EP0353586B1 - Actuator for a quick stop valve - Google Patents

Actuator for a quick stop valve Download PDF

Info

Publication number
EP0353586B1
EP0353586B1 EP89113594A EP89113594A EP0353586B1 EP 0353586 B1 EP0353586 B1 EP 0353586B1 EP 89113594 A EP89113594 A EP 89113594A EP 89113594 A EP89113594 A EP 89113594A EP 0353586 B1 EP0353586 B1 EP 0353586B1
Authority
EP
European Patent Office
Prior art keywords
quick
closing
flap
hydraulic
torque shaft
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
EP89113594A
Other languages
German (de)
French (fr)
Other versions
EP0353586A2 (en
EP0353586A3 (en
Inventor
Wolfgang Kindermann
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Priority to AT89113594T priority Critical patent/ATE68856T1/en
Publication of EP0353586A2 publication Critical patent/EP0353586A2/en
Publication of EP0353586A3 publication Critical patent/EP0353586A3/en
Application granted granted Critical
Publication of EP0353586B1 publication Critical patent/EP0353586B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
    • F15B15/065—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement the motor being of the rack-and-pinion type
    • 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

Definitions

  • the present invention relates to a device for actuating a quick-closing flap according to the preamble of claim 1.
  • a quick-closing flap In a steam feed line to a working machine, in particular a steam turbine, quick-closing fittings are generally arranged which are intended to interrupt the steam flow in the shortest possible time in the event of a fault. Operating times for such quick-closing valves are in the order of 100 milliseconds in the closing direction, while in the opening direction, for example, about 10 seconds of operating time are required.
  • a quick-closing fitting can be designed as a cone seat valve or as a flap mounted approximately in the middle.
  • FR-A-2373742 shows a device for actuating a quick-closing flap in a line, the quick-closing flap being arranged in the line on a rotary shaft, the rotary shaft having an angle of rotation of approximately 90 ° and following the line at two ends through the wall is guided on the outside, with racks engaging in the toothings of the rotary shaft at both ends, so that the flap can be rotated by moving the racks.
  • Counteracting hydraulic means and springs are provided on the racks so that the racks are displaced by the hydraulic means against the spring forces. Both racks act in the same direction to actuate the flap.
  • the object of the present invention is to provide a device for actuating a quick-closing flap which enables the 'short closing times required with minimal wear and high operational reliability.
  • Racks are preferably used in cooperation with a pinion attached to the end of the rotary shaft.
  • a pinion attached to the end of the rotary shaft.
  • the toothed racks can be approximately cylindrical in cross-section and can be guided in bushings that are open toward the pinion. It can be particularly advantageous if there is only a force contact between the toothed racks and the springs or hydraulic cylinders moving them, but not a fixed connection. In this way, the central guidance of springs or hydraulic cylinders remains unaffected by any possible wear of the racks in the bushings.
  • the forces required to open a quick-closing flap at which a large differential pressure is present can be considerably reduced by an additional device, which results in a significant reduction in the hydraulic parts of the opening mechanism.
  • an additional device is suitable if a control valve is also arranged behind a quick-closing flap, which is the case with Steam turbines in general are the case.
  • the downstream control valve is normally also closed.
  • this control valve has a leakage flow, so that a large differential pressure is present at the quick-closing flap.
  • This differential pressure can be compensated by a bypass line that bridges the quick-closing flap.
  • the bypass line must have at least one shut-off device so that it can also be shut off in the event of a short-circuit.
  • at least two shut-off devices are usually arranged one behind the other.
  • a further embodiment of the invention relates to the damped entry of the flap plate into the closed end position.
  • the existing two separate means for opening or closing the quick-closing flap make it possible to use the hydraulic means initially available for opening also to effect a damped entry of the flap plate into the closed end position.
  • the closing process is initially triggered by opening an outlet for the hydraulic fluid present in the hydraulic cylinders via valves. In the first phase of the closing process, it is desirable that the hydraulic fluid can emerge from the hydraulic cylinders as quickly as possible. To reduce the closing speed shortly before the closing end position, however, a counter torque can be brought about in the drive by reducing the hydraulic fluid flow ejected from the hydraulic cylinders.
  • an outflow throttle is preferably kept at a constant or angle-dependent differential pressure by connecting at least one hydraulic pressure compensator.
  • the interaction of one or two pressure compensators with an outflow throttle can achieve a load-independent damping of the quick-closing flap.
  • the spring preloads of the pressure compensators can be changed depending on the angle of rotation, for example, via a cam disk attached to the rotary shaft of the drive.
  • the intercepting throttle can also be adjusted depending on the angle of rotation, the pressure compensators being set to a predetermined differential pressure at the throttle. In this way, a closing speed curve is brought about which continuously changes from the maximum closing speed to a lower impact speed which is still permissible for the elastic seal of the quick-closing flap, regardless of the closing moment of the flap.
  • a bypass line 4 bypasses the quick-closing cap 1 and connects the line section 3a to the section 3b.
  • the bypass line 4 is provided with two shut-off valves 5a, 5b for redundancy reasons, which can be closed simultaneously with the quick-closing flap 1.
  • the bypass line 4 and its shut-off elements 5a, 5b are dimensioned for a steam flow which is at least somewhat larger than the leakage flow of the closed control valve 2.
  • Quick-closing flap 1 and the shut-off valves 5a, 5b are spring-loaded in a safety-related manner so that they close automatically when there are malfunctions in the electronics or hydraulics.
  • the quick-closing flap 1 has a rotary shaft 11 which is guided outwards through the steam line on at least one side and is provided with a pinion 12 at its end. With the pinion 12 are two pairs of racks 13, 14 in engagement.
  • a pair of racks 13 can be actuated by hydraulic opening pistons 6, which slide in hydraulic cylinders 8, and serves to open the quick-closing flap 11.
  • Another pair of racks 14, which is completely independent of the first one is connected to closing springs 7 and acts in the closing direction the quick-closing flap 1.
  • the associated hydraulic system consists of a container 18 with hydraulic fluid, a pump 19 which, if necessary, delivers hydraulic fluid to a reservoir 20 or a hydraulic fluid feed line 21 into the hydraulic cylinders 8 via non-described check valves.
  • the quick-closing flap 1 can be opened and remains open until the hydraulic fluid in the hydraulic cylinders 8 opens a drainage path becomes what leads to the triggering of the quick close.
  • Such a drainage path is provided by the drain lines 22, 25, 28 when the safety-related drain valves 24a, 24b are opened by their controller 23a, 23b.
  • valves 34a, 34b Simultaneously with the valves 24a, 24b, the valves 34a, 34b also open, which close the shut-off valves 5a, 5b in the bypass line 4.
  • a quick close should shut off the steam line 3a, 3b, 3c within about 100 milliseconds.
  • the high speed of the quick-closing flap required for this makes it necessary that the hydraulic fluid in the hydraulic cylinders 8 can initially flow out very quickly.
  • the hydraulic fluid flow ejected from the hydraulic cylinders 8 is reduced towards the end of the closing process.
  • a minimum current can always flow through a throttle point 30 to the discharge line 28, but initially existing partial flows are changed by an intercepting throttle 27 and a throttle point 29 as well as by pressure compensators 26a, 26b and the associated adjustable throttle points depending on the position of the rotary shaft 11.
  • cam disks (not shown) can be fastened on the rotary shaft 11, which change the spring preloads of the intercepting throttle 27 or pressure compensators 26a, 26b depending on the angle of rotation by means of mechanical tappets.
  • an adjustable intercepting throttle 27 which would be greatly reduced in cross section, for example, from an angle of rotation of 79 °, ie 11 ° before the closing end position, would be sufficient to dampen the flap plate.
  • the outflow throttle 27 is preceded by a hydraulic pressure compensator 26a, which Differential pressure above the discharge throttle 27 maintains a constant or predeterminable value depending on the angle of rotation.
  • a hydraulic pressure compensator 26a which Differential pressure above the discharge throttle 27 maintains a constant or predeterminable value depending on the angle of rotation.
  • the working areas in hydraulic pressure compensators are limited are preferably two such devices 26a, 26b connected in parallel.
  • the two pressure compensators can be adjusted from a rotation angle of 80 ° or 85 ° with a different spring preload by means of a cam disc in order to achieve a desired damping characteristic regardless of the form.
  • shut-off valves 5a, 5b with their spring-loaded drives 32a, 32b generally do not require a separate damping device, so that they close immediately when the valves 34a, 34b are opened. If the quick-closing flap 1 is to be opened again, the switch 35 is closed and the pump 19 begins to deliver hydraulic fluid. As a result, the valves 24a, 24b, 34a, 34b are closed and, via the valve control 31, the shut-off valve drives 32a, 32b are initially acted upon with pressurized fluid, so that the valves 5a, 5b open.
  • a pinion 12 is arranged, with which the rack pairs 13, 14 are in engagement.
  • the racks 13, 14 are each guided in guide bushes 15, which are open laterally only in the area of the pinion 12.
  • the guide bushes 15 are incorporated in a housing block 16.
  • Above the housing block 16 is a control room 17, in which the hydraulic controls and the other elements of the hydraulic circuit are arranged.
  • the rotary shaft 11 protrudes into this control chamber 17 and can optionally carry cam disks there, which are in engagement with individual elements of the hydraulic Circuit if they are to be changed depending on the angle of rotation.
  • the present invention is suitable as a drive for quick-closing flaps in steam lines of steam turbine systems, in particular also for high pressures and large nominal widths of the steam lines.

