EP1632650B1 - Steam turbine - Google Patents

Steam turbine Download PDF

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Publication number
EP1632650B1
EP1632650B1 EP04020807.6A EP04020807A EP1632650B1 EP 1632650 B1 EP1632650 B1 EP 1632650B1 EP 04020807 A EP04020807 A EP 04020807A EP 1632650 B1 EP1632650 B1 EP 1632650B1
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EP
European Patent Office
Prior art keywords
steam turbine
steam
control wheel
wheel
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP04020807.6A
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German (de)
French (fr)
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EP1632650A1 (en
Inventor
Olaf Arndt
Udo Tielcke
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Siemens AG
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Siemens AG
Siemens Corp
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Application filed by Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to PL04020807T priority Critical patent/PL1632650T3/en
Priority to EP04020807.6A priority patent/EP1632650B1/en
Priority to ES04020807T priority patent/ES2411657T3/en
Priority to PCT/EP2005/053972 priority patent/WO2006024597A1/en
Priority to CNB2005800293887A priority patent/CN100462525C/en
Priority to BRPI0514816A priority patent/BRPI0514816B8/en
Priority to EP05775974A priority patent/EP1784558A1/en
Publication of EP1632650A1 publication Critical patent/EP1632650A1/en
Publication of EP1632650B1 publication Critical patent/EP1632650B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/18—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbine being of multiple-inlet-pressure type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/18—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbine being of multiple-inlet-pressure type
    • F01K7/20—Control means specially adapted therefor

