EP2162597A1 - Rotary valve for the control of steam throughput in a steam turbine - Google Patents
Rotary valve for the control of steam throughput in a steam turbineInfo
- Publication number
- EP2162597A1 EP2162597A1 EP08774901A EP08774901A EP2162597A1 EP 2162597 A1 EP2162597 A1 EP 2162597A1 EP 08774901 A EP08774901 A EP 08774901A EP 08774901 A EP08774901 A EP 08774901A EP 2162597 A1 EP2162597 A1 EP 2162597A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control
- rotary valve
- fixed ring
- ring
- rotary
- 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.)
- Withdrawn
Links
- 238000010276 construction Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/18—Final actuators arranged in stator parts varying effective number of nozzles or guide conduits, e.g. sequentially operable valves for steam turbines
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/30—Application in turbines
- F05D2220/31—Application in turbines in steam turbines
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86718—Dividing into parallel flow paths with recombining
- Y10T137/86743—Rotary
Definitions
- the invention relates to a rotary valve for controlling the steam flow rate in a steam turbine having the features of the preamble of claim 1.
- Control slots more or less open or close.
- Such rotary valves are relatively simple in construction compared to the valves normally used in steam turbine construction for the control of steam extraction and also have some other advantages.
- a generic rotary valve for a steam turbine is known from DE 19 620 949 Al.
- the well-known rotary valve achieved only at full opening the best efficiency for the steam turbine, since in this position the
- Control slots are flowed through optimally. If the rotary valve is moved in the closing direction by the profile heads are pushed in the rotary ring in front of the control slots in the fixed ring, it comes in the partially closed state of the rotary valve at the edges of the profile heads and the
- the invention has for its object to make the generic rotary valve so that the efficiency of the steam turbine is improved in the partial load range.
- the object is achieved in a generic rotary valve according to the invention by the characterizing features of claim 1.
- Advantageous embodiments of the invention are the subject of the dependent claims.
- the profile heads of the rotary ring can share or cover both partial slots of the control slot.
- the profile heads of the rotary ring at half the opening of the rotary valve in each case close one of the sub-slots, while the other sub-slot is open.
- Half of the partial slots is therefore open and can be flowed through optimally and undisturbed. In this way, a high efficiency is achieved even at half load and the reduction in efficiency at the other part loads less influenced.
- Fig. 1 shows the cross section through a steam turbine with a
- FIG. 2 shows the longitudinal section through a portion of a
- FIG. 3 to 5 show the partial development of the rotary valve, in the open position of the rotary valve (FIG. 3), in the closed position of the rotary valve (FIG. 4) and in the half-open position of the rotary valve (FIG. 5).
- the steam turbine includes a turbine housing 1, in which a turbine rotor 2 rotates.
- the turbine rotor 2 is equipped with blades 3.
- Between the blades 3 are fixed vanes 4, which are suspended on a guide blade carrier 5 connected to the turbine housing 1.
- a rotary valve 6 designed as an axial rotary valve is arranged to control the steam flow rate through the steam turbine (FIG. 2).
- Rotary valve can also be applied to a radial rotary valve with a corresponding arrangement within the steam turbine, as shown in Fig. 1.
- the rotary valve 6 has a fixed ring 7 and a rotary ring 8.
- the fixed ring 7 is fixedly connected to the guide vane 5.
- the rotary ring 8 is arranged concentrically on the fixed ring 7 rotatably.
- Radial rotary ring serving servo motor 9 engages via a Anlenkspindel 10 and an articulation lever 11 to the rotary ring 8. About the stroke of the servo motor 9, a rotation of the rotary ring 8 is effected.
- the rotary valve 6 is provided with control profiles 12, between which control slots 13 are formed.
- the control slots 13 are coaxial with the flow channel of the steam turbine and are shown in FIG. 3 as fully open.
- the control profiles 12 are cut and each have a profile head 12.1 and a profile end 12.2.
- the profile heads 12.1 are in the rotary ring 8 and the profile ends 12.2 are arranged in the fixed ring 7.
- the profile heads 12. 1 and the profile ends 12. 2 lie positively against one another and, due to their aerodynamically optimized shape, form only a relatively small resistance to the steam flowing in the direction of the arrow towards the rotor blades 3 of the turbine rotor 2.
- the control profiles 12 and the control slots 13 are coordinated so that in the plane of contact between the rotary ring 8 and 7 fixed ring the width of the control profiles 12th is equal to the width of the control slots 13.