Abstract

The present invention relates to an actuator for a quick stop valve (1) in a steam line (3a, 3b, 3c), preferably in a steam turbine. Arranged on the torque shaft (11) of the quick stop valve (1) is a pinion (12) with which two pairs of racks (13, 14) engage. One pair of racks (13) serves in conjunction with hydraulic means (6, 8) to open the quick stop valve (1), the other pair (14) serves in conjunction with closing springs (7) for the purpose of rapid closure. By virtue of complete freedom from play, the two independent systems for opening or closing reduce the wear of the mechanism, and via an appropriate hydraulic connection enable damping of the valve disc of the quick stop valve (1) upon entry into the final closing position. In order to keep this damping independent of different operating states, use is made of manometric balances (26a, 26b) in conjunction with an interceptor throttle (27), which can also be adjustable depending on the angle of rotation. A bypass line (4) which for its part can be blocked by a quick stop shut-off valve (5a, 5b), serves the purpose of relieving the pressure of the quick stop valve (1) during opening. <IMAGE>

Description

Die vorliegende Erfindung betrifft eine Einrichtung zur Betätigung einer Schnellschlußklappe gemäß dem Oberbegriff des Anspruchs 1. In einer Dampfzuleitung zu einer Arbeitsmaschine, insbesondere einer Dampfturbine, sind im allgemeinen Schnellschlußarmaturen angeordnet, die im Falle einer Störung in kürzester Zeit die Dampfströmung unterbrechen sollen. Stellzeiten für solche Schnellschlußarmaturen liegen in Schließrichtung in der Größenordnung von 100 Millisekunden, während in Öffnungsrichtung beispielsweise etwa 10 Sekunden Stellzeit gefordert werden. Eine Schnellschlußarmatur kann als Kegelsitzventil oder als etwa mittig gelagerte Klappe ausgeführt sein.The present invention relates to a device for actuating a quick-closing flap according to the preamble of claim 1. In a steam feed line to a working machine, in particular a steam turbine, quick-closing fittings are generally arranged which are intended to interrupt the steam flow in the shortest possible time in the event of a fault. Operating times for such quick-closing valves are in the order of 100 milliseconds in the closing direction, while in the opening direction, for example, about 10 seconds of operating time are required. A quick-closing fitting can be designed as a cone seat valve or as a flap mounted approximately in the middle.

In einem Prospekt "Klinger-Information" mit der Nr. AIC-10.84-2 B-Nr. 168, der Rich. Klinger GmbH, D-6270 Idstein/Taunus, wird eine Hochleistungsklappe beschrieben, deren prinzipieller Aufbau sich auch für die Verwendung als Schnellschlußklappe eignet. Diese Klappe ist doppelexzentrisch gelagert, was zur Folge hat, daß sich in geschlossener Stellung durch den anstehenden Differenzdruck ein großes Drehmoment in Schließrichtung ergibt, welches beim Öffnen überwunden werden muß. Andererseits ist zum Schließen kein großes Stellmoment erforderlich, da im Falle des Vorhandenseins einer Dampfströmung in der Dampfleitung das Schließmoment von dieser verstärkt wird.In a brochure "Klinger Information" with the number AIC-10.84-2 B-No. 168, the rich. Klinger GmbH, D-6270 Idstein / Taunus, describes a high-performance flap whose basic structure is also suitable for use as a quick-closing flap. This flap is double-eccentrically mounted, which has the consequence that in the closed position there is a large torque in the closing direction due to the differential pressure, which must be overcome when opening. On the other hand, no large actuating torque is required for closing, since in the presence of a steam flow in the steam line, the closing torque is increased by the latter.

