EP0808992B1 - Rotary slide valve for the control of steam flow to a steam turbine - Google Patents

Rotary slide valve for the control of steam flow to a steam turbine Download PDF

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Publication number
EP0808992B1
EP0808992B1 EP97108100A EP97108100A EP0808992B1 EP 0808992 B1 EP0808992 B1 EP 0808992B1 EP 97108100 A EP97108100 A EP 97108100A EP 97108100 A EP97108100 A EP 97108100A EP 0808992 B1 EP0808992 B1 EP 0808992B1
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EP
European Patent Office
Prior art keywords
rotary ring
rotary
ring
steam
control
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EP97108100A
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German (de)
French (fr)
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EP0808992A2 (en
EP0808992A3 (en
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Richard Geist
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Alstom SA
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Alstom SA
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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
    • F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
    • F01D17/167—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes of vanes moving in translation
    • 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
    • F01D17/143—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 the shiftable member being a wall, or part thereof of a radial diffuser

Definitions

  • the invention relates to a radial rotary slide valve according to the preamble of claim 1.
  • Radial rotary valves are used to control the steam throughput in a steam turbine. With an immobile fixed ring and one concentric on it rotating ring, its angular position by a servo motor is changeable, it is possible to control slots provided in both rings more or less open or close.
  • a radial rotary valve is known from US Pat. No. 3,127,909, in which by rotating one elastic band opened relative to the rotary valve housing of the rotary valve or can be closed.
  • the elastic band lies on a cylindrical surface of the Housing, which has inlet openings that are distributed over the circumference.
  • the elastic band has corresponding inlet openings.
  • An axial rotary slide valve is known from DE 44 25 344 A1, in which the control profiles are made of profile heads assigned to the rotating ring and profile ends assigned to the fixed ring exist and by their position to each other that belong to a steam channel Open or close control slots.
  • the object of the invention is therefore a radial rotary valve according to the preamble of To create claim 1, in which it is possible to optimize the width of the sliding gap and that Risk of clamping the system, which is extremely dangerous for turbine operation avoid or at least significantly reduce.
  • the turbine housing is split into a top and bottom part by a parting line also fixed and rotating ring in a radial rotary valve basically divided.
  • the rotating ring part and rotating ring part are not rigid, but are connected to one another by suitable connecting means such that the distance from at least two opposite ends of these two ring halves is changeable. This makes it possible to change the inner diameter of the rotating ring, and it can provide the sliding play between the rotating ring and the fixed ring required for rotary movements be adjusted.
  • control profiles determine the type of control slots that in turn lead to the steam channel belong and opened or closed according to the direction of the rotating ring become. It is advantageous to give the control profiles an aerodynamic shape.
  • the profile heads are assigned to the fixed ring, while the profile ends in Fixed ring. The overall profile then comes with a full control slot opening Validity.
  • connecting means that are equipped with appropriate tools, are preferably adjustable by actuating screw elements. This would be it is possible to optimize the required sliding play in each individual case.
  • FIGS. 1 to 3 there is a radial rotary valve 1, 2 with its Fixed ring 1 and its outer rotating ring 2 arranged concentrically to it. Both the turbine housing 3 and the radial rotary valve 1, 2 are along a parting line 16 divided into upper and lower parts.
  • control profiles 4 the profile heads 4a of which are the rotary ring 2 and whose profile ends 4b are assigned to the fixed ring 1.
  • control slots 17 which belong to the steam channel 5 and in the present representations are fully open.
  • profile heads 4a and profile ends 4b form-fit one another and form their aerodynamically optimized shape provides only a relatively low resistance for the in Steam direction 7 flowing through from the steam duct front part 5a to the steam duct rear part 5b Steam. From here, the steam reaches the blades of the Turbine rotor 6.
  • the profile heads 4a can face each other move the profile ends 4b so far that the control slots 17 are completely closed become. With a reduced cross section of the control slots 17, the shape of the Control profiles 4 then no longer play such a large role.
  • A is used for rotatably adjusting the rotating ring 2 relative to the fixed ring 1 Servo motor, not shown, which acts on the rotary ring 2 via a link lever 10.
  • a link fork 11 with fork tines at the end of the link lever 10 11a, 11b, in which inwardly pointing bolts 12 are fastened, which are in the area the parting line 16 engage in corresponding bores in the rotating ring 2.
  • an increase in the inner diameter should only take place if the Dynamic friction exceeds a predetermined limit, then this value to decrease an appropriate amount.
  • an appropriately dimensioned Compression spring 15 is provided, which is gripped by the head of a collar screw 14 and against a collar 19 of the rotating ring upper part 2a is pressed. Since the collar screw 14 in a threaded bush 13 of the rotating ring lower part 2b is screwed in, the rotating ring upper part 2a and lower ring part 2b of the compression spring 15 with its own spring force held together. Only if there is friction between the rotating ring 2 and the fixed ring 1 occurs that exceeds this spring force increases when the link lever is actuated 10 the gap in the area of the parting line 16 so far that the sliding friction drops and a rotary movement becomes possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
  • Sliding Valves (AREA)

