EP2997236B1 - Steam turbine - Google Patents

Steam turbine Download PDF

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Publication number
EP2997236B1
EP2997236B1 EP14753048.9A EP14753048A EP2997236B1 EP 2997236 B1 EP2997236 B1 EP 2997236B1 EP 14753048 A EP14753048 A EP 14753048A EP 2997236 B1 EP2997236 B1 EP 2997236B1
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EP
European Patent Office
Prior art keywords
turbine
steam
blading
wall
sealing
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EP14753048.9A
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German (de)
French (fr)
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EP2997236A1 (en
Inventor
Ingo Assmann
Thilo Müller
Tim Neuberg
Michael STÖBE
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Siemens AG
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Siemens AG
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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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/04—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially axially
    • 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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • 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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/147—Construction, i.e. structural features, e.g. of weight-saving hollow blades
    • 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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/006—Auxiliaries or details not otherwise provided for
    • 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

Definitions

  • the present invention relates to a steam turbine.
  • steam is used to operate steam turbines as the working medium.
  • Pressurized water vapor is generated in a steam boiler and flows via pipelines into the steam turbine.
  • the previously recorded Energy of the working medium converted into kinetic energy.
  • kinetic energy for example, a generator is operated, which converts the generated mechanical power into electrical power.
  • the expanded and cooled steam flows into a condenser where it is condensed by heat transfer in a heat exchanger and returned as liquid water by a pump to the boiler for heating, evaporation and subsequent overheating.
  • the steam power process is evolving towards ever higher live steam parameters. Due to these high live steam parameters, the condensation point of the system shifts deeper into the area of the wet steam and thus a partial condensation.
  • the housing material in the inflow area of the turbine is greatly weakened by the very hot steam in its strength properties, so that it can no longer counteract the pressures prevailing in the interior.
  • a thickening of the housing wall is only conditionally possible, since in very thick housings unacceptably high, thermally induced stresses in the housing wall due to temperature changes occur. In the area of exposure to the reheated steam prevail the same temperatures, therefore, here too, the housing material is greatly weakened. Turbine systems with reheating of conventional systems are thus distinguished by two points in the course of the expansion, which are endangered by extremely high temperatures.
  • the invention was based on the object of reducing the load, in particular the temperature load and pressure load, of a turbine outer casing of a steam turbine.
  • the object of the invention is a steam turbine having a turbine housing with an outer wall, a turbine shaft rotatably mounted in the turbine housing about a turbine axis, a first turbine part, at least a second turbine part, which is arranged in the axial direction of the turbine shaft after the first turbine part, wherein the relaxation direction for steam guided by the steam turbine runs from the first turbine part to the second turbine part, solved.
  • the first turbine part is preferably designed as a high-pressure turbine part
  • the second turbine part is preferably designed as a medium-pressure turbine part and / or as a low-pressure turbine part.
  • the low pressure turbine part can also be designed as a neighboring turbine housing (multi-flow). If, for example, two second turbine parts are provided, the first turbine part is preferably followed by a middle-pressure turbine part and, preferably, one or more low-pressure turbine parts.
  • the steam turbine is designed by the two inner housing in the region of the introduction of the live steam and the reheated steam bivalves. That is, a first inner housing and in the second downstream turbine part, a second inner housing is inserted into the turbine housing in the first turbine part.
  • the first inner housing shields the turbine housing, in particular the outer wall of the turbine housing, from the high temperatures of the incoming live steam.
  • the second inner housing shields the turbine housing, in particular the inner wall of the turbine housing, from the high temperatures of the superheated steam.
  • the pressure gradient is split into two pressure stages, thus allowing very high steam parameters in the inner casings.
  • the arranged in the region of the introduction of the reheated steam second inner housing is a separate component, which is separated from the first inner housing in the region of Frischdampfeinströmung. This makes it possible to make the turbine interior and the relaxation process variable and to arrange both inner housing against the main expansion direction, so that the thrust in the steam turbine can be almost completely compensated.
  • a particular advantage results from the free arrangement of the inner housing, because thus the sealing system of the turbine can be optimized for minimal leakage losses. Due to the rectified relaxation direction of the two inner housing, the sealing shell between the first turbine part and the second turbine part is required. This sealing cup is used exclusively with the pressure difference between the cold and hot line to or from the reheat burdened. Therefore, almost no leakage occurs in the area of the sealing shell.
  • the first inner housing In the relaxation direction of the steam is located in the steam turbine in the first turbine part, the first inner housing.
  • the first blading may include a plurality of blading drums.
  • a blading drum has respective guide blading and blading.
  • the live steam is expanded counter to the main expansion direction of the steam through the steam turbine. This results in two positive effects. First, the first inner housing is cooled by the flowing colder steam and the overall thrust of the turbine is reduced, since builds up in this area, a counter-thrust. After the inner housing, a further drum blading can additionally be arranged in the rear part of the first turbine part. Subsequently, the relaxation process is interrupted by the sealing shell.
  • the cold reheat steam in the rear part of the first turbine part is completely led out of the turbine and superheated in the superheater, in particular in a steam boiler.
  • the superheated steam in the second turbine part flows back into the steam turbine.
  • the steam is very hot, so that the strength of a single-shell turbine housing would be exceeded. That is why the Steam introduced into the second inner housing.
  • the superheated steam is expanded until it has reached a temperature that is permissible for the turbine housing, in particular the outer wall of the turbine housing.
  • the pressure and temperature in the area between the inner housings and the outer wall of the turbine housing are lower than within the inner housing.