- aerodynamically shaped blades 14 are arranged between the profile ends 12.2 of the control profiles 12 within the fixed ring 7 aerodynamically shaped blades 14 are arranged.
- the blades 14 divide the control slots 13 between each two profile ends 12.2 in two partial slots 13.1, 13.2.
- the blades 14 are preferably arranged centrally within the control slot 13, so that in each case two equal-width partial slots 13.1, 13.2 are formed.
- the blades 14 can also be arranged outside the center of the control slot 13, if the desired partial load point is not 50%.
- Partial slots 13.1, 13.2 is clear from Fig. 5 in conjunction with Figs. 3 and 4.
- the rotary ring 8 is rotated so far relative to the fixed ring 7 that the profile heads 12. 1 lie in a form-fitting manner on the profile ends 12. 2 and the control profiles 12 are released.
- Control slots 13 can be flowed through optimally and undisturbed by the steam.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Turbines (AREA)
Abstract
Description
Beschreibungdescription
Drehschieber zur Steuerung des Dampfdurchsatzes bei einer DampfturbineRotary valve for controlling the steam flow rate in a steam turbine
Die Erfindung betrifft einen Drehschieber zur Steuerung des Dampfdurchsatzes bei einer Dampfturbine mit den Merkmalen des Oberbegriffes des Patentanspruches 1.The invention relates to a rotary valve for controlling the steam flow rate in a steam turbine having the features of the preamble of claim 1.
Als Axial- oder Radialdrehschieber ausgebildete Drehschieber dienen zur Steuerung des Dampfdurchsatzes bei einer Dampfturbine. Mit dem unbeweglichen Festring und dem konzentrisch auf diesem drehbeweglich angeordneten Drehring, dessen Winkelstellung durch einen Servomotor veränderbar ist, gelingt es, die in den beiden Ringen vorgesehenenAs axial or radial rotary valve trained rotary valves are used to control the steam flow rate in a steam turbine. With the immovable fixed ring and concentric on this rotatably mounted rotary ring whose angular position is changed by a servo motor, it is possible, provided in the two rings
Steuerschlitze mehr oder weniger zu öffnen oder zu schließen. Derartige Drehschieber sind im Vergleich zu den sonst im Dampfturbinenbau zur Steuerung von Dampfentnahmen verwendeten Ventilen relativ einfach aufgebaut und weisen auch noch einige andere Vorzüge auf.Control slots more or less open or close. Such rotary valves are relatively simple in construction compared to the valves normally used in steam turbine construction for the control of steam extraction and also have some other advantages.
Ein gattungsgemäßer Drehschieber für eine Dampfturbine ist aus der DE 19 620 949 Al bekannt. Der bekannte Drehschieber erzielt lediglich bei voller Öffnung den besten Wirkungsgrad für die Dampfturbine, da in dieser Stellung dieA generic rotary valve for a steam turbine is known from DE 19 620 949 Al. The well-known rotary valve achieved only at full opening the best efficiency for the steam turbine, since in this position the
Steuerschlitze optimal durchströmt sind. Wird der Drehschieber in Schließrichtung bewegt, indem die Profilköpfe im Drehring vor die Steuerschlitze im Festring geschoben werden, kommt es im teilweise geschlossenen Zustand des Drehschiebers an den Kanten der Profilköpfe und derControl slots are flowed through optimally. If the rotary valve is moved in the closing direction by the profile heads are pushed in the rotary ring in front of the control slots in the fixed ring, it comes in the partially closed state of the rotary valve at the edges of the profile heads and the
Profilenden zu starken Verwirbelungen . Aufgrund solcher Verwirbelungen ist der Wirkungsgrad der Dampfturbine bei Teillast deutlich schlechter.Profile ends to strong turbulence. Due to such turbulence, the efficiency of the steam turbine at part load is significantly worse.
Der Erfindung liegt die Aufgabe zugrunde, den gattungsgemäßen Drehschieber so zu gestalten, dass der Wirkungsgrad der Dampfturbine im Teillastbereich verbessert wird. Die Aufgabe wird bei einem gattungsgemäßen Drehschieber erfindungsgemäß durch die kennzeichnenden Merkmale des Patentanspruches 1 gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand der Unteransprüche.The invention has for its object to make the generic rotary valve so that the efficiency of the steam turbine is improved in the partial load range. The object is achieved in a generic rotary valve according to the invention by the characterizing features of claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.
