EP0075211A2 - Control valve, especially for controlling and regulating steam turbines - Google Patents

Control valve, especially for controlling and regulating steam turbines Download PDF

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Publication number
EP0075211A2
EP0075211A2 EP82108333A EP82108333A EP0075211A2 EP 0075211 A2 EP0075211 A2 EP 0075211A2 EP 82108333 A EP82108333 A EP 82108333A EP 82108333 A EP82108333 A EP 82108333A EP 0075211 A2 EP0075211 A2 EP 0075211A2
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EP
European Patent Office
Prior art keywords
channel part
diffuser
valve
convergent
control valve
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Ceased
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EP82108333A
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German (de)
French (fr)
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EP0075211A3 (en
Inventor
Otto Dipl.-Ing. Von Schwerdtner
Hans Dipl.-Ing. Judith
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Kraftwerk Union AG
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Kraftwerk Union AG
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Publication of EP0075211A2 publication Critical patent/EP0075211A2/en
Publication of EP0075211A3 publication Critical patent/EP0075211A3/en
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    • 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
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines

Definitions

  • the invention relates to a control valve, in particular for controlling and regulating steam turbines, according to the preamble of patent claim 1.
  • control valves which are known, for example, from Siemens magazine 41 (1967), supplement “Steam turbines of great output", pages 75 and 76, are intended, on the one hand, to ensure a desired throttle characteristic by changing the stroke position of the valve body and, on the other hand, in a fully open, ie. H. cause the lowest possible gradient losses when driven.
  • the adjustment forces should be kept small with regard to the limits of the dimensions and the performance of the associated actuators. In the single-seat valves mostly used in steam turbine construction, the adjusting forces are reduced by the selection of a relatively small diameter of the valve body. In the narrowest cross section behind the valve seat, high flow velocities result even when the control valve is fully open.
  • valve body If the flow is throttled for control purposes and the For this purpose, the valve body is displaced in the direction of the valve seat, so flow separations occur in the diffuser with increasing closing movement of the valve body.
  • the overspeed of the flow is slowed down by swirling.
  • supersonic velocities of the flow behind the valve seat are increasingly generated, which are reduced by compression surges.
  • both forms of flow slowdown or loss generation by swirling or by compression shocks cause a highly unsteady flow with pronounced coarse turbulence, with pulsation and with back and forth swaying of the flow which initially runs behind the valve seat as a free jet.
  • the pressure fluctuations generated in this way then act as undesirable vibration excitation on the valve body.
  • the invention is therefore based on the object of providing a control valve in which the alternating forces which excite the valve body to vibrate are minimized.
  • the invention is based on the knowledge that a Stabilization of the flow on the diffuser wall can be achieved if the acceleration of the flow at the throttle point between the valve body and the valve seat has a dominant effect in the axial direction and the radial component of the acceleration remains as small as possible. It was also found that such an influencing of the acceleration in the sense of a large axial component and a small radial component can be realized in that the convergent channel part has the contour of a circular truncated cone and merges into the adjoining channel part without a sharp edge but with a curvature.
  • the desired effect ie a noticeable stabilization of the flow
  • cone angle of the circular truncated cone is 65 ° or less.
  • cone angles of 60 ° or less are preferably selected, as a result of which a particularly efficient stabilization of the flow is achieved.
  • the aerodynamically favorable shape of the control valve according to the invention can be further improved in that the inner wall of the valve housing merges into the frustoconical contour without steps and edges in the inlet region of the convergent duct part.
  • a steady transition in the mathematical sense is not necessary.
  • the truncated cone-shaped convergent channel part merges with the curvature into the adjoining channel part. It is provided in a first preferred embodiment that the convergent channel part with the curvature passes directly into the divergent channel part of the diffuser. According to a second preferred embodiment, it is also possible for the convergent channel part with the curvature merges into a cylindrical channel part, which is followed by the divergent channel part of the diffuser. The cylindrical channel part acts on the flow as an additional calming zone and also increases the distance between the diffuser, which is particularly critical in terms of instabilities, and the valve body.
  • the cross-sectional profile of the control valve can be interpreted as a convergent-divergent channel, the valve seat 4 in the convergent channel part 6 being in front of the narrowest cross-section f and the divergent channel part being formed by the diffuser 5.
  • the Contour of the convergent-divergent channel in the area of the valve seat 4, the narrowest cross-section f and the initial area of the divergent channel part or diffuser 5 is formed by a valve seat bushing 7 made of wear-resistant material and inserted into the valve housing 1.
  • the valve body 3 is designed as a piston and is guided in the axial direction within a valve guide 8, which is designed as a cylinder and is fixedly arranged in the valve housing 1.
  • the stroke position of the valve body 3, which determines the throttling of the steam flow S, is set in the direction of the longitudinal axis L of the valve housing 1 via a valve spindle 9 which is positively connected to the valve body 3 by an actuator not shown in the drawing.
  • the convergent channel part 6 has the contour of a circular truncated cone, which is defined by the dash-dotted cone surface line KM and the cone angle 2a. This cone angle 2a is 60 0 in the exemplary embodiment shown. Upstream, the frustoconical contour of the convergent channel part 6 merges into the inner wall of the valve housing 1 without steps or edges, while downstream it merges into the divergent channel part of the diffuser 5 with a curvature 10.
  • FIG. 3 shows a variant in the cross-sectional profile of the convergent-divergent channel.
  • the frustoconical contour of the convergent duct part 6 merges with a curvature 10 'into a cylindrical duct part 11, to which the divergent duct part of a diffuser 5' then directly, ie without further curvature closes.
  • the valve seat bushing, which forms the contour of the cylindrical channel part, is designated 7 'in this variant.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)
  • Control Of Turbines (AREA)
  • Details Of Valves (AREA)

