 und 48 auf. Das Ventil 3 weist die Anschlüsse 49, 50, 51 und 52 auf. Das Ventil 4 weist die Anschlüsse 53, 54, 55 und 56 auf.The valves 2, 3, 4 are designed as double valves, each having a seat valve and a slide valve, the type will be explained in more detail later in connection with FIG. 5. Valves 2, 3, 4 are shown in FIG. 1, each with pressurized drive volume 34, 35, 36; if the supply of oil under pressure through the respective lines 31, 32, 33 is omitted, valves 2, 3, 4 each pressed by strong springs 42, 43 and 44 into a second switching position shown in FIG. 1. This ensures that the valves always assume a defined switching position even in the event of a malfunction. In addition to the line 31, 32, 33 feeding the respective drive volume 34, 35, 36, each of the valves 2, 3, 4 has four further connections for oil lines. The valve 2 has the connections 45, 46, 47 and 48. The valve 3 has the connections 49, 50, 51 and 52. The valve 4 has the connections 53, 54, 55 and 56.

Der Anschluss 45 des Ventils 2 ist mit der Betätigungsleitung 1 verbunden und durch ein schematisch angedeutetes Schieberventil vom Anschluss 46 getrennt. Der Anschluss 46 ist über eine Leitung 60, in welcher ein Rückschlagventil 61 angebracht ist, mit der Leitung 13 des Prüfsystem 14 verbunden. Das Rückschlagventil 61 ist so angeordnet, dass eine Ölströmung aus dem Prüfsystem 14 heraus möglich ist. Der Anschluss 47 ist mit dem Ablauf 41 verbunden. Zwischen den Anschlüssen 47 und 48 ist im Innern des Ventils 2 das Schaltsymbol für ein Sitzventil eingezeichnet. Zwischen den beiden Anschlüssen 47 und 48 ist in dieser Schaltstellung nach beiden Richtungen kein Öldurchlass möglich, da stets auf der Seite des Ablaufs 41 ein niedrigerer Druck herrscht. Der Anschluss 48 ist über ein Rückschlagventil 62 mit der Leitung 13 des Prüfsystems 14 verbunden. Das Rückschlagventil 62 lässt eine Ölströmung aus dem Prüfsystem 14 heraus zu.The connection 45 of the valve 2 is connected to the actuation line 1 and separated from the connection 46 by a schematically indicated slide valve. The connection 46 is connected to the line 13 of the test system 14 via a line 60, in which a check valve 61 is attached. The check valve 61 is arranged such that an oil flow out of the test system 14 is possible. The connection 47 is connected to the outlet 41. Between the connections 47 and 48, the switching symbol for a seat valve is drawn inside the valve 2. In this switching position, no oil passage is possible between the two connections 47 and 48 in both directions, since there is always a lower pressure on the side of the drain 41. The connection 48 is connected to the line 13 of the test system 14 via a check valve 62. Check valve 62 allows oil flow out of test system 14.

Der Anschluss 49 des Ventils 3 ist mit der Betätigungsleitung 1 verbunden und er ist durch ein angedeutetes Schieberventil vom Anschluss 50 getrennt. Der Anschluss 50 ist mit dem Anschluss 48 des Ventils 2 und gleichzeitig über das Rückschlagventil 62 mit dem Prüfsystem 14 verbunden. Der Anschluss 51 ist mit dem Ablauf 41 verbunden. Zwischen den Anschlüssen 51 und 52 ist in dieser Schaltstellung die Verbindung durch ein angedeutetes Sitzventil gesperrt. Der Anschluss 52 ist über ein Rückschlagventil 63 mit der Leitung 13 des Prüfsystems 14 verbunden. Das Rückschlagventil 63 lässt eine Ölströmung aus dem Prüfsystem 14 heraus zu.The connection 49 of the valve 3 is connected to the actuation line 1 and it is separated from the connection 50 by an indicated slide valve. The connection 50 is connected to the connection 48 of the valve 2 and at the same time to the test system 14 via the check valve 62. The connection 51 is connected to the outlet 41. In this switching position, the connection between the connections 51 and 52 is blocked by an indicated seat valve. The connection 52 is connected to the line 13 of the test system 14 via a check valve 63. The check valve 63 allows an oil flow out of the test system 14.