Bei dem erfindungsgemäßen Drehschieber können die Profilköpfe des Drehringes beide Teilschlitze des Steuerschlitzes freigeben oder überdecken. Zusätzlich ist es möglich, dass die Profilköpfe des Drehringes bei halber Öffnung des Drehschiebers jeweils einen der Teilschlitze verschließen, während der andere Teilschlitz geöffnet ist. Die Hälfte der Teilschlitze ist daher geöffnet und kann optimal und ungestört durchströmt werden. Auf diese Weise wird auch bei Halblast ein hoher Wirkungsgrad erreicht und die Verringerung des Wirkungsgrades bei den sonstigen Teillasten weniger stark beeinflusst .In the rotary valve according to the invention, the profile heads of the rotary ring can share or cover both partial slots of the control slot. In addition, it is possible that the profile heads of the rotary ring at half the opening of the rotary valve in each case close one of the sub-slots, while the other sub-slot is open. Half of the partial slots is therefore open and can be flowed through optimally and undisturbed. In this way, a high efficiency is achieved even at half load and the reduction in efficiency at the other part loads less influenced.
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird im Folgenden näher erläutert. Es zeigen:An embodiment of the invention is illustrated in the drawing and will be explained in more detail below. Show it:
Fig. 1 den Querschnitt durch eine Dampfturbine mit einemFig. 1 shows the cross section through a steam turbine with a
Radialdrehschieber, Fig. 2 den Längsschnitt durch einen Teilbereich einerRadial rotary valve, Fig. 2 shows the longitudinal section through a portion of a
Dampfturbine mit einem Axialdrehschieber und Fig. 3 bis 5 die teilweise Abwicklung des Drehschiebers, und zwar in Offenstellung des Drehschiebers (Fig. 3), in Geschlossenstellung des Drehschiebers (Fig. 4) und in Halboffenstellung des Drehschiebers (Fig. 5).3 to 5 show the partial development of the rotary valve, in the open position of the rotary valve (FIG. 3), in the closed position of the rotary valve (FIG. 4) and in the half-open position of the rotary valve (FIG. 5).
Von einer mehrstufigen Dampfturbine ist in der Fig. 2 nur der Mitteldruckteil gezeigt. Die Dampfturbine enthält ein Turbinengehäuse 1, in dem ein Turbinenrotor 2 umläuft. Der Turbinenrotor 2 ist mit Laufschaufeln 3 bestückt. Zwischen den Laufschaufeln 3 befinden sich feststehende Leitschaufeln 4, die an einem mit dem Turbinengehäuse 1 verbundenen Leitschaufelträger 5 aufgehängt sind. Vor dem durch die Laufschaufeln 3 und die Leitschaufeln 4 gebildeten Strömungskanal der Dampfturbine ist ein als Axialdrehschieber ausgebildeter Drehschieber 6 zur Steuerung des Dampfdurchsatzes durch die Dampfturbine angeordnet (Fig. 2) . Die Gestaltung des nachfolgend beschriebenenOf a multi-stage steam turbine in Fig. 2, only the medium-pressure part is shown. The steam turbine includes a turbine housing 1, in which a turbine rotor 2 rotates. The turbine rotor 2 is equipped with blades 3. Between the blades 3 are fixed vanes 4, which are suspended on a guide blade carrier 5 connected to the turbine housing 1. In front of the flow channel of the steam turbine formed by the rotor blades 3 and the guide vanes 4, a rotary valve 6 designed as an axial rotary valve is arranged to control the steam flow rate through the steam turbine (FIG. 2). The design of the below described
Drehschiebers kann bei entsprechender Anordnung innerhalb der Dampfturbine auch auf einen Radialdrehschieber angewendet werden, wie er in Fig. 1 dargestellt ist.Rotary valve can also be applied to a radial rotary valve with a corresponding arrangement within the steam turbine, as shown in Fig. 1.
Der Drehschieber 6 weist einen Festring 7 und einen Drehring 8 auf. Der Festring 7 ist mit dem Leitschaufelträger 5 fest verbunden. Der Drehring 8 ist konzentrisch auf dem Festring 7 drehbeweglich angeordnet. Zum drehbeweglichen Verstellen des Drehringes 8 gegenüber dem Festring 7 dient ein Servomotor 9. Der zum Verstellen des in Fig. 1 dargestelltenThe rotary valve 6 has a fixed ring 7 and a rotary ring 8. The fixed ring 7 is fixedly connected to the guide vane 5. The rotary ring 8 is arranged concentrically on the fixed ring 7 rotatably. For rotatably adjusting the rotary ring 8 relative to the fixed ring 7 is a servomotor 9. Der zur Verstellen des in Fig. 1 dargestellt. Illustrated
Radialdrehringes dienende Servomotor 9 greift über eine Anlenkspindel 10 und einen Anlenkhebel 11 an dem Drehring 8 an. Über den Hub des Servomotors 9 wird ein Verdrehen des Drehringes 8 bewirkt.Radial rotary ring serving servo motor 9 engages via a Anlenkspindel 10 and an articulation lever 11 to the rotary ring 8. About the stroke of the servo motor 9, a rotation of the rotary ring 8 is effected.