Abstract

Control valve, especially for controlling and regulating steam turbines, the valve body of which, movable in a valve guide, is associated with a valve seat, the valve seat being located in the region of a convergent channel part (6) of the valve housing (1) to which the divergent channel part of a diffuser (5) is connected. The alternating forces exciting the valve body to vibrate are minimised, and stabilisation of the flow on the diffuser wall is achieved in that the convergent channel part (6) has the contour of a circular truncated cone and the transition into the divergent channel part of the diffuser (5), or into a cylindrical channel part connected upstream of the diffuser, takes place by means of a bend (10). The cone angle (2 alpha ) of the circular truncated cone must not exceed 65 DEG in this case. Preferably, cone angles (2 alpha ) are selected which are 60 DEG or less. <IMAGE>

Description

Die Erfindung bezieht sich auf ein Stellventil, insbesondere zur Steuerung und Regelung von Dampfturbinen, gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a control valve, in particular for controlling and regulating steam turbines, according to the preamble of patent claim 1.

Derartige Stellventile, die beispielsweise aus der Siemens-Zeitschrift 41 (1967), Beiheft "Dampfturbinen großer Leistung", Seiten 75 und 76, bekannt sind, sollen einerseits durch Verändern der Hubstellung des Ventilkörpers eine gewünschte Drosselcharakteristik gewährleisten und andererseits in voll geöffnetem, d. h. in ausgesteuertem Zustand möglichst geringe Gefälleverluste verursachen. Darüber hinaus sollen im Hinblick auf Grenzen der Baumaße und der Leistung der zugehörigen Stellantriebe die Verstellkräfte klein gehalten werden. Bei den im Dampfturbinenbau zumeist verwendeten Einsitzventilen werden die Verstellkräfte durch die Wahl eines relativ geringen Durchmessers des Ventilkörpers vermindert. Im engsten Querschnitt hinter dem Ventilsitz ergeben sich damit schon im voll geöffneten Zustand des Stellventils hohe Strömungsgeschwindigkeiten. Um die Gefälleverluste in der nachfolgenden Rohrleitung klein zu halten, wird dann die Strömungsgeschwindigkeit in dem hinter dem Ventilsitz angeordneten Diffusor verlustarm verlangsamt. Bei diesem Querschnittsverlauf des Stellventils, der als konvergent-divergenter Kanal aufgefaßt werden kann, ergeben sich tiefste Drucke in dem engsten Querschnitt gefolgt von einem Druckanstieg längs des Diffusors.Such control valves, which are known, for example, from Siemens magazine 41 (1967), supplement "Steam turbines of great output", pages 75 and 76, are intended, on the one hand, to ensure a desired throttle characteristic by changing the stroke position of the valve body and, on the other hand, in a fully open, ie. H. cause the lowest possible gradient losses when driven. In addition, the adjustment forces should be kept small with regard to the limits of the dimensions and the performance of the associated actuators. In the single-seat valves mostly used in steam turbine construction, the adjusting forces are reduced by the selection of a relatively small diameter of the valve body. In the narrowest cross section behind the valve seat, high flow velocities result even when the control valve is fully open. In order to keep the gradient losses in the subsequent pipeline small, the flow velocity in the diffuser arranged behind the valve seat is then slowed down with little loss. With this cross-sectional profile of the control valve, which can be regarded as a convergent-divergent channel, the lowest pressures result in the narrowest cross section, followed by an increase in pressure along the diffuser.