Der Anschluss 53 des Ventils 4 ist mit der Betätigungsleitung 1 verbunden und er ist durch ein angedeutetes Schieberventil vom Anschluss 54 getrennt. Der Anschluss 54 ist mit dem Anschluss 52 des Ventils 3 und gleichzeitig über das Rückschlagventil 63 mit dem Prüfsystem 14 verbunden. Der Anschluss 55 ist mit dem Ablauf 41 verbunden. Zwischen den Anschlüssen 55 und 56 ist in dieser Schaltstellung die Verbindung durch ein angedeutetes Sitzventil gesperrt. Der Anschluss 56 mündet vor dem Rückschlagventil 61 in die Leitung 60 ein, sodass der Anschluss 56 über dieses Rückschlagventil 61 mit dem Prüfsystem 14 in Wirkverbindung steht.The connection 53 of the valve 4 is connected to the actuation line 1 and it is separated from the connection 54 by an indicated slide valve. The connection 54 is connected to the connection 52 of the valve 3 and at the same time to the test system 14 via the check valve 63. The connection 55 is connected to the outlet 41. In this switching position, the connection between the connections 55 and 56 is blocked by an indicated seat valve. The connection 56 opens before the check valve 61 into the line 60, so that the connection 56 is operatively connected to the test system 14 via this check valve 61.

Die Prinzipskizze gemäss Fig. 2 unterscheidet sich von der Fig. 1 lediglich dadurch, dass die Leitung 10 und die Blende 9 ersetzt werden durch drei Leitungen 70, 71 und 72. Auf die Vorteile dieser Anordnung wird später eingegangen. Die Leitung 70 verbindet die Leitung 31 mit dem Anschluss 45 des Ventils 2 und gleichzeitig mit der Betätigungsleitung 1. In die Leitung 70 ist ein Rückschlagventil 73 eingebaut, welches eine Ölströmung von der Leitung 31 her in Richtung Betätigungsleitung 1 erlaubt, wobei die Menge des strömenden Öls durch eine gleichfalls in der Leitung 70 vorgesehene Blende 74 begrenzt wird. Die Leitung 71 verbindet die Leitung 32 mit dem Anschluss 49 des Ventils 3 und gleichzeitig mit der Betätigungsleitung 1. In die Leitung 71 ist ein Rückschlagventil 75 eingebaut und eine Blende 76, sodass eine Ölströmung von der Leitung 32 her in Richtung Betätigungsleitung 1 möglich ist. Die Leitung 72 verbindet die Leitung 33 mit dem Anschluss 53 des Ventils 4 und gleichzeitig mit der Betätigungsleitung 1. In die Leitung 72 ist ein Rückschlagventil 77 eingebaut und eine Blende 78, sodass eine Ölströmung von der Leitung 33 her in Richtung Betätigungsleitung 1 möglich ist.The schematic diagram according to FIG. 2 differs from FIG. 1 only in that the line 10 and the cover 9 are replaced by three lines 70, 71 and 72. The advantages of this arrangement will be discussed later. The line 70 connects the line 31 to the connection 45 of the valve 2 and at the same time to the actuating line 1. A check valve 73 is installed in the line 70, which allows an oil flow from the line 31 in the direction of the actuating line 1, the amount of the flowing Oil is limited by an aperture 74 also provided in line 70. Line 71 connects the line 32 with the connection 49 of the valve 3 and at the same time with the actuation line 1. A check valve 75 and an orifice 76 are installed in the line 71, so that an oil flow from the line 32 in the direction of the actuation line 1 is possible. The line 72 connects the line 33 to the connection 53 of the valve 4 and at the same time to the actuation line 1. A check valve 77 and an orifice 78 are installed in the line 72, so that an oil flow from the line 33 in the direction of the actuation line 1 is possible.