Description

Die Erfindung betrifft einen Radialdrehschieber nach dem Oberbegriff des Anspruchs 1. Radialdrehschieber dienen zur Steuerung des Dampfdurchsatzes bei einer Dampfturbine. Mit einem unbeweglichen Festring und einem konzentrisch auf diesem drehbeweglich angeordneten Drehring, dessen Winkelstellung durch einen Servomotor veränderbar ist, gelingt es, in beiden Ringen vorgesehene Steuerschlitze mehr oder weniger zu öffnen oder zu schließen.The invention relates to a radial rotary slide valve according to the preamble of claim 1. Radial rotary valves are used to control the steam throughput in a steam turbine. With an immobile fixed ring and one concentric on it rotating ring, its angular position by a servo motor is changeable, it is possible to control slots provided in both rings more or less open or close.

Im Dampfturbinenbau verwendet man zur Steuerung von Dampfentnahmen fast ausschließlich Ventile, obwohl Drehschieber im Vergleich hierzu relativ einfach aufgebaut sind und auch noch einige andere Vorzüge aufweisen. Problematisch sind allerdings die Gleitbedingungen, unter denen jeweils der Drehring auf dem Festring drehbeweglich verschiebbar sein muß. Von wesentlicher Bedeutung sind hierbei die durch statische Dampfkräfte erzeugten Druckverhältnisse, da diese für die Reibung zwischen den aufeinander gleitenden Teilen verantwortlich sind. Während Axialdrehschieber von dieser Problematik voll getroffen werden, ergibt sich bei Radialdrehschiebern durch das Gegeneinanderwirken der statischen Dampfkräfte automatisch eine statische Entlastung des außenliegenden Drehrings.In steam turbine construction, control of steam withdrawals is used almost exclusively Valves, although rotary valves are relatively simple compared to this are and also have some other advantages. However, they are problematic Sliding conditions under which the rotating ring rotates on the fixed ring must be movable. Static are essential Steam forces create pressure ratios, as these create friction between each other sliding parts are responsible. While axial rotary valve from this The problem can be fully met in radial rotary valves due to the Counteracting the static steam forces automatically relieves the static external rotating ring.

Aus der DE 42 14 775 A1 ist ein Axialdrehschieber bekannt, bei dem mit Hilfe von Axialnadeldrehkränzen die Gleitreibung des Drehrings weitgehend durch eine Rollenreibung abgelöst ist. Eine entsprechende Rollenlagerung ist selbstverständlich auch bei Radialdrehschiebern möglich, aber nur dann akzeptabel, wenn der hierbei entstehende Gleitspalt so klein ist, dass die dadurch bedingten Dampfverluste gering bleiben. Ein sehr schmaler Gleitspalt ist aber nicht nur wegen geringer Fertigungstoleranzen schwer zu beherrschen, sondern kann auch unter normalen Betriebsbedingungen zu Problemen führen. Drehschieber unterliegen beim Einsatz Temperatureinwirkungen von einigen hundert Grad. Durch uneinheitliche Wärmedehnungen beim Drehring einerseits und Festring andererseits können große, jede Bewegung verhindernde Hemmkräfte entstehen, weil die vorgesehenen Spiele verschwinden und dadurch regelrechte "Klemmverbindungen" erzeugt werden.From DE 42 14 775 A1 an axial rotary valve is known, in which with the help of Axial needle slewing rings, the sliding friction of the rotating ring largely through a roller friction is replaced. A corresponding roller bearing is of course also at Radial rotary valves possible, but only acceptable if the resulting one The sliding gap is so small that the resulting steam losses remain low. A very Narrow sliding gap is difficult not only because of low manufacturing tolerances control, but can also lead to problems under normal operating conditions. Rotary vane are subject to temperature influences of several hundred degrees during use. Due to inconsistent thermal expansion in the rotating ring on the one hand and the fixed ring on the other There can be great inhibitory forces that prevent every movement because the intended ones Games disappear and real "clamp connections" are created.