Definitions

  • the invention relates to a steam turbine having a plurality of stage parts and with a arranged before the first stage part device for power control of the steam turbine.
  • a steam turbine is eg in document US Pat. No. 6,308,407 B1 disclosed.
  • the invention has for its object to provide a steam turbine, which is operable with good efficiencies both in normal operation and in the partial load range with benefits that are well below the rated power.
  • the steam turbine according to the invention should also have a good efficiency in operation with overload.
  • the optimization of the process is influenced by a problem-free mixing of the reintegrated steam after the MD control wheel. It can be seen that at high live steam conditions (HD steam), the quadruple mass flow can be processed in overload operation without significant losses in efficiency in normal and part-load operations.
  • high live steam conditions HD steam
  • the inventive arrangement of a second control wheel with the associated controllable nozzles in a chamber between the first stage part of the steam turbine part and the second stage part of the steam turbine can be successfully used both in drum turbines and in chamber turbines.
  • the invention can be used equally successfully in turbines with constant pressure blading and in turbines with positive pressure blading in the multiple stages of the steam turbine.
  • the HP ratchet wheel and the MD ratchet wheel can be both single-stringed and two-stringed (Curtis wheel).
  • the design of the turbine with HP control wheel and subsequent step part is often optimal. However, this construction is not essential to the invention.
  • the HP control wheel can also be replaced as a step section with an optional inner housing and a throttle control in bypass / internal bypass operation or as a combination of both, HD control wheel and bypass operation in the inner housing.
  • the basic principle therefore does not change, because the MD impeller with nozzle can also be put into operation as required via the pressure gradient between the HD entry state and the selected, optimized MD state if required.
  • the principle of the MD pulse wheel with nozzles can also be carried out as a retrofit or conversion in an existing turbine.
  • This additional HD steam is done via conventional nozzle controls, so that the impulse wheel adds additional power through the nozzles in sliding pressure mode like a free control wheel.
  • the additional power results from the enthalpy difference between the HD vapor state and the local steam state after the MD control wheel and the amount of steam to be optimized.
  • the FIG. 1 shows a steam turbine with a housing 3 and a rotor 5 in longitudinal section.
  • the steam turbine 1 has a first step part 7 and a second step part 9.
  • Each of the stages 7 and 9 consists of a group of blades 11 which are fixed to the rotor 5 and a group of vanes 13, which are usually attached via guide vanes to the housing 3 of the steam turbine 1.
  • a first control wheel 15 is attached to the rotor 5.
  • blades of the control wheel 15 are designed as equal pressure blades.
  • a nozzle ring 17 In the immediate vicinity of the first control wheel 15, a nozzle ring 17 is provided, which has a plurality of nozzles 19 distributed over the circumference.
  • the nozzle ring 17 is acted upon by a live steam line 21 with the partial lines 21a and 21b with steam.
  • a first control valve 23 is provided in each case. Via the controllable nozzles 19 of the nozzle ring 17 supplied live steam is passed to the first control wheel 15 and then passes into a first wheel space 25, which is bounded by the rotor 5 and the housing 3.
  • a second MD control wheel 27 is provided on the rotor 5.
  • the MD control wheel 27 is also formed in the embodiment shown here as a pulse wheel.
  • the second MD control wheel 27 is of one or more nozzles 29, of which in FIG. 1 only one is shown, acted upon by additional steam and thus acts as a Regelradform in Gleit horrin.
  • This additional steam which in FIG. 1 is indicated by an arrow 31, mixed before entering the second stage part 9 with the partially relaxed live steam, which has leaked out of the first stage part 7.
  • This partially relaxed live steam is in FIG. 1 has been provided with the reference numeral 33.
  • the existing between the first stage part 7 and second stage part 9 space in which the second MD control wheel 27 is located, is referred to below as the second wheel chamber 35.
  • the nozzle 29 is also controllable and can be optimized, for example via a second control valve 37 or a valve group, not shown. About this second control valve 37, the supply of additional steam can be controlled in the steam turbine 1 through the nozzle 29.
  • the second control valve 37 or the valve group In normal operation, that is, when the steam turbine is operated at its rated power or in the partial load range, the second control valve 37 or the valve group is closed and the steam turbine 1 operates like a conventional steam turbine.
  • the power control of the steam turbine 1 takes place exclusively via the first control wheel 15 or the control of the nozzles 19, which control the application of the first control wheel 15.
  • the power control of the steam turbine 1 in nominal or normal operation and in partial load operation is well known from the prior art and will therefore not be explained in detail in connection with the invention.
  • An advantage of this power control is the consistently good efficiency of the steam turbine 1 at rated load as well as in Part load operation without significant additional construction costs such.
  • As inner casing turbines with Mitteneinströmung or the like.
  • the second control valve 37 or the valve group, not shown, is opened according to the invention, so that additional steam can flow via the nozzle 29 to the second control wheel 27.
  • the nozzle 29 is designed and optimized so that the vapor state of the additional steam 31 as possible corresponds to the vapor state of the partially relaxed live steam 33, so that in the second wheel chamber 35, a good and easy mixing of these two partial steam flows can be done.
  • the partially relaxed live steam 33 because of a larger distance to be provided between the second MD control wheel 27 and the housing 3 of the steam turbine 1, the second MD control wheel 27 flow around more or less unhindered.
  • the Ventilströmskye in Umströmungs admire be reduced by a conventional ventilation protection device. If the ventilation protection device is insufficient, admixing via the second control valve 37 is recommended.
  • Both partial steam flows 31 and 33 now flow through the second stage part 9 and deliver there work or power to the rotor 5 from.
  • a suitable design of both the first stage part 7 and the second stage part 9 and the first control wheel 15 with its nozzles 19 and the second control wheel 27 with its nozzles 29 can be implemented in overload operation, the fourfold steam flow compared to the design point of the steam turbine 1. This leads to a correspondingly much improved performance increase of the steam turbine, without significant loss of efficiency of the steam turbine.
  • the steam turbine 1 from the partial load operation on the Operate at rated load to overload operation with a good approximately constant efficiency.
  • FIG. 2 the second control wheel 27 and the nozzles 29 are shown schematically in a front view.
  • the second control wheel 27 has blades 39 which are in FIG. 2 are shown only schematically.
  • a valve 43 is provided in each case between an inflow box 41 and the nozzles 29. Depending on how many of the valves 43 are opened, flows a more or less large amount of additional steam via the nozzles 29 on the second MD-control wheel 27 and then mixes with the partially relaxed live steam (see reference numeral 33 in FIG. 1 ).

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)

Description

Die Erfindung betrifft eine Dampfturbine mit mehren Stufenteilen und mit einer vor dem ersten Stufenteil angeordneten Vorrichtung zur Leistungsregelung der Dampfturbine.
Eine solche Dampfturbine ist z.B. in Dokument US 6 308 407 B1 offenbart.The invention relates to a steam turbine having a plurality of stage parts and with a arranged before the first stage part device for power control of the steam turbine.
Such a steam turbine is eg in document US Pat. No. 6,308,407 B1 disclosed.

Dampfturbinen sollen über einen möglichst großen Leistungsbereich zuverlässig und mit konstant hohem Wirkungsgrad betrieben werden können. Diese Anforderungen können von Dampfturbinen herkömmlicher Bauart nicht in vollem Umfang erfüllt werden.Steam turbines should be able to be operated reliably over a large power range and with a constant high efficiency. These requirements can not be fully met by steam turbines of conventional design.