Die Prinzipskizze gemäss Fig. 3 entspricht der Skizze gemäss Fig. 2, lediglich die Magnetventile 25, 26, 27 weisen eine zweite Schaltstellung auf und infolgedessen auch die durch sie betätigten Ventile 2, 3 und 4. Die Magnetventile 25, 26, 27 sind hier in der Schaltstellung dargestellt in welche sie durch die jeweiligen Federn 28, 29, 30 gedrückt werden, wenn die elektrische Energie für die magnetische Erregung ausfällt oder abgesteuert wird. Die drei Leitungen 31, 32 und 33 werden durch die Magnetventile 25, 26, 27 und die Leitung 40 zum Ablauf 41 hin entlastet vom Öldruck und damit werden auch die drei Antriebsvolumina 34, 35, 34 geleert und die Federn 42, 43, 44 drücken die Ventile 2, 3, 4 in die in Fig. 3 gezeichnete Schaltstellung.3 corresponds to the sketch according to FIG. 2, only the solenoid valves 25, 26, 27 have a second switching position and consequently also the valves 2, 3 and 4 actuated by them. The solenoid valves 25, 26, 27 are here shown in the switch position in which they are pressed by the respective springs 28, 29, 30 when the electrical energy for the magnetic excitation fails or is deactivated. The three lines 31, 32 and 33 are relieved of the oil pressure by the solenoid valves 25, 26, 27 and the line 40 to the outlet 41 and thus the three drive volumes 34, 35, 34 are emptied and the springs 42, 43, 44 press the valves 2, 3, 4 in the switching position shown in Fig. 3.

Die Skizze Fig. 4 zeigt einen möglichen Betriebszustand der Einrichtung. Die Ventile 3 und 4 sind wie in Fig. 2 geschaltet, das Ventil 2 ist analog der Fig. 3 geschaltet. Diese Stellung des Ventils 2 kann bewusst erzeugt worden sein durch ein Absteuern der Energie für die magnetische Erregung des zugehörigen Magnetventils 25, wodurch, wie bereits beschrieben, das Antriebsvolumen 34 druckentlastet wird, was zur Folge hat, dass die Feder 42 das Ventil 2 in die gezeichente Schaltstellung drückt, es ist jedoch auch möglich, dass eine echte Störung vorliegt, welche beispielsweise die Energiezufuhr unterbrochen hat. Ein bewusstes Absteuern der Energie würde vorgenommen, wenn beispielsweise eine Funktionskontrolle des Ventils 2 durchgeführt werden soll.The sketch in FIG. 4 shows a possible operating state of the device. The valves 3 and 4 are switched as in FIG. 2, the valve 2 is switched analogously to FIG. 3. This position of the valve 2 may have been deliberately created by controlling the energy for the magnetic excitation of the associated solenoid valve 25, as a result of which, as already described, the drive volume 34 is relieved of pressure, with the result that the spring 42 pushes the valve 2 into the presses the switch position shown, but it is also possible that there is a real malfunction which, for example, has interrupted the energy supply. A conscious one The energy would be cut off if, for example, a functional check of the valve 2 is to be carried out.