Wird zu Steuerungszwecken die Strömung gedrosselt und der Ventilkörper hierzu in Richtung des Ventilsitzes verschoben, so kommt es im Diffusor in mit der Schließbewegung des Ventilkörpers zunehmendem Maße zu Strömungsablösungen. Die Übergeschwindigkeiten der Strömung werden dabei durch Verwirbeln verlangsamt. Bei stärkerer Drosselung werden zunehmend Überschallgeschwindigkeiten der Strömung hinter dem Ventilsitz erzeugt, welche durch Verdichtungsstöße abgebaut werden. Beide Formen der Strömungsverlangsamung bzw. Verlusterzeugung durch Verwirbeln oder durch Verdichtungsstöße bewirken jedoch einen stark instationären Strömungsverlauf mit ausgeprägter Grobturbulenz, mit Pulsieren und mit Hin- und Herschwanken der hinter dem Ventilsitz zunächst als Freistrahl verlaufenden Strömung. Die hierdurch erzeugten Druckschwankungen wirken dann als unerwünschte Schwingungsanregung auf den Ventilkörper.If the flow is throttled for control purposes and the For this purpose, the valve body is displaced in the direction of the valve seat, so flow separations occur in the diffuser with increasing closing movement of the valve body. The overspeed of the flow is slowed down by swirling. With greater throttling, supersonic velocities of the flow behind the valve seat are increasingly generated, which are reduced by compression surges. However, both forms of flow slowdown or loss generation by swirling or by compression shocks cause a highly unsteady flow with pronounced coarse turbulence, with pulsation and with back and forth swaying of the flow which initially runs behind the valve seat as a free jet. The pressure fluctuations generated in this way then act as undesirable vibration excitation on the valve body.

Besonders starke Schwankungen können auch schon bei relativ schwacher Drosselung auftreten. Es ist für eine Diffusorströmung charakteristisch, daß der Beginn der Strömungsablösung instationär verläuft, da es zwischen noch anliegender und schon abgelöster Strömung zu stochastischem Wechsel kommt. Die hierdurch ausgelösten Zusammenbrüche des Druckanstieges im Diffusor und die davon ausgehenden starken Druckstöße wirken ebenfalls als Schwingungsanregungen auf den Ventilkörper.Particularly strong fluctuations can occur even with relatively weak throttling. It is characteristic of a diffuser flow that the start of the flow separation is transient, since there is a stochastic change between the flow that is still present and the flow that has already been detached. The resulting breakdowns in the pressure increase in the diffuser and the resulting strong pressure surges also act as vibration excitations on the valve body.

Der Erfindung liegt daher die Aufgabe zugrunde, ein Stellventil zu schaffen, bei welchem die den Ventilkörper zu Schwingungen anregenden Wechselkräfte minimiert werden.The invention is therefore based on the object of providing a control valve in which the alternating forces which excite the valve body to vibrate are minimized.

Diese Aufgabe wird erfindungsgemäß durch die im kennzeichnenden Teil des Patentanspruchs 1 angegebenen Merkmale gelöst.This object is achieved by the features specified in the characterizing part of patent claim 1.