Der Erfindung liegt die Aufgabe zugrunde, eine Dampfturbine bereitzustellen, die sowohl im Normalbetrieb als auch im Teillastbereich mit Leistungen, die deutlich unter der Nennleistung liegen, mit guten Wirkungsgraden betreibbar ist. Außerdem soll die erfindungsgemäße Dampfturbine auch im Betrieb mit Überlast einen guten Wirkungsgrad aufweisen.The invention has for its object to provide a steam turbine, which is operable with good efficiencies both in normal operation and in the partial load range with benefits that are well below the rated power. In addition, the steam turbine according to the invention should also have a good efficiency in operation with overload.

Diese Aufgabe wird erfindungsgemäß mit den technischen Merkmalen des Anspruchs 1 gelöst.This object is achieved with the technical features of claim 1.

Dadurch, dass im Überlastbetrieb zusätzlicher Dampf in die Dampfturbine eingebracht werden kann und mit diesem zusätzlichen Dampf das zweite MD-Regelrad beaufschlagt wird, kann die Leistung der erfindungsgemäßen Dampfturbine ohne nennenswerte Einbußen beim Wirkungsgrad signifikant erhöht werden.Due to the fact that additional steam can be introduced into the steam turbine in overload operation and the second MD control wheel is acted upon by this additional steam, the power of the steam turbine according to the invention can be significantly increased without significant losses in efficiency.

Die Optimierung des Prozesses wird durch eine problemlose Mischung des wieder eingegliederten Dampfes nach dem MD-Regelrad beeinflusst. Es zeigt sich, dass bei hohen Frischdampfzuständen (HD-Dampf) der vierfache Massenstrom im Überlastbetrieb verarbeitet werden kann, ohne nennenswerte Einbußen im Wirkungsgrad bei normalen und Teillastbetrieben.The optimization of the process is influenced by a problem-free mixing of the reintegrated steam after the MD control wheel. It can be seen that at high live steam conditions (HD steam), the quadruple mass flow can be processed in overload operation without significant losses in efficiency in normal and part-load operations.

Dies wird vor allem dann erreicht werden, wenn eine geeignete Aufteilung der beiden Dampfströme vorgenommen wird und die Regelräder und Stufengruppen so ausgelegt werden, dass in der Kammer des MD-Regelrades die beiden Dampfströme annähernd die gleichen Dampfdaten besitzen. Unterschiedliche Dampftemperaturen aus den beiden Dampfströmen sind akzeptabel.This will be achieved especially if a suitable division of the two vapor streams is made and the control wheels and stages groups are designed so that in the chamber of the MD control wheel, the two vapor streams have approximately the same vapor data. Different steam temperatures from the two steam streams are acceptable.

Die Konstruktion der Turbine mit dem optimierten zusätzlichen MD-Regelrad mit Zuspeisung über Düsen ist bei hohen Dampfpesometer sinnvoll, sodass das HD-Regelrad voll zum Einsatz kommen kann, allerdings ohne aufwendige Innengehäusekonstruktionen.The design of the turbine with the optimized additional MD control wheel with feed via nozzles makes sense with high steam spesometers, so that the HP control wheel can be used fully, but without complicated interior housing constructions.

Die erfindungsgemäße Anordnung eines zweiten Regelrades mit den zugehörigen steuerbaren Düsen in einer Kammer zwischen dem ersten Stufenteil Teil der Dampfturbine und dem zweiten Stufenteil Teil der Dampfturbine kann sowohl bei Trommelturbinen als auch bei Kammerturbinen erfolgreich eingesetzt werden.The inventive arrangement of a second control wheel with the associated controllable nozzles in a chamber between the first stage part of the steam turbine part and the second stage part of the steam turbine can be successfully used both in drum turbines and in chamber turbines.

Die Erfindung kann bei Turbinen mit Gleichdruckbeschaufelung und bei Turbinen mit Überdruckbeschaufelung in den mehreren Stufen der Dampfturbine gleichermaßen erfolgreich eingesetzt werden.The invention can be used equally successfully in turbines with constant pressure blading and in turbines with positive pressure blading in the multiple stages of the steam turbine.

Das HD-Regelrad sowie das MD-Regelrad kann sowohl einkränzig wie auch zweikränzig (Curtisrad) ausgeführt werden.The HP ratchet wheel and the MD ratchet wheel can be both single-stringed and two-stringed (Curtis wheel).