Die Fig. 5 zeigt eine Prinzipskizze des Ventils 2, wobei die Ventile 3 und 4 baugleich ausgeführt sind, die Schaltstellung ist gleich wie in der Fig. 2 gezeigt. Das Ventil 2 ist in einer zylindrischen Bohrung 80 eines hydraulischen Blockes, der auch die Ventile 3 und 4 umfasst, angeordnet. Die Leitung 31 führt in das zylindrische Antriebsvolumen 34. Der Druck des Öles im Antriebsvolumen 34 wirkt auf einen Kolben 81, der in der Bohrung 80 verschieblich angeordnet ist. Der Kolben 81 ist einstückig ausgebildet, er weist zwei Dichtstellen auf, nämlich eine Dichtkante 82, die mit einer Kante 83 der Bohrung 80 zusammenwirkt, wenn sich der Kolben 81 nach oben bewegt, und einen Dichtungssitz 84. Das Ventil 2 weist im oberen Teil demnach ein Schieberventil mit der Dichtkante 82 zwischen den Anschlüssen 45 und 46 auf und im unteren Teil weist es ein Sitzventil mit dem Dichtungssitz 84 zwischen den Anschlüssen 47 und 48 auf. Beim Öffnen des Ventils 2, also wenn sich der Kolben 81 nach oben bewegt, wirkt es sich als vorteilhaft aus, dass das Überfahren der Kante 83 durch die Dichtkante 82 eine Ventilöffnung des Schieberventils bewirkt ohne eine nennenswerte Volumenänderung zu verursachen, die in den benachbarten Volumina und Leitungen zu unzulässigen Druckschwankungen und dadurch verursachte Fehlbetätigungen des Antriebs führen könnte. Im unteren Teil der Skizze ist die Feder 42 angedeutet, die nach einem Druckabfall im Antriebsvolumen 34 den Kolben 81 nach oben in eine definierte Offenstellung schiebt. Die Feder 42 stützt sich gegen einen Support 85 ab.FIG. 5 shows a schematic diagram of the valve 2, the valves 3 and 4 being constructed identically, the switching position being the same as that shown in FIG. 2. The valve 2 is arranged in a cylindrical bore 80 of a hydraulic block, which also includes the valves 3 and 4. The line 31 leads into the cylindrical drive volume 34. The pressure of the oil in the drive volume 34 acts on a piston 81 which is arranged displaceably in the bore 80. The piston 81 is formed in one piece, it has two sealing points, namely a sealing edge 82 which cooperates with an edge 83 of the bore 80 when the piston 81 moves upwards, and a sealing seat 84. The valve 2 accordingly has in the upper part a slide valve with the sealing edge 82 between the connections 45 and 46 and in the lower part it has a seat valve with the sealing seat 84 between the connections 47 and 48. When the valve 2 is opened, i.e. when the piston 81 moves upward, it has an advantageous effect that passing the edge 83 through the sealing edge 82 brings about a valve opening of the slide valve without causing a significant change in volume that occurs in the adjacent volumes and lines could lead to impermissible pressure fluctuations and the resulting incorrect actuation of the drive. In the lower part of the sketch, the spring 42 is indicated, which pushes the piston 81 upwards into a defined open position after a pressure drop in the drive volume 34. The spring 42 is supported against a support 85.

Zur Erläuterung der Wirkungsweise sei die Fig. 1 näher betrachtet. Die Ventile 2, 3, 4 und die Magnetventile 25, 26, 27 arbeiten einwandfrei und die Betätigungsleitung 1 steht unter Druck, sodass das Speiseventil offengehalten wird. Der störungsfreie Normalbetrieb ist gewährleistet. Öl wird in der Betätigungsleitung 1 unter Druck gehalten vom Zulauf 8 her über die Leitung 10. Der dort auftretende Druck liegt im Bereich um 160 bar. Eine Abdichtung der Betätigungsleitung 1 gegen den Ablauf 41 ist sichergestellt, und zwar werden zwei in Reihe geschaltete Dichtungsstellen hierfür eingesetzt. Die erste Dichtungsstelle ist stets ein Schieberventil, beispielsweise zwischen den Anschlüssen 45 und 46 im Ventil 2, und die in Reihe geschaltete zweite Dichtungsstelle, beispielsweise zwischen den Anschlüssen 56 und 55 im Ventil 4, ist stets ein Sitzventil. Das Sitzventil muss jeweils auch dem vollen Druck standhalten, der vom Prüfsystem 14 her ansteht. Für derartig hohe Drücke ist es vorteilhaft ein Sitzventil einzusetzen, da bei diesem Ventiltyp eine etwaige Ölzersetzung keine negativen Auswirkungen auf das Funktionsvermögen des Ventils mit sich bringt. Das Schieberventil ist jeweils nicht so hoch beansprucht, sodass auch hier keine negativen Auswirkungen einer Ölzersetzung zu befürchten sind. Das Prüfsystem 14 wird durch den Druckwächter 16 überwacht, der erst bei Unterschreitung eines Druckschwellwertes anspricht und Signal gibt.To explain the mode of operation, FIG. 1 is considered in more detail. The valves 2, 3, 4 and the solenoid valves 25, 26, 27 work perfectly and the actuating line 1 is under pressure, so that the feed valve is kept open. Trouble-free normal operation is guaranteed. Oil is kept under pressure in the actuation line 1 from the inlet 8 via the line 10. The pressure occurring there is in the range around 160 bar. Sealing of the actuating line 1 against the outlet 41 is ensured, namely two sealing points connected in series are used for this. The first sealing point is always a slide valve, for example between connections 45 and 46 in valve 2, and the second sealing point connected in series, for example between connections 56 and 55 in valve 4, is always a seat valve. The poppet valve must also withstand the full pressure applied by the test system 14. For such high pressures, it is advantageous to use a seat valve, since with this type of valve any oil decomposition has no negative effects on the functionality of the valve. The slide valve is not so heavily stressed, so that there are no negative effects of oil decomposition to fear. The test system 14 is monitored by the pressure monitor 16, which only responds and signals when a pressure threshold is undershot.