In der FR-A-2373742 ist eine Einrichtung zur Betätigung einer Schnellschlußklappe in einer Leitung gezeigt, wobei die Schnellschlußklappe in der Leitung auf einer Drehwelle angeordnet ist, die Drehwelle einen Drehwinkel von etwa 90° hat und an zwei Enden durch die Wand der Leitung nach außen geführt ist, wobei an beiden Enden Zahnstangen in Verzahnungen der Drehwelle eingreifen, so daß die Klappe durch Verschieben der Zahnstangen gedreht werden kann. An den Zahnstangen sind einander entgegenwirkende hydraulische Mittel und Federn vorgesehen, so daß die Verschiebung der Zahnstangen durch die hydraulischen Mittel gegen die Federkräfte erfolgt. Zur Betätigung der Klappe wirken beide Zahnstangen gleichsinnig.FR-A-2373742 shows a device for actuating a quick-closing flap in a line, the quick-closing flap being arranged in the line on a rotary shaft, the rotary shaft having an angle of rotation of approximately 90 ° and following the line at two ends through the wall is guided on the outside, with racks engaging in the toothings of the rotary shaft at both ends, so that the flap can be rotated by moving the racks. Counteracting hydraulic means and springs are provided on the racks so that the racks are displaced by the hydraulic means against the spring forces. Both racks act in the same direction to actuate the flap.

Aufgabe der vorliegenden Erfindung ist die Schaffung einer Einrichtung zur Betätigung einer Schnellschlußklappe, welche die ' geforderten kurzen Schließzeiten bei minimalem Verschleiß und hoher Betriebssicherheit ermöglicht.The object of the present invention is to provide a device for actuating a quick-closing flap which enables the 'short closing times required with minimal wear and high operational reliability.

Zur Lösung dieser Aufgabe wird eine gattungsgemäße Einrichtung mit den kennzeichnenden Merkmalen des Anspruchs 1 vorgeschlagen. Wesentlich hierbei ist, daß zwei getrennte mechanische Mittel für die beiden Bewegungsrichtungen der Schnellschlußklappe vorgesehen sind, welche immer beide gleichzeitig in Eingriff sind. Wie bei sicherheitstechnisch relevanten Armaturen üblich, werden dabei federbelastete mechanische Mittel in Schließrichtung verwendet und hydraulische für die Bewegung in Öffnungsrichtung. Dadurch, daß beide Mittel in entgegengesetzten Richtungen gleichzeitig in Eingriff sind, wird jedes Spiel in der Mechanik vermieden, wodurch selbst bei einer Momentenumkehr und hohen Betätigungsgeschwindigkeiten im Falle des Schließens kein großer Verschleiß auftreten kann.To solve this problem, a generic device with the characterizing features of claim 1 is proposed. It is essential here that two separate mechanical means are provided for the two directions of movement of the quick-closing flap, which always both engage simultaneously are. As is usual with safety-relevant fittings, spring-loaded mechanical means are used in the closing direction and hydraulic ones for the movement in the opening direction. Because both means are engaged in opposite directions at the same time, any play in the mechanics is avoided, which means that even with a torque reversal and high actuation speeds in the event of closing, no great wear can occur.

Vorteilhafte Ausbildungen der Erfindung sind in den Unteransprüchen beschrieben. Bevorzugt werden Zahnstangen im Zusammenwirken mit einem auf dem Ende der Drehwelle befestigten Ritzel verwendet. Dabei ist es aus Gründen der symmetrischen Belastung des Ritzels besonders günstig, Paare von auf gegenüberliegenden Seiten des Ritzels angreifenden Zahnstangen für jede der beiden mechanischen Bewegungsrichtungen zu verwenden.Advantageous developments of the invention are described in the subclaims. Racks are preferably used in cooperation with a pinion attached to the end of the rotary shaft. For reasons of the symmetrical loading of the pinion, it is particularly favorable to use pairs of toothed racks acting on opposite sides of the pinion for each of the two mechanical directions of movement.

Dabei können die Zahnstangen bis auf den gezähnten Bereich im Querschnitt etwa zylindrisch geformt sein und in zum Ritzel hin offenen Buchsen geführt werden. Dabei kann es besonders vorteilhaft sein, wenn zwischen den Zahnstangen und den diese bewegenden Federn bzw. Hydraulikzylindern nur ein Kraftkontakt besteht, nicht aber eine feste Verbindung. Auf diese Weise bleibt die Mittenführung von Federn bzw. Hydraulikzylinder unbeeinflußt von einem eventuellen Führungsverschleiß der Zahnstangen in den Buchsen.Except for the toothed area, the toothed racks can be approximately cylindrical in cross-section and can be guided in bushings that are open toward the pinion. It can be particularly advantageous if there is only a force contact between the toothed racks and the springs or hydraulic cylinders moving them, but not a fixed connection. In this way, the central guidance of springs or hydraulic cylinders remains unaffected by any possible wear of the racks in the bushings.

Weitere erfindungsgemäße Einzelheiten der mechanischen Teile der Einrichtung werden anhand der Zeichnung näher erläutert.Further details according to the invention of the mechanical parts of the device are explained in more detail with reference to the drawing.