Die Konstruktion der Turbine mit HD-Regelrad und nachfolgendem Stufenteil ist oftmals optimal. Allerdings ist diese Konstruktion nicht erfindungsnotwendig. Das HD-Regelrad kann auch als Stufenteil mit einem eventuellen Innengehäuse und einer Drosselregelung im Bypass-/innerem Bypassbetrieb oder als Kombination aus beiden, HD-Regelrad und Bypassbetrieb im Innengehäuse ersetzt werden. Das Grundprinzip ändert sich deshalb nicht, da das MD-Impulsrad mit Düse über das Druckgefälle zwischen HD-Eintrittszustand zum gewählten, optimierten MD-Zustand zusätzlich bei Bedarf leistungssteigernd in Betrieb gesetzt werden kann. Das Prinzip des MD-Impulsrades mit Düsen kann auch als Nachrüstung oder Umbau in einer bestehenden Turbine ausgeführt werden.
Wenn die Dampfturbine im Überlastbetrieb gefahren werden soll, wird erfindungsgemäß die geforderte oder gewünschte Überlastleistung durch den erforderlichen HD-Dampf über die nachgeschaltete zusätzlich integrierte Impulsstufe eingebracht. Die Einspeisung dieses zusätzlichen HD-Dampfes erfolgt über herkömmliche Düsensteuerungen, sodass das Impulsrad wie ein freies Regelrad über die Düsen in Gleitdruckbetrieb zusätzliche Leistung einbringt. Die Zusatzleistung ergibt sich aus der Enthalpiedifferenz zwischen HD-Dampfzustand und dem örtlichen Dampfzustand nach dem MD-Regelrad und der zu optimierenden Dampfmenge.The design of the turbine with HP control wheel and subsequent step part is often optimal. However, this construction is not essential to the invention. The HP control wheel can also be replaced as a step section with an optional inner housing and a throttle control in bypass / internal bypass operation or as a combination of both, HD control wheel and bypass operation in the inner housing. The The basic principle therefore does not change, because the MD impeller with nozzle can also be put into operation as required via the pressure gradient between the HD entry state and the selected, optimized MD state if required. The principle of the MD pulse wheel with nozzles can also be carried out as a retrofit or conversion in an existing turbine.
When the steam turbine is to be operated in overload operation, according to the invention, the required or desired overload power is introduced by the required high-pressure steam via the downstream additionally integrated impulse stage. The injection of this additional HD steam is done via conventional nozzle controls, so that the impulse wheel adds additional power through the nozzles in sliding pressure mode like a free control wheel. The additional power results from the enthalpy difference between the HD vapor state and the local steam state after the MD control wheel and the amount of steam to be optimized.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Zeichnung, deren Beschreibung und den Patentansprüchen entnehmbar. Alle in der Zeichnung, deren Beschreibung und den Patentansprüchen offenbarte Merkmale können sowohl einzeln als auch in Kombination miteinander erfindungswesentlich sein.Further advantages and advantageous embodiments of the invention are the following drawings, the description and the claims removable. All features disclosed in the drawing, the description and the claims can be essential to the invention both individually and in combination with one another.

Zeichnungdrawing

Es zeigen:

Figur 1
einen Längsschnitt durch ein Ausführungsbeispiel einer erfindungsgemäßen Dampfturbine und
Figur 2
ein Ausführungsbeispiel eines Regelrades mit einer Gruppe von steuerbaren Düsen.
Show it:
FIG. 1
a longitudinal section through an embodiment of a steam turbine according to the invention and
FIG. 2
an embodiment of a control wheel with a group of controllable nozzles.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die Figur 1 zeigt eine Dampfturbine mit einem Gehäuse 3 und einem Rotor 5 im Längsschnitt. Die Dampfturbine 1 weist einen ersten Stufenteil 7 und einen zweiten Stufenteil 9 auf.The FIG. 1 shows a steam turbine with a housing 3 and a rotor 5 in longitudinal section. The steam turbine 1 has a first step part 7 and a second step part 9.

Jede der Stufen 7 und 9 besteht aus einer Gruppe von Laufschaufeln 11, die am Rotor 5 befestigt sind und einer Gruppe von Leitschaufeln 13, die üblicherweise über Leitschaufelträger am Gehäuse 3 der Dampfturbine 1 befestigt sind. In Figur 1 sind aus Gründen der Übersichtlichkeit nicht alle Laufschaufeln und nicht alle Leitschaufeln mit dem Bezugszeichen versehen worden. In Strömungsrichtung vor dem ersten Stufenteil 7 ist ein erstes Regelrad 15 am Rotor 5 befestigt. Die in Figur 1 nicht einzeln dargestellten Laufschaufeln des Regelrades 15 sind als Gleichdruckschaufeln ausgeführt.Each of the stages 7 and 9 consists of a group of blades 11 which are fixed to the rotor 5 and a group of vanes 13, which are usually attached via guide vanes to the housing 3 of the steam turbine 1. In FIG. 1 For reasons of clarity, not all moving blades and not all the guide vanes have been provided with the reference number. In the flow direction before the first stage part 7, a first control wheel 15 is attached to the rotor 5. In the FIG. 1 not individually shown blades of the control wheel 15 are designed as equal pressure blades.