Der Erfindung liegt die Erkenntnis zugrunde, daß eine Stabilisierung der Strömung an der Diffusorwand dann erreicht werden kann, wenn die Beschleunigung der Strömung an der Drosselstelle zwischen Ventilkörper und Ventilsitz dominierend in axialer Richtung wirkt und die Radialkomponente der Beschleunigung möglichst klein bleibt. Es wurde ferner herausgefunden, daß eine derartige Beeinflussung der Beschleunigung im Sinne einer großen Axialkomponente und einer geringen Radialkomponente dadurch realisiert werden kann, daß der konvergente Kanalteil die Kontur eines Kreiskegelstumpfes aufweist und ohne scharfe Kante, sondern mit einer Krümmung in den daran anschließenden Kanalteil übergeht. Bei einem derartigen Querschnittsverlauf des konvergenten Kanalteils tritt der gewünschte Effekt, d. h. eine merkliche Stabilisierung der Strömung aber erst dann ein, wenn der Kegelwinkel des Kreiskegelstumpfes 650 oder weniger beträgt. Vorzugsweise werden jedoch Kegelwinkel von 60° oder weniger gewählt, wodurch eine besonders effiziente Stabilisierung der Strömung erzielt wird.The invention is based on the knowledge that a Stabilization of the flow on the diffuser wall can be achieved if the acceleration of the flow at the throttle point between the valve body and the valve seat has a dominant effect in the axial direction and the radial component of the acceleration remains as small as possible. It was also found that such an influencing of the acceleration in the sense of a large axial component and a small radial component can be realized in that the convergent channel part has the contour of a circular truncated cone and merges into the adjoining channel part without a sharp edge but with a curvature. With such a cross-sectional profile of the convergent channel part, the desired effect, ie a noticeable stabilization of the flow, only occurs when the cone angle of the circular truncated cone is 65 ° or less. However, cone angles of 60 ° or less are preferably selected, as a result of which a particularly efficient stabilization of the flow is achieved.

Die strömungstechnisch günstige Formgebung des erfindungsgemäßen Stellventils kann dadurch noch weiter verbessert werden, daß im Einlaufbereich des konvergenten Kanalteils die Innenwandung des Ventilgehäuses stufen- und kantenlos in die kreiskegelstumpfförmige Kontur übergeht. Eine Stetigkeit des Übergangs im mathematischen Sinne ist dabei jedoch nicht erforderlich.The aerodynamically favorable shape of the control valve according to the invention can be further improved in that the inner wall of the valve housing merges into the frustoconical contour without steps and edges in the inlet region of the convergent duct part. However, a steady transition in the mathematical sense is not necessary.

Wie bereits erwähnt wurde, ist es für die erwünschte Stabilisierung der Strömung erforderlich, daß der kreiskegelstumpfförmige konvergente Kanalteil mit einer Krümmung in den daran anschließenden Kanalteil übergeht. Dabei ist bei einer ersten bevorzugten Ausführungsform vorgesehen, daß der konvergente Kanalteil mit der Krümmung unmittelbar in den divergenten Kanalteil des Diffusors übergeht. Gemäß einer zweiten bevorzugten Ausführung ist es aber auch möglich, daß der konvergente Kanalteil mit der Krümmung in einen zylindrischen Kanalteil übergeht, an welchen sich der divergente Kanalteil des Diffusors anschließt. Der zylindrische Kanalteil wirkt dabei auf die Strömung als zusätzliche Beruhigungszone und vergrößert außerdem den Abstand zwischen dem in Bezug auf Instabilitäten besonders kritischen Diffusor und dem Ventilkörper.As already mentioned, for the desired stabilization of the flow, it is necessary that the truncated cone-shaped convergent channel part merges with the curvature into the adjoining channel part. It is provided in a first preferred embodiment that the convergent channel part with the curvature passes directly into the divergent channel part of the diffuser. According to a second preferred embodiment, it is also possible for the convergent channel part with the curvature merges into a cylindrical channel part, which is followed by the divergent channel part of the diffuser. The cylindrical channel part acts on the flow as an additional calming zone and also increases the distance between the diffuser, which is particularly critical in terms of instabilities, and the valve body.

Im folgenden sind Aufbau und Wirkungsweise von Ausführungsbeispielen der Erfindung anhand der Zeichnung näher erläutert. Dabei zeigt:

  • Fig. 1 einen teilweisen Längsschnitt durch das Ventilgehäuse eines Stellventils für Dampfturbinen,
  • Fig. 2 in größer gewähltem Maßstab einen Ausschnitt aus der Fig. 1 mit dem Querschnittsverlauf im Bereich des Ventilsitzes und des hinter dem Ventilsitz liegenden Kanals und
  • Fig. 3 eine Variante des in Fig. 2 dargestellten Querschnittsverlaufs.
  • Fig. 1 zeigt einen Längsschnitt durch einen Teil des Ventilgehäuses 1 eines Stellventils. Die durch Pfeile S angedeutete Dampfströmung tritt durch einen seitlichen Eintrittsstutzen 2 in das Ventilgehäüse ein, durchströmt einen zwischen der Kegellippe 31 eines Ventilkörpers 3 und einem Ventilsitz 4 gebildeten Ringquerschnitt und tritt dann nach unten aus dem Ventilgehäuse 1 aus, wobei der Austrittsbereich als Diffusor 5 ausgebildet ist.
The structure and mode of operation of exemplary embodiments of the invention are explained in more detail below with reference to the drawing. It shows:
  • 1 is a partial longitudinal section through the valve housing of a control valve for steam turbines,
  • Fig. 2 on a larger scale a section of Fig. 1 with the cross-sectional profile in the region of the valve seat and the channel behind the valve seat and
  • Fig. 3 shows a variant of the cross-sectional profile shown in Fig. 2.
  • Fig. 1 shows a longitudinal section through part of the valve housing 1 of a control valve. The steam flow indicated by arrows S enters the valve housing through a lateral inlet connection 2, flows through an annular cross section formed between the cone lip 31 of a valve body 3 and a valve seat 4 and then emerges downwards from the valve housing 1, the outlet area being designed as a diffuser 5 is.

Der Querschnittsverlauf des Stellventils kann dabei als konvergent-divergenter Kanal aufgefaßt werden, wobei der Ventilsitz 4 in dem konvergenten Kanalteil 6 vor dem engsten Querschnitt f liegt und wobei der divergente Kanalteil durch den Diffusor 5 gebildet wird. Dabei ist die Kontur des konvergent-divergenten Kanals im Bereich des Ventilsitzes 4, des engsten Querschnittes f und des Anfangsbereichs des divergenten Kanalteils bzw. Diffusors 5 durch eine aus verschleißfestem Material bestehende und in das Ventilgehäuse 1 eingesetzte Ventilsitzbuchse 7 gebildet.The cross-sectional profile of the control valve can be interpreted as a convergent-divergent channel, the valve seat 4 in the convergent channel part 6 being in front of the narrowest cross-section f and the divergent channel part being formed by the diffuser 5. Here is the Contour of the convergent-divergent channel in the area of the valve seat 4, the narrowest cross-section f and the initial area of the divergent channel part or diffuser 5 is formed by a valve seat bushing 7 made of wear-resistant material and inserted into the valve housing 1.

Der Ventilkörper 3 ist als Kolben ausgebildet, und innerhalb einer als Zylinder ausgebildeten und im Ventilgehäuse 1 fest angeordneten Ventilführung 8 in axialer Richtung geführt. Die Hubstellung des Ventilkörpers 3, welche die Drosselung der Dampfströmung S bestimmt, wird dabei in Richtung der Längsachse L des Ventilgehäuses 1 über eine formschlüssig mit dem Ventilkörper 3 verbundene Ventilspindel 9 von einem in der Zeichnung nicht dargestellten Stellantrieb eingestellt.The valve body 3 is designed as a piston and is guided in the axial direction within a valve guide 8, which is designed as a cylinder and is fixedly arranged in the valve housing 1. The stroke position of the valve body 3, which determines the throttling of the steam flow S, is set in the direction of the longitudinal axis L of the valve housing 1 via a valve spindle 9 which is positively connected to the valve body 3 by an actuator not shown in the drawing.

Um nun die den Ventilkörper 3 zu Schwingungen anregenden Wechselkräfte zu minimieren, ist ein in dem Ausschnitt der Fig. 2 im Detail dargestellter Querschnittsverlauf des konvergent-divergenten Kanals vorgesehen. Der konvergente Kanalteil 6 weist dabei die Kontur eines Kreiskegelstumpfes auf, welcher durch die strichpunktierte Kegelmantellinie KM und den Kegelwinkel 2a definiert ist. Dieser Kegelwinkel 2a beträgt im dargestellten Ausführungsbeispiel 600. Stromaufwärts geht die kreiskegelstumpfförmige Kontur des konvergenten Kanalteils 6 ohne Stufen oder Kanten in die Innenwandung des Ventilgehäuses 1 über, während sie stromabwärts mit einer Krümmung 10 in den divergenten Kanalteil des Diffusors 5 übergeht.In order to minimize the alternating forces that excite the valve body 3 to vibrate, a cross-sectional profile of the convergent-divergent channel shown in detail in the detail in FIG. 2 is provided. The convergent channel part 6 has the contour of a circular truncated cone, which is defined by the dash-dotted cone surface line KM and the cone angle 2a. This cone angle 2a is 60 0 in the exemplary embodiment shown. Upstream, the frustoconical contour of the convergent channel part 6 merges into the inner wall of the valve housing 1 without steps or edges, while downstream it merges into the divergent channel part of the diffuser 5 with a curvature 10.