In Fig. 2 wird die Betätigungsleitung 1 über die Leitungen 70, 71 und 72 mit Öl unter Druck versorgt. Diese Anordnung hat den Vorteil, dass beim Hochfahren des Öldrucks in dieser hydraulischen Einrichtung kein Öl in den Ablauf 41 verloren geht. Ferner können die Leitungen 70, 71, 72, wie Fig. 5 zeigt, vorteilhaft im Innern der Ventile 2, 3, 4 untergebracht werden, sodass zusätzliche Leitungen, Verschraubungen und Dichtstellen entfallen, was die Sicherheit erhöht. Die übrige Funktion der Einrichtung gemäss Fig. 2 entspricht der der Einrichtung gemäss Fig. 1.2, the actuation line 1 is supplied with oil under pressure via the lines 70, 71 and 72. This arrangement has the advantage that no oil is lost in the drain 41 when the oil pressure is raised in this hydraulic device. Furthermore, as shown in FIG. 5, the lines 70, 71, 72 can advantageously be accommodated inside the valves 2, 3, 4, so that additional lines, screw connections and sealing points are omitted, which increases safety. The other function of the device according to FIG. 2 corresponds to that of the device according to FIG. 1.

In Fig. 3 ist die sogenannte "fail safe"-Stellung der Einrichtung dargestellt. Die Magnetventile 25, 26, 27 und die Ventile 2, 3, 4 sind in ihrer Ruhestellung angelangt. In dieser Stellung fliesst das Öl unter Druck aus der Betätigungsleitung 1 in den Ablauf 41 ab, und zwar sowohl durch die Leitung, welche die Betätigungsleitung 1 mit dem Anschluss 45 des Ventils 2 verbindet, als auch durch die entsprechenden Leitungen, die zu den Anschlüssen 49 bzw. 53 der Ventile 3 bzw. 4 führen und durch den jeweils in Reihe geschalteten zweiten Ventilsitz hindurch. Das Speiseventil schliesst mit grosser Sicherheit, sodass die durch dieses Speiseventil gespeiste Turbine keinen unkontrollierbaren Betriebszustand erreichen kann. Durch die Rückschlagventile 61, 62, 63 entweicht gleichzeitig der Druck aus dem Prüfsystem 14, sodass auch der Druckwächter 16 an das übergeordnete Anlagenleitsystem meldet, dass diese Einheit heruntergefahren ist. Diese "fail safe"-Stellung wird immer erreicht, da die Federn 42, 43, 44 der Ventile 2, 3, 4 und die Federn 28, 29, 30 der Magnetventile 25, 26, 27 eine grosse mechanische Kraftreserve beinhalten, die diese Ventile mit grosser Sicherheit in die gezeichneten Stellungen drückt, wenn der Öldruck gesamthaft abfällt oder für eine Abschaltung abgesteuert wird.3 shows the so-called "fail safe" position of the device. The solenoid valves 25, 26, 27 and the valves 2, 3, 4 have reached their rest position. In this position, the oil flows under pressure from the actuation line 1 into the outlet 41, both through the line that connects the actuation line 1 to the connection 45 of the valve 2 and through the corresponding lines that lead to the connections 49 or 53 of the valves 3 or 4 and through the second valve seat connected in series. The feed valve closes with great certainty, so that the turbine fed by this feed valve cannot reach an uncontrollable operating state. Through the check valves 61, 62, 63, the pressure escapes from the test system 14 at the same time, so that the pressure switch 16 also reports to the higher-level system control system that this unit has shut down. This "fail safe" position is always achieved because the springs 42, 43, 44 of the valves 2, 3, 4 and the springs 28, 29, 30 of the solenoid valves 25, 26, 27 contain a large mechanical force reserve which these valves presses with great certainty into the positions shown if the total oil pressure drops or is deactivated for a shutdown.