In unmittelbarer Nähe des ersten Regelrades 15 ist ein Düsenring 17 vorgesehen, welcher über den Umfang verteilt mehrere Düsen 19 aufweist. Der Düsenring 17 wird über eine Frischdampfleitung 21 mit den Teilleitungen 21a und 21b mit Dampf beaufschlagt. In den Teilleitungen 21a und 21b ist jeweils ein erstes Regelventil 23 vorgesehen. Über die steuerbaren Düsen 19 wird der dem Düsenring 17 zugeführte Frischdampf auf das erste Regelrad 15 geleitet und gelangt anschließend in einen ersten Radraum 25, welcher vom Rotor 5 und vom Gehäuse 3 begrenzt wird.In the immediate vicinity of the first control wheel 15, a nozzle ring 17 is provided, which has a plurality of nozzles 19 distributed over the circumference. The nozzle ring 17 is acted upon by a live steam line 21 with the partial lines 21a and 21b with steam. In the sub-lines 21a and 21b, a first control valve 23 is provided in each case. Via the controllable nozzles 19 of the nozzle ring 17 supplied live steam is passed to the first control wheel 15 and then passes into a first wheel space 25, which is bounded by the rotor 5 and the housing 3.

Daran anschließend gelangt der Frischdampf (nicht dargestellt in Figur 1) in den ersten Stufenteil 7 der Dampfturbine 1 und wird dort entspannt.Subsequently, the live steam (not shown in FIG FIG. 1 ) in the first stage part 7 of the steam turbine 1 and is relaxed there.

Im Anschluss an den ersten Stufenteil 7 ist am Rotor 5 ein zweites MD-Regelrad 27 vorgesehen. Das MD-Regelrad 27 ist bei dem hier gezeigten Ausführungsbeispiel ebenfalls als Impulsrad ausgebildet. Das zweite MD-Regelrad 27 wird von einer oder mehreren Düsen 29, von denen in Figur 1 nur eine dargestellt ist, mit zusätzlichem Dampf beaufschlagt und wirkt dadurch wie eine Regelradstufe im Gleitdruckbetrieb. Dieser Zusatzdampf, welcher in Figur 1 durch einen Pfeil 31 angedeutet ist, vermischt sich vor dem Eintritt in den zweiten Stufenteil 9 mit dem teilweise entspannten Frischdampf, der aus dem ersten Stufenteil 7 ausgetreten ist. Dieser teilweise entspannte Frischdampf ist in Figur 1 mit dem Bezugszeichen 33 versehen worden. Der zwischen erstem Stufenteil 7 und zweitem Stufenteil 9 vorhandene Raum, in dem sich das zweite MD-Regelrad 27 befindet, wird im Folgenden als zweiter Radraum 35 bezeichnet.Subsequent to the first step part 7, a second MD control wheel 27 is provided on the rotor 5. The MD control wheel 27 is also formed in the embodiment shown here as a pulse wheel. The second MD control wheel 27 is of one or more nozzles 29, of which in FIG. 1 only one is shown, acted upon by additional steam and thus acts as a Regelradstufe in Gleitdruckbetrieb. This additional steam, which in FIG. 1 is indicated by an arrow 31, mixed before entering the second stage part 9 with the partially relaxed live steam, which has leaked out of the first stage part 7. This partially relaxed live steam is in FIG. 1 has been provided with the reference numeral 33. The existing between the first stage part 7 and second stage part 9 space in which the second MD control wheel 27 is located, is referred to below as the second wheel chamber 35.

Die Düse 29 ist ebenfalls steuerbar und kann beispielsweise über ein zweites Regelventil 37 oder eine nicht dargestellte Ventilgruppe optimiert werden. Über dieses zweite Regelventil 37 kann die Zufuhr von Zusatzdampf in die Dampfturbine 1 durch die Düse 29 geregelt werden.The nozzle 29 is also controllable and can be optimized, for example via a second control valve 37 or a valve group, not shown. About this second control valve 37, the supply of additional steam can be controlled in the steam turbine 1 through the nozzle 29.