Gemäß dem Anspruch 6 können die Kräfte, die zum Öffnen einer Schnellschlußklappe, an der ein großer Differenzdruck ansteht, notwendig sind, durch eine Zusatzeinrichtung erheblich verringert werden, was eine deutliche Verkleinerung der hydraulischen Teile der Öffnungsmechanik zur Folge hat. Eine solche Zusatzeinrichtung eignet sich dann, wenn hinter einer Schnellschlußklappe noch ein Steuerventil angeordnet ist, was bei Dampfturbinen im allgemeinen der Fall ist. Bei geschlossener Schnellschlußklappe wird normalerweise auch das nachgeordnete Steuerventil geschlossen. Dieses Steuerventil hat jedoch einen Leckagedurchfluß, so daß an der Schnellschlußklappe ein großer Differenzdruck ansteht. Durch eine Umgehungsleitung, welche die Schnellschlußklappe überbrückt, kann dieser Differenzdruck ausgeglichen werden. Die Umgehungsleitung muß dabei mindestens ein Absperrorgan aufweisen, damit diese im Schnellschlußfalle ebenfalls abgesperrt werden kann. Aus Sicherheits- bzw. Redundanzgründen werden meist mindestens zwei Absperrorgane hintereinander angeordnet. Durch Öffnen der Absperrorgane in der Umgehungsleitung vor dem Öffnen der Schnellschlußklappe kann ein Druckausgleich vor und hinter der Schnellschlußklappe hergestellt werden. Dadurch läßt sich diese mit wesentlich geringeren Momenten öffnen. Hierzu sollten die Umgehungsleitung und deren Absperrorgane mindestens für einen Dampfdurchfluß ausgelegt sein, der etwas größer als der Leckagedurchfluß des nachgeschalteten Stellventils in geschlossenem Zustand ist.According to claim 6, the forces required to open a quick-closing flap at which a large differential pressure is present can be considerably reduced by an additional device, which results in a significant reduction in the hydraulic parts of the opening mechanism. Such an additional device is suitable if a control valve is also arranged behind a quick-closing flap, which is the case with Steam turbines in general are the case. When the quick-closing flap is closed, the downstream control valve is normally also closed. However, this control valve has a leakage flow, so that a large differential pressure is present at the quick-closing flap. This differential pressure can be compensated by a bypass line that bridges the quick-closing flap. The bypass line must have at least one shut-off device so that it can also be shut off in the event of a short-circuit. For safety or redundancy reasons, at least two shut-off devices are usually arranged one behind the other. By opening the shut-off devices in the bypass line before opening the quick-closing flap, pressure equalization in front of and behind the quick-closing flap can be established. As a result, it can be opened with significantly lower moments. For this purpose, the bypass line and its shut-off devices should be designed at least for a steam flow that is somewhat larger than the leakage flow of the downstream control valve in the closed state.

Um einen Verschleiß der Schnellschlußklappe selbst und von deren Dichtung zu vermindern, betrifft eine weitere Ausgestaltung der Erfindung den gedämpften Einlauf des Klappentellers in die Schließendstellung. Durch die vorhandenen zwei getrennten Mittel zum Öffnen bzw. Schließen der Schnellschlußklappe bietet sich die Möglichkeit, die zunächst zum Öffnen vorhandenen hydraulischen Mittel auch dazu einzusetzen, einen gedämpften Einlauf des Klappentellers in die Schließendstellung zu bewirken. Der Schließvorgang wird zunächst dadurch ausgelöst, daß für das in den Hydraulikzylindern vorhandene Hydraulikfluid über Ventile ein Auslaß geöffnet wird. In der ersten Phase des Schließvorganges ist es dabei erwünscht, daß das Hydraulikfluid möglichst schnell aus den Hydraulikzylindern austreten kann. Zur Reduzierung der Schließgeschwindigkeit kurz vor der Schließendstellung kann jedoch im Antrieb ein Gegenmoment dadurch bewirkt werden, daß der aus den Hydraulikzylindern ausgeschobene Hydraulikfluidstrom verringert wird. Diese Verringerung kann vorzugsweise drehwinkelabhängig erfolgen ab einem bestimmten, einstellbaren Drehwinkel der Drehwelle, beispielsweise 79°. Ein Teil des drehwinkelabhängigen Schließmomentes, dem das Dämpfungsmoment entgegenwirken muß, ist das vom Differenzdruck an der Klappe abhängige Strömungsmoment. Je nach Lastzustand der Gesamtanlage, bei dem der Schnellschluß der Klappe erfolgt, ist daher das Schließmoment und damit der Öldruck im Hydraulikzylinder während des Dämpfungsvorganges ein anderer. Deshalb wird in der erfindungsgemäßen Ausführung der Dämpfungseinrichtung vorzugsweise eine Abströmdrossel durch das Vorschalten mindestens einer hydraulischen Druckwaage auf konstantem bzw. drehwinkelabhängigem Differenzdruck gehalten. Wie anhand der Zeichnung näher erläutert wird, kann durch das Zusammenwirken von einer oder zwei Druckwaagen mit einer Abströmdrossel eine belastungsunabhängige Dämpfung der Schnellschlußklappe erreicht werden. Dabei können zur Erzielung einer ganz bestimmten Dämpfungscharakteristik die Federvorspannungen der Druckwaagen beispielsweise über eine auf der Drehwelle des Antriebes befestigte Nockenscheibe drehwinkelabhängig verändert werden. Alternativ kann auch die Abfangdrossel drehwinkelabhängig verstellt werden, wobei die Druckwaagen auf einen fest vorgegebenen Differenzdruck an der Drossel eingestellt werden. So wird ein Schließgeschwindigkeitsverlauf herbeigeführt, der von der maximalen Schließgeschwindigkeit stetig übergeht in eine geringere, für die elastische Dichtung der Schnellschlußklappe noch zulässige Auftreffgeschwindigkeit, und zwar unabhängig vom Schließmoment der Klappe.In order to reduce wear on the quick-closing flap itself and on its seal, a further embodiment of the invention relates to the damped entry of the flap plate into the closed end position. The existing two separate means for opening or closing the quick-closing flap make it possible to use the hydraulic means initially available for opening also to effect a damped entry of the flap plate into the closed end position. The closing process is initially triggered by opening an outlet for the hydraulic fluid present in the hydraulic cylinders via valves. In the first phase of the closing process, it is desirable that the hydraulic fluid can emerge from the hydraulic cylinders as quickly as possible. To reduce the closing speed shortly before the closing end position, however, a counter torque can be brought about in the drive by reducing the hydraulic fluid flow ejected from the hydraulic cylinders. This reduction can preferably take place depending on the angle of rotation from a certain, adjustable Angle of rotation of the rotating shaft, for example 79 °. Part of the closing torque, which is dependent on the angle of rotation and which the damping torque must counteract, is the flow torque, which is dependent on the differential pressure at the flap. Depending on the load condition of the overall system, in which the flap closes quickly, the closing torque and thus the oil pressure in the hydraulic cylinder during the damping process are different. Therefore, in the embodiment of the damping device according to the invention, an outflow throttle is preferably kept at a constant or angle-dependent differential pressure by connecting at least one hydraulic pressure compensator. As will be explained in more detail with reference to the drawing, the interaction of one or two pressure compensators with an outflow throttle can achieve a load-independent damping of the quick-closing flap. In order to achieve a very specific damping characteristic, the spring preloads of the pressure compensators can be changed depending on the angle of rotation, for example, via a cam disk attached to the rotary shaft of the drive. Alternatively, the intercepting throttle can also be adjusted depending on the angle of rotation, the pressure compensators being set to a predetermined differential pressure at the throttle. In this way, a closing speed curve is brought about which continuously changes from the maximum closing speed to a lower impact speed which is still permissible for the elastic seal of the quick-closing flap, regardless of the closing moment of the flap.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt, und zwar zeigen