Der Drehschieber 6 ist mit Steuerprofilen 12 versehen, zwischen denen Steuerschlitze 13 gebildet sind. Im Falle des Axialdrehschiebers liegen die Steuerschlitze 13 koaxial zu dem Strömungskanal der Dampfturbine und sind in der Fig. 3 als voll geöffnet gezeigt. Die Steuerprofile 12 sind geschnitten und weisen jeweils einen Profilkopf 12.1 und ein Profilende 12.2 auf. Die Profilköpfe 12.1 sind in dem Drehring 8 und die Profilenden 12.2 sind in dem Festring 7 angeordnet. Im voll geöffneten Zustand des Drehschiebers 6 (Fig. 3) liegen die Profilköpfe 12.1 und die Profilenden 12.2 formschlüssig aufeinander und bilden durch ihre aerodynamisch optimierte Form nur einen relativ geringen Widerstand für den in Pfeilrichtung den Laufschaufeln 3 des Turbinenrotors 2 zuströmenden Dampf.The rotary valve 6 is provided with control profiles 12, between which control slots 13 are formed. In the case of the Axialdrehschiebers the control slots 13 are coaxial with the flow channel of the steam turbine and are shown in FIG. 3 as fully open. The control profiles 12 are cut and each have a profile head 12.1 and a profile end 12.2. The profile heads 12.1 are in the rotary ring 8 and the profile ends 12.2 are arranged in the fixed ring 7. In the fully opened state of the rotary valve 6 (FIG. 3), the profile heads 12. 1 and the profile ends 12. 2 lie positively against one another and, due to their aerodynamically optimized shape, form only a relatively small resistance to the steam flowing in the direction of the arrow towards the rotor blades 3 of the turbine rotor 2.
Die Steuerprofile 12 und die Steuerschlitze 13 sind so aufeinander abgestimmt, dass in der Berührungsebene zwischen Drehring 8 und Festring 7 die Breite der Steuerprofile 12 gleich der Breite der Steuerschlitze 13 ist. Zwischen den Profilenden 12.2 der Steuerprofile 12 innerhalb des Festringes 7 sind aerodynamisch geformte Schaufeln 14 angeordnet. Die Schaufeln 14 teilen die Steuerschlitze 13 zwischen jeweils zwei Profilenden 12.2 in zwei Teilschlitze 13.1, 13.2. Die Schaufeln 14 sind vorzugsweise mittig innerhalb des Steuerschlitzes 13 angeordnet, so dass jeweils zwei gleich breite Teilschlitze 13.1, 13.2 gebildet sind.The control profiles 12 and the control slots 13 are coordinated so that in the plane of contact between the rotary ring 8 and 7 fixed ring the width of the control profiles 12th is equal to the width of the control slots 13. Between the profile ends 12.2 of the control profiles 12 within the fixed ring 7 aerodynamically shaped blades 14 are arranged. The blades 14 divide the control slots 13 between each two profile ends 12.2 in two partial slots 13.1, 13.2. The blades 14 are preferably arranged centrally within the control slot 13, so that in each case two equal-width partial slots 13.1, 13.2 are formed.
Eine solche Anordnung wird gewählt, wenn der Teillastpunkt bei 50% der Volllast liegt. Die Schaufeln 14 können auch außerhalb der Mitte des Steuerschlitzes 13 angeordnet werden, wenn der gewünschte Teillastpunkt nicht auf 50% liegt.Such an arrangement is chosen when the partial load point is 50% of full load. The blades 14 can also be arranged outside the center of the control slot 13, if the desired partial load point is not 50%.