Nachdem die gesamte Dampfmenge durch den zweiten Stufenteil geströmt ist und sich dabei entspannt hat, wird der Abdampf über einen Auslass 39 aus der Dampfturbine 1 abgeführt.After the entire amount of steam has flowed through the second stage part and has thereby relaxed, the exhaust steam is discharged via an outlet 39 from the steam turbine 1.

Im Normalbetrieb, das heißt wenn die Dampfturbine mit ihrer Nennleistung oder im Teillastbereich betrieben wird, ist das zweite Regelventil 37 oder die Ventilgruppe geschlossen und die Dampfturbine 1 arbeitet wie eine konventionelle Dampfturbine. Die Leistungsregelung der Dampfturbine 1 erfolgt ausschließlich über das erste Regelrad 15 beziehungsweise die Ansteuerung der Düsen 19, welche die Beaufschlagung des ersten Regelrades 15 steuern. Die Leistungsregelung der Dampfturbine 1 im Nenn- oder Normalbetrieb und im Teillastbetrieb ist hinlänglich aus dem Stand der Technik bekannt und wird deshalb im Zusammenhang mit der Erfindung nicht im Detail erläutert. Vorteilhaft an dieser Leistungsregelung ist der gleichbleibend gute Wirkungsgrad der Dampfturbine 1 bei Nennlast ebenso wie im Teillastbetrieb ohne erheblichen Konstruktionsmehraufwand wie z. B. Innengehäuse, Turbinen mit Mitteneinströmung oder ähnliches.In normal operation, that is, when the steam turbine is operated at its rated power or in the partial load range, the second control valve 37 or the valve group is closed and the steam turbine 1 operates like a conventional steam turbine. The power control of the steam turbine 1 takes place exclusively via the first control wheel 15 or the control of the nozzles 19, which control the application of the first control wheel 15. The power control of the steam turbine 1 in nominal or normal operation and in partial load operation is well known from the prior art and will therefore not be explained in detail in connection with the invention. An advantage of this power control is the consistently good efficiency of the steam turbine 1 at rated load as well as in Part load operation without significant additional construction costs such. As inner casing, turbines with Mitteneinströmung or the like.

Wenn nun die Dampfturbine 1 mit Überlast betrieben werden soll, wird erfindungsgemäß das zweite Regelventil 37 oder die nicht dargestellte Ventilgruppe geöffnet, so dass Zusatzdampf über die Düse 29 auf das zweite Regelrad 27 strömen kann. Dabei wird die Düse 29 so ausgeführt und optimiert, dass der Dampfzustand des Zusatzdampfes 31 möglichst dem Dampfzustand des teilweise entspannten Frischdampfes 33 entspricht, so dass im zweiten Radraum 35 eine gute und problemlose Mischung dieser beiden Teildampfströme erfolgen kann. Der teilweise entspannte Frischdampf 33 kann wegen eines vorzusehenden größeren Abstandes zwischen zweitem MD-Regelrad 27 und dem Gehäuse 3 der Dampfturbine 1 das zweite MD-Regelrad 27 mehr oder weniger ungehindert umströmen.If now the steam turbine 1 is to be operated with overload, the second control valve 37 or the valve group, not shown, is opened according to the invention, so that additional steam can flow via the nozzle 29 to the second control wheel 27. In this case, the nozzle 29 is designed and optimized so that the vapor state of the additional steam 31 as possible corresponds to the vapor state of the partially relaxed live steam 33, so that in the second wheel chamber 35, a good and easy mixing of these two partial steam flows can be done. The partially relaxed live steam 33, because of a larger distance to be provided between the second MD control wheel 27 and the housing 3 of the steam turbine 1, the second MD control wheel 27 flow around more or less unhindered.

Die Ventilströmverluste im Umströmungsbetrieb werden durch eine übliche Ventilationsschutzeinrichtung gemindert. Falls die Ventilationsschutzeinrichtung nicht ausreicht, wird ein Beimischen über das zweite Regelventil 37 empfohlen.The Ventilströmverluste in Umströmungsbetrieb be reduced by a conventional ventilation protection device. If the ventilation protection device is insufficient, admixing via the second control valve 37 is recommended.