Aus der US 3,127,909 ist ein Radialdrehschieber bekannt, bei dem durch Verdrehen eines elastischen Bandes relativ zu dem Drehschiebergehäuse der Drehschieber geöffnet oder geschlossen werden kann. Das elastische Band liegt auf einer zylindrischen Fläche des Gehäuses auf, welche Einlassöffnungen, die über den Umfang verteilt sind, aufweist. Das elastische Band weist entsprechende Einlassöffnungen auf. Durch Einleiten der zum Verdrehen des Bandes notwendigen Kräfte wird das Band aufgeweitet, so dass die Reibungskräfte verringert werden. Allerdings ist diese Ausführungsform nur für sehr geringe Betätigungskräfte einsetzbar. Auch können die von großen Gas- oder Dampfströmen auf das Band ausgeübten Kräfte von diesem nicht aufgenommen werden.A radial rotary valve is known from US Pat. No. 3,127,909, in which by rotating one elastic band opened relative to the rotary valve housing of the rotary valve or can be closed. The elastic band lies on a cylindrical surface of the Housing, which has inlet openings that are distributed over the circumference. The elastic band has corresponding inlet openings. By initiating the Twisting the band necessary forces the band is expanded so that the Frictional forces are reduced. However, this embodiment is only for very small ones Actuating forces can be used. Also from large gas or steam flows on the Band exerted forces are not absorbed by this.

Aus der DE 44 25 344 A1 ist ein Axialdrehschieber bekannt, bei dem die Steuerprofile aus dem Drehring zugeordneten Profilköpfen und dem Festring zugeordneten Profilenden bestehen und diese durch ihre Stellung zueinander die zu einem Dampfkanal gehörigen Steuerschlitze öffnen oder schließen.An axial rotary slide valve is known from DE 44 25 344 A1, in which the control profiles are made of profile heads assigned to the rotating ring and profile ends assigned to the fixed ring exist and by their position to each other that belong to a steam channel Open or close control slots.

Aufgabe der Erfindung ist es deshalb, einen Radialdrehschieber nach dem Oberbegriff des Anspruchs 1 zu schaffen, bei dem es gelingt die Breite des Gleitspaltes zu optimieren und das Risiko einer für den Turbinenbetrieb äußerst gefährlichen Klemmung des Systems zu vermeiden oder zumindest deutlich zu vermindern.The object of the invention is therefore a radial rotary valve according to the preamble of To create claim 1, in which it is possible to optimize the width of the sliding gap and that Risk of clamping the system, which is extremely dangerous for turbine operation avoid or at least significantly reduce.

Diese Aufgabe wird durch die im Anspruch 1 gekennzeichneten Merkmale gelöst. Zweckmäßige Ausgestaltungen und Weiterbildungen des Erfindungsgegenstandes sind in den Unteransprüchen genannt.This object is achieved by the features characterized in claim 1. Appropriate refinements and developments of the subject matter of the invention are in the Subclaims called.

So wie das Turbinengehäuse durch eine Teilfuge in ein Ober- und Unterteil gespalten ist, sind auch Fest- und Drehring bei einem Radialdrehschieber grundsätzlich geteilt. Im Unterschied zu herkömmlichen Konstruktionen ist es jedoch ein wesentlicher Vorteil der erfindungsgemäßen Lösung, dass Drehringoberteil und Drehringunterteil nicht starr, sondern durch geeignete Verbindungsmittel so miteinander verbunden sind, dass der Abstand von mindestens zwei sich gegenüberstehenden Enden dieser beiden Ringhälften veränderbar ist. Dadurch ist eine Veränderung des Drehring-Innendurchmessers ermöglicht, und es kann das für Drehbewegungen erforderliche Gleitspiel zwischen Drehring und Festring angepasst werden.Just as the turbine housing is split into a top and bottom part by a parting line also fixed and rotating ring in a radial rotary valve basically divided. The difference However, it is a major advantage of conventional constructions solution according to the invention that the rotating ring part and rotating ring part are not rigid, but are connected to one another by suitable connecting means such that the distance from at least two opposite ends of these two ring halves is changeable. This makes it possible to change the inner diameter of the rotating ring, and it can provide the sliding play between the rotating ring and the fixed ring required for rotary movements be adjusted.