Die Einrichtung arbeitet einwandfrei, wenn alle Ventile 2, 3, 4 und alle Magnetventile 25, 26, 27 voll funktionsfähig sind, wie bisher beschrieben. Es kann nun jedoch der Fall eintreten, dass eine Baugruppe dieser Einheit ausfällt. In diesem Fall ist, wie Fig. 4 zeigt, ein einwandfreies Funktionieren des Antriebs ebenfalls sichergestellt. Der Druck in der Betätigungsleitung 1 wird auch nach dem Absteuern des Ventils 2 aufrecht erhalten, sodass das Speiseventil geöffnet bleibt. Lediglich der Druck im Prüfsystem 14 wird durch das Rückschlagventil 62 etwas reduziert, da die Nachspeisung durch die Leitung 12 zu schwach ist, um den vollen Druck aufrecht zu erhalten, wenn sich eines der Rückschlagventile 61, 62, 63 öffnet. Der Druckwächter 16 meldet in diesem Fall einen Druckabfall im Prüfsystem 14, welcher als Indiz für eine Störung in der Einrichtung zu betrachten ist. Eine Kontrolle der Einrichtung und ihrer Bauelemente ist nötig, welche zum Auffinden der defekten Teile und deren Reperatur führt. Während dieser Wartungsperiode ist ein durchgehender, einwandfreier Betrieb des Antriebs gewährleistet.The device works properly when all valves 2, 3, 4 and all solenoid valves 25, 26, 27 are fully functional, as previously described. However, it can now happen that a module of this unit fails. In this case, as shown in FIG. 4, proper functioning of the drive is also ensured. The pressure in the actuation line 1 is maintained even after the valve 2 has been shut off, so that the feed valve remains open. Only the pressure in the test system 14 is somewhat reduced by the check valve 62, since the make-up through line 12 is too weak to maintain the full pressure when one of the check valves 61, 62, 63 opens. The pressure switch 16 reports in In this case, a pressure drop in the test system 14, which is to be regarded as an indication of a malfunction in the device. A control of the device and its components is necessary, which leads to the finding of the defective parts and their repair. Continuous, trouble-free operation of the drive is guaranteed during this maintenance period.

Es ist auch möglich entsprechende vorsorgliche Wartungsarbeiten durchzuführen, indem der Reihe nach bewusst jeweils eines der Ventile 2, 3, 4 über das entsprechende Magnetventil 25, 25, 27 abgesteuert und separaten Funktionskontrollen unterworfen wird, ohne dass der Betrieb des Antriebs negativ beeinflusst wird. Die Verfügbarkeit der Einrichtung ist dadurch als vergleichsweise hoch einzustufen.It is also possible to carry out corresponding precautionary maintenance work by deliberately switching off one of the valves 2, 3, 4 via the corresponding solenoid valve 25, 25, 27 and subjecting them to separate function checks without adversely affecting the operation of the drive. The availability of the facility can therefore be classified as comparatively high.