Beide Teildampfströme 31 und 33 strömen nun durch den zweiten Stufenteil 9 und geben dort Arbeit beziehungsweise Leistung an den Rotor 5 ab. Bei geeigneter Auslegung sowohl des ersten Stufenteils 7 und des zweiten Stufenteils 9 als auch des ersten Regelrades 15 mit seinen Düsen 19 und des zweiten Regelrades 27 mit seinen Düsen 29 kann im Überlastbetrieb der vierfache Dampfstrom verglichen mit dem Auslegungspunkt der Dampfturbine 1 umgesetzt werden. Dies führt zu einer entsprechend wesentlich verbesserten Leistungssteigerung der Dampfturbine, ohne nennenswerte Wirkungsgradeinbußen der Dampfturbine.Both partial steam flows 31 and 33 now flow through the second stage part 9 and deliver there work or power to the rotor 5 from. With a suitable design of both the first stage part 7 and the second stage part 9 and the first control wheel 15 with its nozzles 19 and the second control wheel 27 with its nozzles 29 can be implemented in overload operation, the fourfold steam flow compared to the design point of the steam turbine 1. This leads to a correspondingly much improved performance increase of the steam turbine, without significant loss of efficiency of the steam turbine.

Deshalb ist es mit der erfindungsgemäßen Dampfturbine 1 möglich, die Dampfturbine 1 vom Teillastbetrieb über den Betrieb bei Nennlast bis zum Überlastbetrieb mit einem guten annähernd konstanten Wirkungsgrad zu betreiben.Therefore, it is possible with the steam turbine 1 according to the invention, the steam turbine 1 from the partial load operation on the Operate at rated load to overload operation with a good approximately constant efficiency.

In Figur 2 sind das zweite Regelrad 27 sowie die Düsen 29 schematisch in einer Ansicht von vorne dargestellt. Das zweite Regelrad 27 weist Laufschaufeln 39 auf, die in Figur 2 nur schematisch dargestellt sind. Bei dem in Figur 2 dargestellten Ausführungsbeispiel sind drei Düsen 29, die in der Literatur auch als Düsensegmente bezeichnet werden, so angeordnet, dass durch die Austritte der Düse 29 die Laufschaufel 39 des zweiten MD-Regelrades 27 mit zusätzlichem Dampf beaufschlagt werden können. Dazu ist zwischen einem Einströmkasten 41 und den Düsen 29 jeweils ein Ventil 43 vorgesehen. Je nachdem wie viele der Ventile 43 geöffnet werden, strömt eine mehr oder minder große Menge von Zusatzdampf über die Düsen 29 auf das zweite MD-Regelrad 27 und vermischt sich anschließend mit dem teilweise entspannten Frischdampf (siehe Bezugszeichen 33 in Figur 1).In FIG. 2 the second control wheel 27 and the nozzles 29 are shown schematically in a front view. The second control wheel 27 has blades 39 which are in FIG. 2 are shown only schematically. At the in FIG. 2 illustrated embodiment, three nozzles 29, which are also referred to in the literature as nozzle segments, arranged so that the blades 39 of the second MD control wheel 27 can be acted upon by the exits of the nozzle 29 with additional steam. For this purpose, a valve 43 is provided in each case between an inflow box 41 and the nozzles 29. Depending on how many of the valves 43 are opened, flows a more or less large amount of additional steam via the nozzles 29 on the second MD-control wheel 27 and then mixes with the partially relaxed live steam (see reference numeral 33 in FIG FIG. 1 ).

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Dampfturbinesteam turbine
33
Gehäusecasing
55
Rotorrotor
77
erster Stufenteilfirst stage part
99
zweiter Stufenteilsecond stage part
1111
Laufschaufelblade
1313
Leitschaufelvane
1515
erstes Regelradfirst control wheel
1717
Düsenringnozzle ring
1919
Düsejet
2121
FrischdampfleitungSteam line
2323
Regelventilcontrol valve
2525
erster Radraumfirst wheelspace
2727
zweites MD-Regelradsecond MD control wheel
2929
Düsejet
3131
Zusatzdampfadditional steam
3333
teilweise entspannter Frischdampfpartially relaxed steam
3535
zweiter Radraumsecond wheelspace
3737
zweites Regelventilsecond control valve
3939
Laufschaufelblade
4141
EinströmkastenEinströmkasten
4343
VentilValve

Claims (5)