Fig. 3 zeigt eine Variante im Querschnittsverlauf des konvergent-divergenten Kanals. Hier geht die kreiskegelstumpfförmige Kontur des konvergenten Kanalteils 6 mit einer Krümmung 10' in einen zylindrischen Kanalteil 11 über, an welchen sich dann der divergente Kanalteil eines Diffusors 5' direkt, d. h. ohne weitere Krümmung anschließt. Die Ventilsitzbuchse, welche die Kontur des zylindrischen Kanalteils bildet, ist bei dieser Variante mit 7' bezeichnet.3 shows a variant in the cross-sectional profile of the convergent-divergent channel. Here the frustoconical contour of the convergent duct part 6 merges with a curvature 10 'into a cylindrical duct part 11, to which the divergent duct part of a diffuser 5' then directly, ie without further curvature closes. The valve seat bushing, which forms the contour of the cylindrical channel part, is designated 7 'in this variant.

Bei dem in Fig. 2 dargestellten Querschnittsverlauf und bei dem in Fig. 3 dargestellten Querschnittsverlauf wird erreicht, daß die Beschleunigung der Dampfströmung S an der Drosselstelle zwischen der Kegellippe 31 und dem Ventilsitz 4 dominierend in Richtung der Längsachse L wirkt, während die Radialkomponente der Beschleunigung normal zur Längsachse L äußerst klein bleibt. Hierdurch wird die Dampfströmung S an der Wandung des Diffusors 5 bzw. an der Wandung des Diffusors 5' stabilisiert. Bei dem in Fig. 3 dargestellten Querschnittsverlauf wirkt der zylindrische Kanalteil 11 noch als zusätzliche Beruhigungszone.In the cross-sectional profile shown in Fig. 2 and in the cross-sectional profile shown in Fig. 3 it is achieved that the acceleration of the steam flow S at the throttle point between the cone lip 31 and the valve seat 4 acts dominantly in the direction of the longitudinal axis L, while the radial component of the acceleration remains extremely small normal to the longitudinal axis L. As a result, the steam flow S is stabilized on the wall of the diffuser 5 or on the wall of the diffuser 5 '. 3, the cylindrical channel part 11 also acts as an additional calming zone.

Claims (5)

1. Stellventil, insbesondere zur Steuerung und Regelung von Dampfturbinen, dessen in einer Ventilführung verschiebbarer Ventilkörper einem Ventilsitz zugeordnet ist, wobei der Ventilsitz im Bereich eines konvergenten Kanalteils des Ventilgehäuses liegt, an welchen sich der divergente Kanalteil eines Diffusors anschließt, gekennzeichnet durch folgende Merkmale: a) der konvergente Kanalteil (6) weist die Kontur eines Kreiskegelstumpfes auf; b) der Kegelwinkel (2a) des Kreiskegelstumpfes beträgt höchstens 65°; c) der konvergente Kanalteil (6) geht mit einer Krümmung (10; 11) in den daran anschließenden Kanalteil über. 1.Control valve, in particular for controlling and regulating steam turbines, the valve body of which is displaceable in a valve guide is assigned to a valve seat, the valve seat being in the region of a convergent duct part of the valve housing, to which the divergent duct part of a diffuser is connected, characterized by the following features: a) the convergent channel part (6) has the contour of a circular truncated cone; b) the cone angle (2a) of the circular truncated cone is at most 65 °; c) the convergent duct part (6) merges with a curvature (10; 11) into the adjoining duct part. 2. Stellventil nach Anspruch 1, dadurch gekennzeichnet, daß im Einlaufbereich des konvergenten Kanalteils (6) die Innenwandung des Ventilgehäuses (1) stufen- und kantenlos in die kreiskegelstumpfförmige Kontur übergeht.2. Control valve according to claim 1, characterized in that in the inlet region of the convergent channel part (6) the inner wall of the valve housing (1) merges into the circular truncated cone-shaped contour without steps and edges. 3. Stellventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Kegelwinkel (2a) des Kreiskegelstumpfes höchstens 60° beträgt.3. Control valve according to claim 1 or 2, characterized in that the cone angle (2a) of the circular truncated cone is at most 60 °. 4. Stellventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet , daß der konvergente Kanalteil (6) mit der Krümmung (10) unmittelbar in den divergenten Kanalteil des Diffusors (5) übergeht.4. Control valve according to one of the preceding claims, characterized in that the convergent channel part (6) with the curvature (10) passes directly into the divergent channel part of the diffuser (5). 5. Stellventil nach einem der Ansprüche 1 bis 3, d a - durch gekennzeichnet, daß der konvergente Kanalteil (6) mit der Krümmung (10') in einen zylindrischen Kanalteil (11) übergeht, an welchen sich der divergente Kanalteil des Diffusors (5') anschließt.5. Control valve according to one of claims 1 to 3, since - characterized in that the convergent channel part (6) merges with the curvature (10 ') into a cylindrical channel part (11) to which the divergent channel part of the diffuser (5') connects.
EP82108333A 1981-09-22 1982-09-09 Control valve, especially for controlling and regulating steam turbines Ceased EP0075211A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3137720 1981-09-22
DE19813137720 DE3137720A1 (en) 1981-09-22 1981-09-22 CONTROL VALVE, ESPECIALLY FOR CONTROL AND REGULATION OF STEAM TURBINES