  • Fig. 1 eine schematisierte Gesamtanordnung von Schnellschlußklappe und zugehöriger hydraulischer Steuerung und
  • Fig. 2 einen Längsschnitt durch einen Schnellschlußklappen-Schaltantrieb.
An embodiment of the invention is shown in the drawing, namely show
  • Fig. 1 is a schematic overall arrangement of quick-closing flap and associated hydraulic control and
  • Fig. 2 shows a longitudinal section through a quick-closing valve actuator.

Fig. 1 zeigt eine aus drei Abschnitten 3a, 3b, 3c bestehende Dampfleitung, deren Abschnitte durch eine Schnellschlußklappe 1 und ein nachgeschaltetes Stellventil 2 voneinander getrennt werden können. Eine Umgehungsleitung 4 umgeht die Schnellschlußkappe 1 und verbindet den Leitungsabschnitt 3a mit dem Abschnitt 3b. Die Umgehungsleitung 4 ist aus Redundanzgründen mit zwei Absperrventilen 5a, 5b versehen, welche gleichzeitig mit der Schnellschlußklappe 1 geschlossen werden können. Die Umgehungsleitung 4 und deren Absperrorgane 5a, 5b sind für einen Dampfdurchfluß dimensioniert, der mindestens etwas größer als der Leckagedurchfluß des geschlossenen Stellventils 2 ist. Schnellschlußklappe 1 und die Absperrventile 5a, 5b sind sicherheitsgerichtet federbelastet, so daß sie sich automatisch schließen, wenn es zu Störungen in der Elektronik oder Hydraulik kommt. Die Schnellschlußklappe 1 weist eine Drehwelle 11 auf, welche mindestens an einer Seite durch die Dampfleitung nach außen geführt und mit einem Ritzel 12 an ihrem Ende versehen ist. Mit dem Ritzel 12 stehen zwei Paare von Zahnstangen 13, 14 in Eingriff. Ein Zahnstangenpaar 13 kann dabei von Hydraulik-Öffnungskolben 6, die in Hydraulikzylindern 8 gleiten, betätigt werden und dient zum Öffnen der Schnellschlußklappe 11. Ein weiteres Zahnstangenpaar 14, welches völlig unabhängig von dem ersten ist, steht mit Schließfedern 7 in Verbindung und wirkt in Schließrichtung der Schnellschlußklappe 1. Zwischen den Zahnstangenpaaren 13, 14 und den Hydrauliköffnungskolben 6 bzw. den Schließfedern 7 besteht nur ein Kraftkontakt, so daß die Mittenführung der Hydraulik-Öffnungs kolben 6 bzw. Schließfedern 7 nicht durch einen etwaigen Verschleiß in der Führung der Zahnstangen 13, 14 beeinträchtigt wird.1 shows a steam line consisting of three sections 3a, 3b, 3c, the sections of which are connected by a quick-closing flap 1 and a downstream control valve 2 can be separated from each other. A bypass line 4 bypasses the quick-closing cap 1 and connects the line section 3a to the section 3b. The bypass line 4 is provided with two shut-off valves 5a, 5b for redundancy reasons, which can be closed simultaneously with the quick-closing flap 1. The bypass line 4 and its shut-off elements 5a, 5b are dimensioned for a steam flow which is at least somewhat larger than the leakage flow of the closed control valve 2. Quick-closing flap 1 and the shut-off valves 5a, 5b are spring-loaded in a safety-related manner so that they close automatically when there are malfunctions in the electronics or hydraulics. The quick-closing flap 1 has a rotary shaft 11 which is guided outwards through the steam line on at least one side and is provided with a pinion 12 at its end. With the pinion 12 are two pairs of racks 13, 14 in engagement. A pair of racks 13 can be actuated by hydraulic opening pistons 6, which slide in hydraulic cylinders 8, and serves to open the quick-closing flap 11. Another pair of racks 14, which is completely independent of the first one, is connected to closing springs 7 and acts in the closing direction the quick-closing flap 1. Between the pairs of racks 13, 14 and the hydraulic opening piston 6 or the closing springs 7 there is only a force contact, so that the central guidance of the hydraulic opening piston 6 or closing springs 7 is not caused by any wear in the guide of the racks 13, 14 is impaired.