  1. Steam turbine with a plurality of stage sections (7, 9) and with a device for output control of the steam turbine, which is located upstream of the first stage section (7), the device for output control of the steam turbine, which is located upstream of the first stage section (7), being designed as a first control wheel (15) with a nozzle ring (17) and with a plurality of controllable nozzles (19), and a second IP control wheel (27), with nozzles (29), being provided downstream of the first stage section (7).
  2. Steam turbine according to Claim 1,
    characterized in that
    the first control wheel (15), and/or the second IP control wheel (27), is designed as an impulse rotor wheel, especially in Curtis design, or is designed as an impulse wheel.
  3. Steam turbine according to one of the preceding claims,
    characterized in that the second control wheel (27) is subjected to admission of additional steam from a live steam line (21) through a group of controllable nozzles (29).
  4. Steam turbine according to one of the preceding claims,
    characterized in that
    the steam turbine (1) is designed as a chamber-type turbine.
  5. Steam turbine according to one of the preceding claims,
    characterized in that
    the stage sections (7, 9) of the steam turbine (1) have an impulse blading or a reaction blading.
EP04020807.6A 2004-09-01 2004-09-01 Steam turbine Expired - Lifetime EP1632650B1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
PL04020807T PL1632650T3 (en) 2004-09-01 2004-09-01 Steam turbine
EP04020807.6A EP1632650B1 (en) 2004-09-01 2004-09-01 Steam turbine
ES04020807T ES2411657T3 (en) 2004-09-01 2004-09-01 Steam turbine
CNB2005800293887A CN100462525C (en) 2004-09-01 2005-08-12 Steam turbine
PCT/EP2005/053972 WO2006024597A1 (en) 2004-09-01 2005-08-12 Steam turbine
BRPI0514816A BRPI0514816B8 (en) 2004-09-01 2005-08-12 STEAM TURBINE
EP05775974A EP1784558A1 (en) 2004-09-01 2005-08-12 Steam turbine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04020807.6A EP1632650B1 (en) 2004-09-01 2004-09-01 Steam turbine

Publications (2)

Publication Number Publication Date
EP1632650A1 EP1632650A1 (en) 2006-03-08
EP1632650B1 true EP1632650B1 (en) 2013-05-15

Family

ID=34926390

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EP04020807.6A Expired - Lifetime EP1632650B1 (en) 2004-09-01 2004-09-01 Steam turbine
EP05775974A Withdrawn EP1784558A1 (en) 2004-09-01 2005-08-12 Steam turbine

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP05775974A Withdrawn EP1784558A1 (en) 2004-09-01 2005-08-12 Steam turbine

Country Status (6)

Country Link
EP (2) EP1632650B1 (en)
CN (1) CN100462525C (en)
BR (1) BRPI0514816B8 (en)
ES (1) ES2411657T3 (en)
PL (1) PL1632650T3 (en)
WO (1) WO2006024597A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL2078821T3 (en) * 2008-01-10 2011-07-29 Siemens Ag Steam turbine
DE102008033402A1 (en) 2008-07-16 2010-01-21 Siemens Aktiengesellschaft Steam turbine plant and method for operating a steam turbine
DE102008062078B4 (en) 2008-12-16 2019-10-17 Man Energy Solutions Se Entry level for a steam turbine
JP5479191B2 (en) * 2010-04-07 2014-04-23 株式会社東芝 Steam turbine plant
EP2667027A1 (en) * 2012-05-24 2013-11-27 Alstom Technology Ltd Steam rankine cycle solar plant and method for operating such plants
US20180195392A1 (en) * 2017-01-11 2018-07-12 General Electric Company Steam turbine system with impulse stage having plurality of nozzle groups
EP3409895B1 (en) * 2017-05-29 2019-10-30 Siemens Aktiengesellschaft Nozzle casing component for a steam turbine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB228920A (en) * 1924-02-05 1925-09-24 International General Electric Company Incorporated
US4658590A (en) * 1984-12-28 1987-04-21 Hitachi, Ltd. Steam turbine governor system and method of controlling the same
FR2635561B1 (en) * 1988-08-16 1990-10-12 Alsthom Gec STEAM TURBINE INSTALLATION WITH ADJUSTED FILLING
DE4100777A1 (en) * 1990-12-18 1992-06-25 Asea Brown Boveri INLET HOUSING FOR STEAM TURBINE
DE59808650D1 (en) * 1998-12-16 2003-07-10 Alstom Switzerland Ltd Modular steam turbine with standard blading
DE10042317A1 (en) * 2000-08-29 2002-03-14 Alstom Power Nv Steam turbine for combined cycle power plant, has quick acting valves in combination with regulating valves, provided in both fresh steam and bypass paths

Also Published As

Publication number Publication date
WO2006024597A1 (en) 2006-03-09
BRPI0514816A (en) 2008-06-24
EP1632650A1 (en) 2006-03-08
CN100462525C (en) 2009-02-18
BRPI0514816B1 (en) 2019-07-02
ES2411657T3 (en) 2013-07-08
PL1632650T3 (en) 2013-10-31
EP1784558A1 (en) 2007-05-16
CN101010490A (en) 2007-08-01
BRPI0514816B8 (en) 2023-04-25

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