Dadurch, dass zwei sich gegenüberstehende Enden der beiden Drehringhälften durch ein Scharnier zusammengehalten werden, wird nur ein Federelement benötigt.The fact that two opposite ends of the two rotating ring halves through one Hinge are held together, only one spring element is required.

Für den Einsatz des Federelementes an den beiden sich gegenüberstehenden Enden der beiden Drehringhälften, die nicht durch ein Scharnier verbunden sind, ist vorgesehen, dass hier eine Bundschraube angreift, die in eine Gewindebuchse der einen Drehringhälfte eingeschraubt ist. Mit ihrem Kopf erfasst die Bundschraube eine Druckfeder, die sich auf einem Kragen der anderen Drehringhälfte abstützt. Sobald Klemmkräfte auftreten, die größer sind als die von der Druckfeder ausgehende, die beiden Ringhälften verbindende Federkraft, vergrößert sich an dieser Stelle die Teilfuge zwischen den beiden Ringhälften und die Gleitreibung vermindert sich.For the use of the spring element at the two opposite ends of the two Rotary ring halves, which are not connected by a hinge, are provided here Attacks collar screw which is screwed into a threaded bushing of the one half of the rotating ring. The collar screw catches a compression spring with its head, which is located on a collar of the other half of the rotating ring. As soon as clamping forces occur that are greater than that of the spring force coming from the compression spring and connecting the two ring halves increases at this point the parting line between the two halves of the ring and the sliding friction Decreases.

Eine noch sicherere Öffnung der Teilfuge bei zu hoher Gleitreibung wird dadurch erreicht, dass ein die Verbindung zum Servomotor herstellender Anlenkhebel an einer Anlenkgabel endet, an deren Gabelzinken je ein nach innen weisender Bolzen befestigt ist und dass diese beiden Bolzen mittig zur Teilfuge in eine Bohrung eingreifen, die je zur Hälfte im Drehringoberteil und Drehringunterteil ausgespart ist.An even more secure opening of the parting line with excessive sliding friction is achieved that a link lever on a link fork that connects to the servo motor ends, on the fork tines of which an inward-pointing bolt is attached and that this center of both bolts Engage the parting joint in a hole, half of which is in the upper part of the rotating ring and The lower part of the rotating ring is recessed.

Die Steuerprofile bestimmen die Art der Steuerschlitze, die ihrerseits zum Dampfkanal gehören und entsprechend der Stellrichtung des Drehrings geöffnet oder geschlossen werden. Es ist vorteilhaft den Steuerprofilen eine aerodynamische Form zu geben. Hierbei werden dem Festring die Profilköpfe zugeordnet, während die Profilenden im Festring liegen. Das Gesamtprofil kommt dann bei voller Steuerschlitzöffnung zur Geltung.The control profiles determine the type of control slots that in turn lead to the steam channel belong and opened or closed according to the direction of the rotating ring become. It is advantageous to give the control profiles an aerodynamic shape. The profile heads are assigned to the fixed ring, while the profile ends in Fixed ring. The overall profile then comes with a full control slot opening Validity.

Obwohl das automatische Vergrößern des Gleitspiels sehr vorteilhaft ist, könnte man alternativ auch Verbindungsmittel vorsehen, die mit entsprechenden Werkzeugen, vorzugsweise durch Betätigung von Schraubelementen, einstellbar sind. Hierdurch wäre es möglich in jedem Einzelfall das benötigte Gleitspiel zu optimieren.Although automatically increasing glide play is very beneficial, you could alternatively also provide connecting means that are equipped with appropriate tools, are preferably adjustable by actuating screw elements. This would be it is possible to optimize the required sliding play in each individual case.

Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden im folgenden näher beschrieben. Es zeigen:

Fig. 1
einen radialen Schnitt durch ein Dampfturbinengehäuse im Bereich des Drehschiebers, mit Ober- und Unterteil und Verbindungsmitteln,
Fig. 2
ein vergrößertes Detail X des Radialdrehschiebers mit Verbindungsmitteln und Betätigungsmitteln des Servomotors,
Fig. 3
einen Schnitt durch die Betätigungsmittel nach Fig. 2 entlang der Schnittlinie AA im Bereich der Teilfuge.
Embodiments of the invention are shown in the drawings and are described in more detail below. Show it:
Fig. 1
a radial section through a steam turbine housing in the area of the rotary valve, with upper and lower part and connecting means,
Fig. 2
an enlarged detail X of the radial rotary valve with connecting means and actuating means of the servo motor,
Fig. 3
a section through the actuating means of FIG. 2 along the section line AA in the region of the parting line.

Das Verständnis der zu beschreibenden Anordnung wird erleichtert, wenn man die sich ergänzenden Details aller Fig. 1 bis 3 gemeinsam in die Betrachtung mit einbezieht. Innerhalb eines Turbinengehäuses 3 befindet sich ein Radialdrehschieber 1, 2 mit seinem Festring 1 und seinem konzentrisch dazu angeordneten, außenliegenden Drehring 2. Sowohl das Turbinengehäuse 3, als auch der Radialdrehschieber 1,2 sind entlang einerTeilfuge 16 in Ober- und Unterteile geteilt. Understanding the arrangement to be described is easier if you look at the additional details of all FIGS. 1 to 3 together in the consideration. Within a turbine housing 3 there is a radial rotary valve 1, 2 with its Fixed ring 1 and its outer rotating ring 2 arranged concentrically to it. Both the turbine housing 3 and the radial rotary valve 1, 2 are along a parting line 16 divided into upper and lower parts.

Die Dampfsteuerung erfolgt mit Steuerprofilen 4, deren Profilköpfe 4a dem Drehring 2 und deren Profilenden 4b dem Festring 1 zugeordnet sind. Zwischen den Steuerprofilen liegen Steuerschlitze 17, die zum Dampfkanal 5 gehören und in den vorliegenden Darstellungen voll geöffnet sind. Bei dieser Winkelstellung des Drehrings 2 zum Festring 1 liegen Profilköpfe 4a und Profilenden 4b formschlüssig aufeinander und bilden durch ihre aerodynamisch optimierte Form nur einen relativ geringen Widerstand für den in Dampfrichtung 7 vom Dampfkanal-Vorderteil 5a zum Dampfkanal-Hinterteil 5b durchströmenden Dampf. Von hier aus gelangt der Dampf dann zu den Laufschaufeln des Turbinenrotors 6. Durch Drehen des Drehrings 2 können sich die Profilköpfe 4a gegenüber den Profilenden 4b soweit verschieben, daß die Steuerschlitze 17 völlig geschlossen werden. Bei vermindertem Querschnitt der Steuerschlitze 17 spielt die Form der Steuerprofile 4 dann keine so große Rolle mehr.The steam is controlled using control profiles 4, the profile heads 4a of which are the rotary ring 2 and whose profile ends 4b are assigned to the fixed ring 1. Between the tax profiles are control slots 17, which belong to the steam channel 5 and in the present representations are fully open. With this angular position of the rotating ring 2 relative to the fixed ring 1 profile heads 4a and profile ends 4b form-fit one another and form their aerodynamically optimized shape provides only a relatively low resistance for the in Steam direction 7 flowing through from the steam duct front part 5a to the steam duct rear part 5b Steam. From here, the steam reaches the blades of the Turbine rotor 6. By turning the rotating ring 2, the profile heads 4a can face each other move the profile ends 4b so far that the control slots 17 are completely closed become. With a reduced cross section of the control slots 17, the shape of the Control profiles 4 then no longer play such a large role.