Sobald jedoch zwei Zweige der Einrichtung gestört sind, z.B. das Ventil 2 und das Magnetventil 26, so werden das Ventil 2 und das Ventil 3 in ihre Ruhestellung gedrückt, und der Druck in der Betätigungsleitung 1 wird durch die Leitung, welche den Anschluss 49 des Ventils 3 mit der Betätigungsleitung 1 verbindet, völlig abgebaut in Richtung Ablauf 41. Das Speiseventil schliesst infolgedessen, und erst nach der Behebung der Störungen ist eine Wiederinbetriebnahme der Einrichtung möglich. Ebenso meldet der Druckwächter 16 einen starken Druckabfall im Prüfsystem 14, sodass die übergeordnete Anlagenleittechnik ein Abfahren der Gesamtanlage einleiten kann.However, as soon as two branches of the device are disturbed, e.g. the valve 2 and the solenoid valve 26, the valve 2 and the valve 3 are pressed into their rest position, and the pressure in the actuation line 1 is completely reduced in the line which connects the connection 49 of the valve 3 to the actuation line 1 Direction of sequence 41. The feed valve closes as a result, and the device cannot be restarted until the faults have been remedied. Likewise, the pressure switch 16 reports a strong pressure drop in the test system 14, so that the higher-level system control system can initiate a shutdown of the entire system.

Claims (7)

  1. Drive for a feed valve having an hydraulically pressurized actuating line (1) and having a device for controlling the pressure in the actuating line (1) which has three valves (2, 3, 4) connected to one another to form an hydraulic auctioneering circuit,
    characterized in that
    - a test system (14) can be pressurized via this device,
    - a pressure drop in the test system (14) can be sensed by means of a sensor, and
    - connecting lines between the valves (2, 3, 4) and the test system (14) are provided with a non-return valve (61, 62, 63) in each case, which permits a through-flow in the direction of the valve (2, 3, 4).
  2. Drive according to Claim 1, characterized in that
    - each of the three valves (2, 3, 4) is designed to be hydraulically activated, and
    - in each case a solenoid valve (25, 26, 27) is provided for the hydraulic activation, said solenoid valve being connected to the respective associated valve (2, 3, 4).
  3. Drive according to Claim 1, characterized in that
    - the actuating line (1) is pressurized via a direct line (10) provided with an orifice plate (9).
  4. Drive according to Claim 2, characterized in that
    - the actuating line (1) is connected to the respective connection between solenoid valve (25, 26, 27) and valve (2, 3, 4) by means of one bypass line in each case, and
    - these bypass lines each have a non-return valve (73, 75, 77) which permits a through-flow in the direction of the actuating line (1), as well as in each case an orifice plate (74, 76, 78) for limiting the through-flow.
  5. Drive according to Claim 4, characterized in that
    - these bypass lines are arranged inside the respective valves (2, 3, 4).
  6. Drive according to Claim 1 or 2, characterized in that
    - each of the valves (2, 3, 4) is constructed as a a double valve with a common piston (81)
    - the piston (81) has on the one hand a sealing edge (82) which is part of a sliding valve, and on the other hand a sealing seat (84) which is part of a seat valve, and
    - the valves (2, 3, 4) are connected to one another in such a way that in the activated state in each case one sliding valve and one seat valve are connected in series, the seat valve always facing an outlet (41).
  7. Drive according to at least one of the preceding claims, characterized in that
    - the device for controlling the pressure and the solenoid valves (25, 26, 27) are connected to form a monolithic, hydraulic block, and
    - connecting lines are inserted into this block.
EP90123496A 1989-12-21 1990-12-07 Actuator for a feeding valve Expired - Lifetime EP0433791B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90123496T ATE104014T1 (en) 1989-12-21 1990-12-07 DRIVE FOR A FEED VALVE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH457489 1989-12-21
CH4574/89 1989-12-21

Publications (2)

Publication Number Publication Date
EP0433791A1 EP0433791A1 (en) 1991-06-26
EP0433791B1 true EP0433791B1 (en) 1994-04-06

Family

ID=4278633

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90123496A Expired - Lifetime EP0433791B1 (en) 1989-12-21 1990-12-07 Actuator for a feeding valve