  • the turbine outer housing is less stressed. This ensures that the turbine housing or the outer wall of the turbine housing is not or little curved during operation of the steam turbine. Due to the special arrangement and design of the inner housing and the blading in the inner housings, it is achieved that prevail in the relaxation direction in front of and behind the sealing shell no extreme pressure and temperature parameters, so that leakage through the sealing elements of the sealing shell are low.
  • the second inner housing with the second blading as the first inner housing with the first blading, is used against the direction of relaxation of the vapor.
  • the second inner housing is cooled by the steam flowing around.
  • a superheater is arranged, which is used for overheating of the first Intermediate steam line exiting "cold" steam and for forwarding the overheated in the superheater steam to the second intermediate steam line is formed.
  • the first turbine part may preferably be provided in a steam turbine that at least a third blading with a Leitbeschaufelung on the inside of the outer wall and a corresponding blade blading on the turbine shaft is arranged in the rear part of the first turbine part ,
  • This third blading is not located between the inner wall of the blade area of the first inner housing and the turbine shaft, but between the outer wall of the turbine housing and the turbine shaft.
  • the third blading between the first inner housing and the sealing shell can be installed.
  • This third blading also relieves the sealing shell.
  • the possibility of inserting a further blading exists only within the technically controllable parameters of the single-shell housing area.
  • a steam turbine in which arranged in the rear part of the second turbine part or the rear part of the second turbine part downstream in the expansion direction, a third turbine part, in particular a low-pressure turbine part is arranged.
  • the first turbine part is a high-pressure turbine part and the second turbine part is a medium-pressure turbine part or a low-pressure turbine part.
  • the sealing areas of the inner housings are sealed off via sealing elements to the turbine shaft. This can be done for example via brush or labyrinth seals.
  • Fig. 1 schematically the course of the steam 40 is shown in a first embodiment of a steam turbine 1 according to the invention.
  • Live steam 42 flows from outside the turbine housing 2 through a main steam line 41 into the interior of the first inner housing 11.
  • the first inner housing 11 is arranged in the first turbine part 10, which is preferably a high-pressure part.
  • the first inner housing 11 has a first sealing area 12 and a first blade area 13.
  • the first sealing region 12 extends perpendicular to In this case, the first sealing region divides the first turbine part 10 into a front part 14 and a rear part 15.
  • the first blade region 13 extends parallel to the turbine axis 4 against the main expansion direction 30 of the steam 40 through the steam turbine 1 from the first sealing region 12 away.
  • a first Leitbeschaufelung 16 is arranged at the turbine shaft 5 facing side of the first blade portion 13.
  • a correspondingly designed first rotor blading 17 is arranged on the turbine shaft 5.
  • the first guide blading 16 and the first blading 17 together form a first blading or blading drum.
  • the fresh steam 42 flowing into the first inner housing 11 is guided through the first blading 16, 17, that is to say counter to the actual expansion direction 30 of the steam 40.
  • the live steam 42 is thereby released.
  • the pressure and the temperature of the live steam take place in the first blading 16, 17, so that in the front part 14 of the first turbine part 10, the pressure and the temperature are lower than before the relaxation by the first blading 16, 17.
  • the expanded steam 40 flows around the first inner housing 11 completely and cools it thereby.
  • the load of the outer wall 3 of the turbine housing 2 is also reduced by the expansion of the live steam 42 within the first inner housing 11.
  • the relaxed live steam flows along the outside of the first blade area 13 and is interspersed through openings 18 in the first sealing area 12 and through openings 18, respectively the first sealing region 12 and the outer wall 3 of the turbine housing 2 to the rear part 15 of the first turbine part 10 passed. In this rear part 15 of the steam 40 is cooled and the pressure of the steam 40 is reduced.
  • the first turbine part 10 is separated from the second turbine part 20 by a sealing shell 6.
  • the sealing shell 6 extends between the outer wall 3 of the turbine housing 2 and the turbine shaft 5. In this case, the sealing shell 6 is sealed by means of sealing elements 8 to the turbine shaft 5.
  • the cold, Relaxed steam 44 is led out of the rear part 15 through a first intermediate steam line 43 through the turbine housing 2 to an external superheater 50, see Fig. 2 , In the superheater 50, the steam is superheated and returned to the second turbine part 20. That is, the superheated steam 46 is passed through a second intermediate steam line through the turbine housing 2 into the interior of the second inner housing 21 arranged in the second turbine section 10.
  • a second blading 26, 27 is provided within the second inner housing 21, a second blading 26, 27 is provided.
  • the second inner housing 21 is similar or the same as the first inner housing 11.
  • a second sealing portion 22 of the second inner housing 21 extends perpendicular to the turbine axis 4.
  • a second blade portion 23 is arranged, which is opposite to the main expansion direction 30 of the steam 40 extends through the steam turbine 1.
  • the superheated steam 46 is expanded by the second blading 26, 27 and fed to the front part 24 of the second turbine part 20.
  • the second sealing area 22 of the second inner housing separates the front part 24 from the rear part 25.
  • the expanded steam 40 cools both the second inner housing 21 and the outer wall 3 of the turbine housing 2. As a result, the loads on the single-shell turbine housing 2 are reduced.
  • the expanded steam 40 enters the rear part 25 of the second turbine part 20. From there, the cooled, wet exhaust steam 48 via a Dampfauslasstechnisch 47 are discharged from the turbine housing.
  • the first inner housing 11 is cooled by the flowing colder steam 40 and the total thrust of the steam turbine 1 is reduced, since in this area a counter-thrust builds.
  • a further drum blading with a guide blading 60 and a rotor blading 61 can additionally be arranged in the rear part 15 of the first turbine part 10. This relaxes the steam 40 on. Subsequently, the relaxation process is interrupted by the sealing shell 6.
  • the cold reheat steam 44 in the rear part 15 of the first turbine part 10 is completely led out of the steam turbine 1 and overheated again in the superheater 50. Subsequently, the superheated steam 46 flows into the second turbine part 20 back into the steam turbine 1. At this point, the steam 46 is very hot.
  • the superheated steam 46 is introduced into the second inner housing 21.
  • the superheated steam 46 is relaxed until it has reached a temperature permissible for the turbine housing 2, in particular the outer wall 3 of the turbine housing 2.
  • a further blading 70, 71 can be arranged in the rear part 25 of the second turbine part 20, see 3 and 4 , This can be arranged between the outer wall 3 and the turbine shaft 5.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Architecture (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Description