Zum drehbeweglichen Verstellen des Drehrings 2 gegenüber dem Festring 1 dient ein nicht dargestellter Servomotor, der über einen Anlenkhebel 10 am Drehring 2 angreift. Hierzu befindet sich am Ende des Anlenkhebels 10 eine Anlenkgabel 11 mit Gabelzinken 11a, 11b, in denen nach innen weisende Bolzen 12 befestigt sind, die im Bereich der Teilfuge 16 in entsprechende Bohrungen im Drehring 2 eingreifen. Bei der in soweit beschriebenen Anordnung würde eine vom Servomotor ausgehende Zugkraft den Drehringunterteil 2b vom Drehringoberteil 2a wegziehen während sich bei einer Druckkraft die Verhältnisse umkehren würden. In beiden Fällen würde sich aber der Innendurchmesser des Drehrings 2 bzw. der in der Teilfuge 16 liegende Spalt vergrößern.A is used for rotatably adjusting the rotating ring 2 relative to the fixed ring 1 Servo motor, not shown, which acts on the rotary ring 2 via a link lever 10. For this purpose, there is a link fork 11 with fork tines at the end of the link lever 10 11a, 11b, in which inwardly pointing bolts 12 are fastened, which are in the area the parting line 16 engage in corresponding bores in the rotating ring 2. With the in so far described arrangement would be a traction from the servo motor Pull the lower ring part 2b away from the upper ring part 2a while under pressure would reverse the circumstances. In both cases, however, the inner diameter would change of the rotating ring 2 or the gap in the parting line 16.

Eine Vergrößerung des Innendurchmessers soll jedoch nur dann stattfinden, wenn die Gleitreibung einen vorgegebenen Grenzwert überschreitet, um dann diesen Wert auf einen angemessenen Betrag zu vermindern. Hierzu ist eine entsprechend dimensionierte Druckfeder 15 vorgesehen, die vom Kopf einer Bundschraube 14 erfaßt und gegen einen Kragen 19 des Drehringoberteils 2a gepreßt wird. Da die Bundschraube 14 in eine Gewindebuchse 13 des Drehringunterteils 2b eingeschraubt ist, werden Drehringoberteil 2a und Drehringunterteil 2b von der Druckfeder 15 mit der ihr eigenen Federkraft zusammengehalten. Nur wenn zwischen Drehring 2 und Festring 1 eine Friktion auftritt, die diese Federkraft überschreitet, vergrößert sich bei Betätigung des Anlenkhebels 10 der Spalt im Bereich der Teilfuge 16 soweit, daß die Gleitreibung sinkt und eine Drehbewegung möglich wird.An increase in the inner diameter should only take place if the Dynamic friction exceeds a predetermined limit, then this value to decrease an appropriate amount. For this, an appropriately dimensioned Compression spring 15 is provided, which is gripped by the head of a collar screw 14 and against a collar 19 of the rotating ring upper part 2a is pressed. Since the collar screw 14 in a threaded bush 13 of the rotating ring lower part 2b is screwed in, the rotating ring upper part 2a and lower ring part 2b of the compression spring 15 with its own spring force held together. Only if there is friction between the rotating ring 2 and the fixed ring 1 occurs that exceeds this spring force increases when the link lever is actuated 10 the gap in the area of the parting line 16 so far that the sliding friction drops and a rotary movement becomes possible.

Claims (3)

  1. Radial rotary slide valve for controlling the steam throughput in a steam turbine, comprising an immovable fixed ring (1) and a rotary ring (2) arranged concentrically thereon and movable in a rotary manner, the angular position of the rotary ring (2) being changeable by means of a servomotor and the rotary ring (2) comprising first control profiles (4a) corresponding to equivalent second control profiles (4b) of the fixed ring (1) in such a way that control slots (17) located between the control profiles (4) can be changed for the purpose of opening or closing, the rotary ring (2) being divided in the region of the partial joint (16) into a rotary ring upper part (2a) and a rotary ring lower part (2b), characterised in that the rotary ring upper part (2a) and rotary ring lower part (2b) are connected to one another by suitable connecting means (8, 9; 11 to 15) in such a way that the spacing between two opposing half-ring ends can be changed and a change in the internal diameter of the rotary ring thus allowed, in that the two opposing ends of the two rotary ring halves (2a, 2b) are held together by a hinge (8, 9) and in that a collar screw (14) engages at the two other opposing ends of the two rotary ring halves (2a, 2b) not connected by the hinge (8), the collar screw (14) being screwed into a threaded bush (13) of the one rotary ring half (2b) and grasping with its head a compression spring (15) supported on a collar of the other rotary ring half (2a), in that a link lever (10) producing the connection to the servomotor ends at a link fork (11), to each of the fork prongs (11a, 11b) of which an inwardly directed bolt (12) is fastened and in that these two bolts (12) engage, centrally to the partial joint (16), in a hole which is recessed, half in the rotary ring upper part (2a) and half in the rotary ring lower part (2b), respectively.
  2. Radial rotary slide valve according to claim 1, characterised in that the control profiles (4) consist of the profile heads (4a) associated with the rotary ring (2) and the profile ends (4b) associated with the fixed ring (1) and these open and close the control slots (17) belonging to a steam conduit (5) owing to their position with respect to one another.
  3. Radial rotary slide valve according to claim 1, characterised in that the connecting means (8, 9; 11 to 15) can be adjusted by appropriate tools, preferably by actuating screw elements.
EP97108100A 1996-05-24 1997-05-20 Rotary slide valve for the control of steam flow to a steam turbine Expired - Lifetime EP0808992B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19620949A DE19620949A1 (en) 1996-05-24 1996-05-24 Radial rotary valve to control the steam throughput in a steam turbine
DE19620949 1996-05-24