Publications (2)

Publication Number Publication Date
EP0075211A2 true EP0075211A2 (en) 1983-03-30
EP0075211A3 EP0075211A3 (en) 1983-07-20

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP82108333A Ceased EP0075211A3 (en) 1981-09-22 1982-09-09 Control valve, especially for controlling and regulating steam turbines

Country Status (3)

Country Link
EP (1) EP0075211A3 (en)
JP (1) JPS5865904A (en)
DE (1) DE3137720A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0200509A1 (en) * 1985-04-25 1986-11-05 Westinghouse Electric Corporation Plug for a modulating control valve for a steam turbine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4328626A1 (en) * 1993-08-27 1995-03-02 Motan Verfahrenstechnik Method for operating a conveyor pipeline with dense-stream conveyance and apparatus for carrying out the method
NO334212B1 (en) * 2005-08-23 2014-01-13 Typhonix As Device at control valve
DE102010024342B4 (en) * 2010-06-18 2014-10-23 Siemens Aktiengesellschaft Control valve for a steam turbine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB560793A (en) * 1941-11-04 1944-04-20 Bendix Aviat Corp Improvements in or relating to valves
US2561214A (en) * 1950-07-26 1951-07-17 Gen Electric Combination balanced shutoff and throttling valve assembly
DE1425730A1 (en) * 1963-06-20 1968-12-12 Zikesch Dipl Ing Herbert Drain valve
US3458170A (en) * 1966-02-09 1969-07-29 Sulzer Ag Pressure gradient valve
FR2430566A1 (en) * 1978-07-07 1980-02-01 Bbc Brown Boveri & Cie REGULATION VALVE, PARTICULARLY FOR HIGH PRESSURE STEAM
US4337788A (en) * 1981-02-02 1982-07-06 Smith International Inc. High pressure valve

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH474702A (en) * 1967-05-23 1969-06-30 Sulzer Ag Valve
DE2944670C2 (en) * 1979-11-06 1982-11-25 Industrie- und Pipeline-Service Gerhard Kopp GmbH, 4450 Lingen High pressure shut-off valve
DE2948639C2 (en) * 1979-12-04 1981-12-03 C.H. Zikesch GmbH, 4230 Wesel Shut-off and control valve

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB560793A (en) * 1941-11-04 1944-04-20 Bendix Aviat Corp Improvements in or relating to valves
US2561214A (en) * 1950-07-26 1951-07-17 Gen Electric Combination balanced shutoff and throttling valve assembly
DE1425730A1 (en) * 1963-06-20 1968-12-12 Zikesch Dipl Ing Herbert Drain valve
US3458170A (en) * 1966-02-09 1969-07-29 Sulzer Ag Pressure gradient valve
FR2430566A1 (en) * 1978-07-07 1980-02-01 Bbc Brown Boveri & Cie REGULATION VALVE, PARTICULARLY FOR HIGH PRESSURE STEAM
US4337788A (en) * 1981-02-02 1982-07-06 Smith International Inc. High pressure valve

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0200509A1 (en) * 1985-04-25 1986-11-05 Westinghouse Electric Corporation Plug for a modulating control valve for a steam turbine

Also Published As

Publication number Publication date
EP0075211A3 (en) 1983-07-20
JPS5865904A (en) 1983-04-19
DE3137720A1 (en) 1983-04-07

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