Die bisher beschriebenen Teile sind in der Fig. 1 nur schematisch dargestellt, da diese Figur der Veranschaulichung des zugehörigen hydraulischen Schaltschemas dient. Das zugehörige Hydrauliksystem besteht aus einem Behälter 18 mit Hydraulikflüssigkeit, einer Pumpe 19, welche bei Bedarf über nicht näher beschriebene Rückschlagventile Hydraulikfluid in einen Speicher 20 bzw. über eine Hydraulikfluid-Zuleitung 21 in die Hydraulikzylinder 8 fördert. Auf diese Weise kann die Schnellschlußklappe 1 geöffnet werden und bleibt solange offen, bis dem Hydraulikfluid in den Hydraulikzylindern 8 ein Abflußweg geöffnet wird, was zur Auslösung des Schnellschlusses führt. Ein solcher Abflußweg ist durch die Ablaufleitungen 22, 25, 28 gegeben, wenn die sicherheitsgerichteten Ablaßventile 24a, 24b durch ihre Steuerung 23a, 23b geöffnet werden. Diese Ventile und Steuerungen sind aus Redundanzgründen doppelt vorhanden. Gleichzeitig mit den Ventilen 24a, 24b öffnen auch die Ventile 34a, 34b, welche die Absperrventile 5a, 5b in der Umgehungsleitung 4 schließen. Ein Schnellschluß soll die Dampfleitung 3a, 3b, 3c innerhalb von etwa 100 Millisekunden absperren. Die hierzu notwendige große Geschwindigkeit der Schnellschlußklappe macht es erforderlich, daß das Hydraulikfluid in den Hydraulikzylindern 8 zunächst sehr schnell ausströmen kann. Um jedoch zu vermeiden, daß der Klappenteller der Schnellschlußklappe 1 mit großer Geschwindigkeit in die Schließendstellung fährt und dabei Verschleiß oder ein Schaden entsteht, wird gegen Ende des Schließvorganges der aus den Hydraulikzylindern 8 ausgeschobene Hydraulikfluidstrom verringert. Ein Mindeststrom kann zwar immer durch eine Drosselstelle 30 zur Ablaufleitung 28 fließen, jedoch werden anfangs vorhandene Teilströme durch eine Abfangdrossel 27 und eine Drosselstelle 29 sowie durch Druckwaagen 26a, 26b und damit verbundene regelbare Drosselstellen in Abhängigkeit von der Stellung der Drehwelle 11 verändert. Hierzu können nicht dargestellte Nockenscheiben auf der Drehwelle 11 befestigt werden, welche über mechanische Stößel die Federvorspannungen von Abfangdrossel 27 bzw. Druckwaagen 26a, 26b drehwinkelabhängig verändern. Bei konstanten Bedinungen würde eine verstellbare Abfangdrossel 27, welche beispielsweise ab einem Drehwinkel von 79°, d.h. 11° vor der Schließendstellung, im Querschnitt stark verkleinert würde, zur Dämpfung des Klappentellers ausreichen. Da jedoch je nach der Dampfströmung in der Dampfleitung 3a, 3b, 3c ganz unterschiedliche Schließkräfte auf den Klappenteller wirken können, was unterschiedliche Öldrücke im Hydraulikzylinder während des Dämpfungsvorganges bewirkt, ist es vorteilhaft, wenn der Abströmdrossel 27 eine hydraulische Druckwaage 26a vorgeschaltet wird, welche den Differenzdruck über der Abströmdrossel 27 auf einem konstanten bzw. vorgebbar drehwinkelabhängigen Wert hält. Da die Arbeitsbereiche bei hydraulischen Druckwaagen begrenzt sind, werden vorzugsweise zwei derartige Einrichtungen 26a, 26b parallel geschaltet. So können die beiden Druckwaagen beispielsweise ab einem Drehwinkel von 80° bzw. 85° mit einer anderen Federvorspannung durch eine Nockenscheibe eingestellt werden, um eine gewünschte Dämpfungscharakteristik unabhängig vom Vordruck zu erreichen. Das ausströmende Druckfluid gelangt über die Ablaufleitung 28 wieder in den Behälter 18. Die wesentlich kleineren Absperrventile 5a, 5b mit ihren federbelasteten Antrieben 32a, 32b benötigen im allgemeinen keine gesonderte Dämpfungseinrichtung, so daß diese sich beim Öffnen der Ventil 34a, 34b sofort schließen. Soll die Schnellschlußklappe 1 wieder geöffnet werden, so wird der Schalter 35 geschlossen und die Pumpe 19 beginnt Hydraulikfluid zu fördern. Dadurch werden die Ventile 24a, 24b, 34a, 34b geschlossen und über die Ventilsteuerung 31 zunächst die Absperrventilantriebe 32a, 32b mit Druckfluid beaufschlagt, so daß die Ventile 5a, 5b öffnen. Dadurch entsteht ein Druckausgleich in den Leitungsabschnitten 3a, 3b, so daß die Schnellschlußklappe 1 nunmehr leicht durch Betätigung der Hydraulik-Öffnungskolben 6, die ebenfalls mit Druckfuid beaufschlagt werden, geöffnet werden kann. Dabei werden die Federn 7 wieder gespannt, so daß ein Schnellschluß durch Öffnen des Schalters 35 oder einen Ausfall im Hydrauliksystem ausgelöst werden kann.The parts described so far are only shown schematically in FIG. 1, since this figure serves to illustrate the associated hydraulic circuit diagram. The associated hydraulic system consists of a container 18 with hydraulic fluid, a pump 19 which, if necessary, delivers hydraulic fluid to a reservoir 20 or a hydraulic fluid feed line 21 into the hydraulic cylinders 8 via non-described check valves. In this way, the quick-closing flap 1 can be opened and remains open until the hydraulic fluid in the hydraulic cylinders 8 opens a drainage path becomes what leads to the triggering of the quick close. Such a drainage path is provided by the drain lines 22, 25, 28 when the safety-related drain valves 24a, 24b are opened by their controller 23a, 23b. These valves and controls are duplicated for redundancy reasons. Simultaneously with the valves 24a, 24b, the valves 34a, 34b also open, which close the shut-off valves 5a, 5b in the bypass line 4. A quick close should shut off the steam line 3a, 3b, 3c within about 100 milliseconds. The high speed of the quick-closing flap required for this makes it necessary that the hydraulic fluid in the hydraulic cylinders 8 can initially flow out very quickly. However, in order to prevent the flap plate of the quick-closing flap 1 from moving into the closed end position at high speed and thereby causing wear or damage, the hydraulic fluid flow ejected from the hydraulic cylinders 8 is reduced towards the end of the closing process. A minimum current can always flow through a throttle point 30 to the discharge line 28, but initially existing partial flows are changed by an intercepting throttle 27 and a throttle point 29 as well as by pressure compensators 26a, 26b and the associated adjustable throttle points depending on the position of the rotary shaft 11. For this purpose, cam disks (not shown) can be fastened on the rotary shaft 11, which change the spring preloads of the intercepting throttle 27 or pressure compensators 26a, 26b depending on the angle of rotation by means of mechanical tappets. At constant conditions, an adjustable intercepting throttle 27, which would be greatly reduced in cross section, for example, from an angle of rotation of 79 °, ie 11 ° before the closing end position, would be sufficient to dampen the flap plate. However, since depending on the steam flow in the steam line 3a, 3b, 3c, very different closing forces can act on the valve disc, which causes different oil pressures in the hydraulic cylinder during the damping process, it is advantageous if the outflow throttle 27 is preceded by a hydraulic pressure compensator 26a, which Differential pressure above the discharge throttle 27 maintains a constant or predeterminable value depending on the angle of rotation. Because the working areas in hydraulic pressure compensators are limited are preferably two such devices 26a, 26b connected in parallel. For example, the two pressure compensators can be adjusted from a rotation angle of 80 ° or 85 ° with a different spring preload by means of a cam disc in order to achieve a desired damping characteristic regardless of the form. The outflowing pressure fluid reaches the container 18 again via the discharge line 28. The substantially smaller shut-off valves 5a, 5b with their spring-loaded drives 32a, 32b generally do not require a separate damping device, so that they close immediately when the valves 34a, 34b are opened. If the quick-closing flap 1 is to be opened again, the switch 35 is closed and the pump 19 begins to deliver hydraulic fluid. As a result, the valves 24a, 24b, 34a, 34b are closed and, via the valve control 31, the shut-off valve drives 32a, 32b are initially acted upon with pressurized fluid, so that the valves 5a, 5b open. This creates a pressure equalization in the line sections 3a, 3b, so that the quick-closing flap 1 can now be easily opened by actuating the hydraulic opening pistons 6, which are also pressurized with pressure fluid. The springs 7 are tensioned again so that a quick close by opening the switch 35 or a failure in the hydraulic system can be triggered.