Die Bedeutung der durch die Schaufeln 14 gebildetenThe meaning of the formed by the blades 14
Teilschlitze 13.1, 13.2 wird aus der Fig. 5 in Verbindung mit den Fig. 3 und 4 deutlich. In der Fig. 3 ist der Drehring 8 gegenüber dem Festring 7 so weit verdreht, dass die Profilköpfe 12.1 formschlüssig auf den Profilenden 12.2 liegen und die Steuerprofile 12 freigegeben sind. DiePartial slots 13.1, 13.2 is clear from Fig. 5 in conjunction with Figs. 3 and 4. In FIG. 3, the rotary ring 8 is rotated so far relative to the fixed ring 7 that the profile heads 12. 1 lie in a form-fitting manner on the profile ends 12. 2 and the control profiles 12 are released. The
Steuerschlitze 13 können optimal und ungestört von dem Dampf durchströmt werden.Control slots 13 can be flowed through optimally and undisturbed by the steam.
Durch ein Verdrehen des Drehringes 8 gegenüber dem Festring 7 kann erreicht werden, dass die Profilköpfe 12.1 formschlüssig an den Kanten der Profilenden 12.2 anliegen und die Steuerschlitze 13 mit den Teilschlitzen 13.1, 13.2 vollständig überdecken und ein Durchtritt von Dampf gesperrt ist (Fig. 4) .By rotating the rotary ring 8 with respect to the fixed ring 7, it can be achieved that the profile heads 12.1 rest positively on the edges of the profile ends 12.2 and completely cover the control slots 13 with the partial slots 13.1, 13.2 and a passage of steam is blocked (FIG. 4). ,
Bei Halblast ist gemäß Fig. 5 der Drehring 8 gegenüber dem Festring 7 so weit verdreht, dass jeder Profilkopf 12.1 teilweise formschlüssig an den Profilenden 12.2 anliegt und gerade einen Teilschlitz 13.1 überdeckt und den anderen Teilschlitz 13.2 freigibt. In einer solchen Stellung ist der geöffnete Teilschlitz 13.2 wiederum optimal und ungestört von Dampf durchströmt. At half load, as shown in FIG. 5, the rotary ring 8 is rotated so far relative to the fixed ring 7 that each profile head 12.1 bears partly positively against the profile ends 12.2 and just covers a partial slot 13.1 and releases the other partial slot 13.2. In such a position, the opened sub-slot 13.2 is again flowed through optimally and undisturbed by steam.
Claims
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP08774901A EP2162597A1 (en) | 2007-07-10 | 2008-07-09 | Rotary valve for the control of steam throughput in a steam turbine |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP20070013509 EP2014876B1 (en) | 2007-07-10 | 2007-07-10 | Rotary slide valve for the control of steam flow to a steam turbine |
| EP08774901A EP2162597A1 (en) | 2007-07-10 | 2008-07-09 | Rotary valve for the control of steam throughput in a steam turbine |
| PCT/EP2008/058883 WO2009007383A1 (en) | 2007-07-10 | 2008-07-09 | Rotary valve for the control of steam throughput in a steam turbine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| EP2162597A1 true EP2162597A1 (en) | 2010-03-17 |
Family
ID=38951455
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP20070013509 Not-in-force EP2014876B1 (en) | 2007-07-10 | 2007-07-10 | Rotary slide valve for the control of steam flow to a steam turbine |
| EP08774901A Withdrawn EP2162597A1 (en) | 2007-07-10 | 2008-07-09 | Rotary valve for the control of steam throughput in a steam turbine |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP20070013509 Not-in-force EP2014876B1 (en) | 2007-07-10 | 2007-07-10 | Rotary slide valve for the control of steam flow to a steam turbine |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US8408248B2 (en) |
| EP (2) | EP2014876B1 (en) |
| BR (1) | BRPI0814044A2 (en) |
| ES (1) | ES2388747T3 (en) |
| PL (1) | PL2014876T3 (en) |
| WO (1) | WO2009007383A1 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010042412A1 (en) * | 2010-10-13 | 2012-04-19 | Robert Bosch Gmbh | steam turbine |
| CN102352782A (en) * | 2011-11-02 | 2012-02-15 | 哈尔滨汽轮机厂有限责任公司 | Rotating barrier for extraction steam turbine with 300MW power |