Country Status (9)

Country Link
US (1) US5143119A (en)
EP (1) EP0433791B1 (en)
JP (1) JPH04119272A (en)
AT (1) ATE104014T1 (en)
CZ (1) CZ282934B6 (en)
DE (1) DE59005267D1 (en)
DK (1) DK0433791T3 (en)
ES (1) ES2054201T3 (en)
RU (1) RU1838810C (en)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59203461D1 (en) * 1991-11-04 1995-10-05 Asea Brown Boveri Supply circuit for a two-pipe hydraulic system.
DE59408022D1 (en) * 1993-05-28 1999-05-06 Luk Fahrzeug Hydraulik Valve arrangement
JPH07239054A (en) * 1994-02-24 1995-09-12 Komatsu Ltd Operation pressure detection structure of pilot pressure operation type switching valve device
EP0915406B1 (en) * 1997-11-10 2003-05-07 ALSTOM (Switzerland) Ltd Method for monitoring the supply system of a gas turbine with a plurality of burners and device for carrying out this method
GB2332023B (en) * 1997-12-03 2002-07-03 Caterpillar Inc System and method for calibrating an independent metering valve
JP4369292B2 (en) * 2004-05-06 2009-11-18 タイコ フローコントロールジャパン株式会社 Emergency shut-off valve device
US7409965B2 (en) * 2006-10-16 2008-08-12 Elliott Company Direct acting hydraulic trip block
CH699602A1 (en) 2008-09-30 2010-03-31 Alstom Technology Ltd Hydraulic release unit for a valve unit in a combustion engine system, in particular for a quick-closing valve of a turbine installation.
US8794268B2 (en) * 2010-11-05 2014-08-05 Dresser-Rand Company Voting hydraulic dump system
DE102011104530A1 (en) * 2011-02-04 2012-08-09 Robert Bosch Gmbh Hydraulic actuating arrangement
US9896962B2 (en) 2014-02-28 2018-02-20 General Electric Company Trip manifold assembly for turbine systems
DE102015210274A1 (en) 2014-06-03 2015-12-03 Voith Patent Gmbh Multi-way valve, in particular a 6/2-way valve and multi-way valve arrangement
EP3152447B1 (en) 2014-06-03 2020-05-27 Voith Patent GmbH Hydraulic control device for a quick-acting valve of a steam turbine and a steam turbine assembly
CN109322876A (en) * 2018-09-27 2019-02-12 中船重型装备有限公司 A kind of shield machine hydraulic cylinder and valve group detection device
KR102212434B1 (en) * 2020-11-13 2021-02-04 (주)한빛산업 Directional control hydraulic valve and system including the same

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1128573A (en) * 1966-07-14 1968-09-25 Stal Laval Turbin Ab Hydraulic system for testing the operation of overspeed monitors
US4001654A (en) * 1975-07-31 1977-01-04 General Electric Company Testable protective system
DE3138561A1 (en) * 1981-09-28 1983-04-21 Siemens AG, 1000 Berlin und 8000 München Protection device for steam turbine systems, whose functional safety can be tested
CH666132A5 (en) * 1984-07-20 1988-06-30 Bbc Brown Boveri & Cie DEVICE FOR MONITORING PHYSICAL QUANTITIES IN PLANTS.
AT400172B (en) * 1988-12-28 1995-10-25 Sgp Va Energie Umwelt METHOD FOR TESTING AND TESTING DEVICE FOR STEAM TURBINE CONTROL VALVES

Also Published As

Publication number Publication date
US5143119A (en) 1992-09-01
ATE104014T1 (en) 1994-04-15
ES2054201T3 (en) 1994-08-01
EP0433791A1 (en) 1991-06-26
RU1838810C (en) 1993-08-30
DE59005267D1 (en) 1994-05-11
DK0433791T3 (en) 1995-11-20
CZ282934B6 (en) 1997-11-12
CS633590A3 (en) 1992-04-15
JPH04119272A (en) 1992-04-20

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