Der Aufbau des in Fig. 1 nur schematisch dargestellten Schaltantriebes der Schnellschlußklappe 1 ist in Fig. 2 im Längsschnitt zur Veranschaulichung der Platzverhältnisse detaillierter dargestellt. Auf der Drehwelle 11 ist ein Ritzel 12 angeordnet, mit welchem sich die Zahnstangenpaare 13, 14 in Eingriff befinden. Die Zahnstangen 13, 14 werden jeweils in Führungsbuchsen 15 geführt, welche seitlich nur im Bereich des Ritzels 12 offen sind. Die Führungsbuchsen 15 sind in einen Gehäuseblock 16 eingearbeitet. Oberhalb des Gehäuseblocks 16 befindet sich ein Steuerungsraum 17, in welchem die Hydrauliksteuerungen und die übrigen Elemente der hydraulischen Schaltung angeordnet sind. Die Drehwelle 11 ragt in diesen Steuerungsraum 17 hinein und kann ggf. dort Nockenscheiben tragen, die sich im Eingriff mit einzelnen Elementen der hydraulischen Schaltung befinden, sofern diese drehwinkelabhängig verändert werden sollen. Seitlich an dem Gehäuseblock 16 befindet sich ein Behälter 18 mit Hydraulikfluid, in welchem eine Pumpe 19 angeordnet ist. Auf der gegenüberliegenden Seite des Gehäuseblockes 16 sind Druckspeicher 20 angeordnet. Der gesamte Schaltantrieb 10 ist außerhalb der Dampfleitung 3a, 3b, 3c um die aus dieser herausragende Drehwelle 11 angeordnet.The structure of the switching drive of the quick-closing flap 1, which is shown only schematically in FIG. 1, is shown in detail in longitudinal section in FIG. 2 to illustrate the space conditions. On the rotary shaft 11, a pinion 12 is arranged, with which the rack pairs 13, 14 are in engagement. The racks 13, 14 are each guided in guide bushes 15, which are open laterally only in the area of the pinion 12. The guide bushes 15 are incorporated in a housing block 16. Above the housing block 16 is a control room 17, in which the hydraulic controls and the other elements of the hydraulic circuit are arranged. The rotary shaft 11 protrudes into this control chamber 17 and can optionally carry cam disks there, which are in engagement with individual elements of the hydraulic Circuit if they are to be changed depending on the angle of rotation. At the side of the housing block 16 there is a container 18 with hydraulic fluid, in which a pump 19 is arranged. Pressure accumulators 20 are arranged on the opposite side of the housing block 16. The entire switching drive 10 is arranged outside the steam line 3a, 3b, 3c about the rotary shaft 11 projecting therefrom.

Die vorliegende Erfindung eignet sich als Antrieb für Schnellschlußklappen in Dampfleitungen von Dampfturbinenanlagen, insbesondere auch für hohe Drücke und große Nennweiten der Dampfleitungen.The present invention is suitable as a drive for quick-closing flaps in steam lines of steam turbine systems, in particular also for high pressures and large nominal widths of the steam lines.

Claims (12)

1. A device for actuating a quick shutoff flap (1) in a steam line (3a, 3b, 3c), wherein the quick shutoff flap (1) is arranged, preferably doubly eccentrically, in the steam line (3a, 3b, 3c), on a torque shaft (11) which has an angle of rotation of approximately 90°, and wherein the torque shaft (11) is guided to the outside at least at one end through the wall of the steam line (3a, 3b, 3c), and mechanical means (12, 13, 14) for rotating the torque shaft (11) act at least at this end, characterised by the following features:
a) at least two mechanical means (13, 14), separate from each other and opposing one another, act at the end (12) of the torque shaft (11) in order to convert a linear motion into a rotary motion;
b) the first (13) of these means are means acting hydraulically (6) in the opening direction;
c) the second (14) of these means are means operating through latent spring forces (7) in the closing direction.
2. A device according to claim 1, characterised in that the mechanical means (13, 14) for converting a linear motion into a rotary motion are at least one pinion (12) secured to the torque shaft (11) and gear racks (13, 14) cooperating therewith, especially pairs of gear racks (13, 14) acting on opposite sides of the pinion (12).
3. A device according to claim 2, characterised in that the gear racks (13, 14) are approximately cylindrical in cross-section and are guided in bushes (15) open towards the pinion (12).
4. A device according to claim 1, 2 or 3, characterised in that the hydraulic means (13) operating in the opening direction are hydraulic cylinders (8) with hydraulic opening pistons (6).
5. A device according to claim 1, 2, 3 or 4, characterised in that the mechanical means acting in the closing direction are gear rack pairs (14) loaded by spring assemblies (7), in particular consisting of disc springs.
6. A device according to one of the preceding claims, wherein the quick shutoff flap (1) is connected in series with a pilot valve (2), which is arranged on the side of lower steam pressure, characterised in that the quick shutoff flap (1) is by-passed by a by-pass line (4), which branches off from the steam line (3a) before the quick shutoff flap (1), reopens into the steam line (3b) between the quick shutoff flap (1) and the pilot valve (2), and has at least one shutoff element (5a, 5b), preferably a quick-closing valve.
7. A device according to claim 6, characterised in that the by-pass line (4) has at least two shutoff elements (5a, 5b) connected one after the other and closable by spring force.
8. A device according to claim 6 or 7, characterised in that the by-pass line (4) and the shutoff elements (5a, 5b) are designed for a rate of steam through-flow which is at least somewhat higher than the rate of leakage through-flow of the closed control valve (2).
9. A device according to claim 4, 5, 6, 7 or 8, characterised in that the hydraulic cylinders (8) of the hydraulic opening pistons (6) are able to be emptied via drain lines (22, 25, 28), drain valves (24a, 24b), and throttle devices (26a, 26b, 27, 29, 30).
10. A device according to claim 9, characterised in that the throttle devices include at least one interceptor throttle (27) and at least one pressure balance (26a, 26b), at least one of which can be adjusted depending on the position of the torque shaft (11).
11. A device according to claim 10, characterised in that two pressure balances (26a, 26b) are present, connected in parallel, and which have varying operating ranges.
12. A device according to claim 10 or 11, characterised in that there is (or are) secured to the torque shaft (11) one or several cam discs which, for the purpose of adjusting the interceptor throttle (27) and/or the pressure balance(s) (26a, 26b), engages (engage) with this (or these).
EP89113594A 1988-08-04 1989-07-24 Actuator for a quick stop valve Expired - Lifetime EP0353586B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89113594T ATE68856T1 (en) 1988-08-04 1989-07-24 DEVICE FOR ACTIVATING A QUICK-CLOSING FLAP.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3826592 1988-08-04
DE3826592A DE3826592A1 (en) 1988-08-04 1988-08-04 DEVICE FOR ACTUATING A QUICK-RELEASE VALVE