| US9011082B2 (en) * | 2011-12-22 | 2015-04-21 | United Technologies Corporation | Gas turbine engine duct blocker with rotatable vane segments |
| US20140105720A1 (en) * | 2012-10-11 | 2014-04-17 | Krishna Kumar Bindingnavale Ranga | Method and a system for adjusting nozzle area in steam turbines |
| DE102014201502A1 (en) * | 2014-01-28 | 2015-07-30 | Siemens Aktiengesellschaft | steam turbine |
| DE102014225608A1 (en) | 2014-12-11 | 2016-06-16 | Siemens Aktiengesellschaft | Apparatus and method for controlling a steam mass flow in a steam turbine |
| US9803557B2 (en) | 2015-01-20 | 2017-10-31 | United Technologies Corporation | Gas turbine engine and blocker door assembly |
| KR101625794B1 (en) * | 2015-04-06 | 2016-05-30 | 두산중공업 주식회사 | Nozzle box for turbine |
| US10030544B2 (en) * | 2015-10-06 | 2018-07-24 | Nuovo Pignone S.R.L. | Extracting steam from a turbine |
| CN111350557B (en) * | 2020-03-26 | 2025-03-07 | 中国船舶重工集团公司第七0三研究所 | A rotating diaphragm for a double extraction steam turbine unit |
| CZ310425B6 (en) * | 2023-12-13 | 2025-06-04 | Doosan Škoda Power a.s | Steam turbine control baffle |
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| SE75786C1 (en) | ||||
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| US707727A (en) * | 1901-05-10 | 1902-08-26 | Richard Schulz | Steam-turbine. |
| FR362019A (en) | 1905-12-22 | 1907-02-09 | Desire Bonnet Marie-Julie-Leonie Ier | Distributor with movable blades for turbines |
| US867611A (en) * | 1906-03-06 | 1907-10-08 | Richard Schulz | Steam-turbine. |
| GB191301187A (en) | 1912-03-19 | 1913-06-19 | George Westinghouse | Improvements in and relating to Fluid Pressure Turbines. |
| US2666618A (en) * | 1949-07-29 | 1954-01-19 | Bendix Aviat Corp | Rotary throttle blade design |
| SU802562A1 (en) | 1979-03-30 | 1981-02-07 | Харьковский Филиал Центральногоконструкторского Бюро Главэнерго-Pemohta Министерства Энергети-Ческой Промышленности Cccp | Adjustable nozzle unit of steam turbine |
| US4526199A (en) * | 1983-11-14 | 1985-07-02 | Northern Research & Engineering Corp. | Valve for throttling fluid |
| US5157779A (en) * | 1990-06-07 | 1992-10-20 | Sun Microsystems, Inc. | User extensible testing system |
| DE4214775A1 (en) * | 1992-05-04 | 1993-11-11 | Abb Patent Gmbh | Steam turbine with a rotary valve |
| DE4238550A1 (en) | 1992-11-14 | 1994-05-19 | Daimler Benz Ag | Exhaust gas turbocharger for an internal combustion engine |
| NO177874C (en) | 1993-07-14 | 1996-10-30 | Sinvent As | Device for mixing the components in a fluid flow, and using the device in a mass flow meter |
| DE19620949A1 (en) | 1996-05-24 | 1997-11-27 | Abb Patent Gmbh | Radial rotary valve to control the steam throughput in a steam turbine |
| US7097421B2 (en) * | 2004-10-08 | 2006-08-29 | United Technologies Corporation | Vernier duct blocker |
| GB0608404D0 (en) * | 2006-04-28 | 2006-06-07 | Ibm | Method and system for recording interactions of distributed users |
-
2007
- 2007-07-10 PL PL07013509T patent/PL2014876T3/en unknown
- 2007-07-10 EP EP20070013509 patent/EP2014876B1/en not_active Not-in-force
- 2007-07-10 ES ES07013509T patent/ES2388747T3/en active Active
-
2008
- 2008-07-09 WO PCT/EP2008/058883 patent/WO2009007383A1/en not_active Ceased
- 2008-07-09 US US12/668,072 patent/US8408248B2/en not_active Expired - Fee Related
- 2008-07-09 BR BRPI0814044 patent/BRPI0814044A2/en not_active IP Right Cessation
- 2008-07-09 EP EP08774901A patent/EP2162597A1/en not_active Withdrawn
Non-Patent Citations (1)
| Title |
|---|
| See references of WO2009007383A1 * |
Also Published As
| Publication number | Publication date |
|---|---|
| US8408248B2 (en) | 2013-04-02 |
| BRPI0814044A2 (en) | 2015-02-10 |
| WO2009007383A1 (en) | 2009-01-15 |
| ES2388747T3 (en) | 2012-10-18 |
| US20100189550A1 (en) | 2010-07-29 |
| EP2014876A1 (en) | 2009-01-14 |
| PL2014876T3 (en) | 2012-11-30 |
| EP2014876B1 (en) | 2012-06-06 |
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