Publications (3)

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EP0808992A2 EP0808992A2 (en) 1997-11-26
EP0808992A3 EP0808992A3 (en) 1999-07-07
EP0808992B1 true EP0808992B1 (en) 2003-03-26

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EP97108100A Expired - Lifetime EP0808992B1 (en) 1996-05-24 1997-05-20 Rotary slide valve for the control of steam flow to a steam turbine

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US (1) US5799927A (en)
EP (1) EP0808992B1 (en)
JP (1) JPH1082470A (en)
DE (2) DE19620949A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU6176300A (en) * 2000-05-23 2001-12-03 Heru Prasanta Wijaya Diaphragmed air valve system
US7097421B2 (en) * 2004-10-08 2006-08-29 United Technologies Corporation Vernier duct blocker
PL2014876T3 (en) 2007-07-10 2012-11-30 Siemens Ag Rotary slide valve for the control of steam flow to a steam turbine
IT1401665B1 (en) * 2010-08-31 2013-08-02 Nuova Pignone S R L DRIVING SYSTEM FOR TURBOMACHINE AND METHOD.
GB201308680D0 (en) * 2013-05-14 2013-06-26 Imp Innovations Ltd A flow control device for a turbocharger
US9803557B2 (en) * 2015-01-20 2017-10-31 United Technologies Corporation Gas turbine engine and blocker door assembly
US10030544B2 (en) * 2015-10-06 2018-07-24 Nuovo Pignone S.R.L. Extracting steam from a turbine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3127909A (en) * 1962-07-18 1964-04-07 Honeywell Regulator Co Rotary gate valve

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2666618A (en) * 1949-07-29 1954-01-19 Bendix Aviat Corp Rotary throttle blade design
DD44684A3 (en) * 1962-12-22 1966-03-25
US3860357A (en) * 1973-10-01 1975-01-14 Lewis M D Grainger Rotary steam engine
DD202745A1 (en) * 1981-07-08 1983-09-28 Karl Speicher CONTROL DEVICE FOR A STEAM OR GAS STREAM OF A TURBO MACHINE
DE8609300U1 (en) * 1986-04-05 1986-05-22 Viesel, Manfred, 7432 Bad Urach Clamping device for screw jackets
US4884944A (en) * 1988-09-07 1989-12-05 Avco Corporation Compressor flow fence
DE4214775A1 (en) * 1992-05-04 1993-11-11 Abb Patent Gmbh Steam turbine with a rotary valve
KR950006278Y1 (en) * 1993-01-25 1995-08-05 이성환 Ventilating appartus of airconditioner
DE4425344C2 (en) * 1994-07-18 2001-05-23 Abb Patent Gmbh Rotary vane with at least one axial needle slewing ring as a rotatable bearing element

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3127909A (en) * 1962-07-18 1964-04-07 Honeywell Regulator Co Rotary gate valve

Also Published As

Publication number Publication date
EP0808992A2 (en) 1997-11-26
EP0808992A3 (en) 1999-07-07
JPH1082470A (en) 1998-03-31
US5799927A (en) 1998-09-01
DE19620949A1 (en) 1997-11-27
DE59709597D1 (en) 2003-04-30

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