Publications (3)

Publication Number Publication Date
EP0353586A2 EP0353586A2 (en) 1990-02-07
EP0353586A3 EP0353586A3 (en) 1990-05-30
EP0353586B1 true EP0353586B1 (en) 1991-10-23

Family

ID=6360278

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89113594A Expired - Lifetime EP0353586B1 (en) 1988-08-04 1989-07-24 Actuator for a quick stop valve

Country Status (3)

Country Link
EP (1) EP0353586B1 (en)
AT (1) ATE68856T1 (en)
DE (2) DE3826592A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10111187C1 (en) * 2001-03-08 2002-07-25 Siemens Ag Steam line closure valve for steam turbine plant provided by several elements cooperating for blocking steam line cross-section
CN104197080B (en) * 2014-06-09 2016-05-25 常州机电职业技术学院 Valve changes up pass hydraulic control system soon

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3621489A1 (en) * 1986-06-27 1988-01-07 Waldorf Veronika Device for converting a linear movement into a rotary movement

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE362149C (en) * 1920-10-12 1922-10-24 Georg Einhorn Sheet feeder and delivery device for platen printing presses
US3591127A (en) * 1968-09-30 1971-07-06 Ametak Inc Butterfly valve structure with combined translation and rotary movements
DE2655493C3 (en) * 1976-12-08 1979-05-23 Ing.-Buero Pfannenschmidt Gmbh, 2000 Hamburg Pressurized medium-actuated rotary drive for a valve
DE3606102A1 (en) * 1986-02-26 1987-08-27 Amg Antrieb Mechanik Gmbh SWIVEL DRIVE

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3621489A1 (en) * 1986-06-27 1988-01-07 Waldorf Veronika Device for converting a linear movement into a rotary movement

Also Published As

Publication number Publication date
DE58900399D1 (en) 1991-11-28
EP0353586A2 (en) 1990-02-07
DE3826592A1 (en) 1990-02-08
ATE68856T1 (en) 1991-11-15
EP0353586A3 (en) 1990-05-30

Similar Documents

Publication Publication Date Title
EP1431496A2 (en) Servo-electrohydraulic door drive for driving a door, window or the like
EP0126291A2 (en) Fluid pressure-controlled valve
EP0928388B1 (en) Turbine valve
EP0353586B1 (en) Actuator for a quick stop valve
DE2832898C2 (en) Irreversible hydraulic actuator
EP1451474A1 (en) Drive
DE2423595C2 (en) Hydraulic circuit arrangement
DE1209387B (en) Drive unit for shut-off devices, in particular gate valves on tankers
EP0163861B1 (en) Door actuating device
WO1999008029A1 (en) Pilot-operated pressure control valve
EP0505349B2 (en) Hydraulic actuator
DE3234615A1 (en) Door-actuating device
DE3812116C2 (en) Electro-hydraulic directional valve
EP0077984B1 (en) Positioning actuator
DE10261224B3 (en) Electrohydraulic door operating drive with open holding function provided by hydraulically-controlled valve with 2/2-way valve and non-return valve
DE2322998C3 (en) Hydraulic adjusting device, in particular for a steering
DE2928802C2 (en) Pressure medium operated differential pressure switch
DE2450330C3 (en) Double hydraulic actuator
DE19505333C2 (en) Hydraulic drive
DE3041788C2 (en) Drive device for the slide gate of a metallurgical vessel
WO2003074883A1 (en) Valve arrangement
DE2108545C (en) Double hydraulic actuator
DE4131821C1 (en) Pressure medium safety circuit for boiler lid handling - has extra safety valve coupled to valve system for switching in dependence on pressure threshold value
DE112004000191B4 (en) Drive for a turbine valve
DE2743738A1 (en) Electrical servo drive for valve - has movable wall bounding chamber acted upon by spring and pressure medium

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT CH DE FR GB LI SE

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KINDERMANN, WOLFGANG

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT CH DE FR GB LI SE

17P Request for examination filed

Effective date: 19900625

17Q First examination report despatched

Effective date: 19910125

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT CH DE FR GB LI SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19911023

Ref country code: GB

Effective date: 19911023

Ref country code: FR

Effective date: 19911023

REF Corresponds to:

Ref document number: 68856

Country of ref document: AT

Date of ref document: 19911115

Kind code of ref document: T

REF Corresponds to:

Ref document number: 58900399

Country of ref document: DE

Date of ref document: 19911128

EN Fr: translation not filed
GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19920724

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19920731

Ref country code: CH

Effective date: 19920731

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19930401