Die vorliegende Erfindung betrifft eine Dampfturbine.The present invention relates to a steam turbine.

In Dampfkraftwerken wird zum Betrieb von Dampfturbinen als Arbeitsmedium Dampf verwendet. Unter Druck stehender Wasserdampf wird in einem Dampfkessel erzeugt und strömt über Rohrleitungen in die Dampfturbine. In der Dampfturbine wird die zuvor aufgenommene
Energie des Arbeitsmediums in Bewegungsenergie umgewandelt. Mittels der Bewegungsenergie wird z.B. ein Generator betrieben, welcher die erzeugte mechanische Leistung in elektrische Leistung umwandelt. Danach strömt der entspannte und abgekühlte Dampf in einen Kondensator, wo er durch Wärmeübertragung in einem Wärmetauscher kondensiert und als flüssiges Wasser durch eine Pumpe erneut dem Dampfkessel zum Erhitzen, Verdampfen und anschließendem Überhitzen zugeführt wird. Um höhere und höchste Wirkungsgrade im Dampfkraftprozess zu erreichen, entwickelt sich der Dampfkraftprozess zu immer höheren Frischdampfparametern hin. Bedingt durch diese hohen Frischdampfparameter verschiebt sich der Kondensationspunkt der Anlage tiefer in den Bereich des Nassdampfes und somit einer Teilkondensation.In steam power plants, steam is used to operate steam turbines as the working medium. Pressurized water vapor is generated in a steam boiler and flows via pipelines into the steam turbine. In the steam turbine, the previously recorded
Energy of the working medium converted into kinetic energy. By means of kinetic energy, for example, a generator is operated, which converts the generated mechanical power into electrical power. Thereafter, the expanded and cooled steam flows into a condenser where it is condensed by heat transfer in a heat exchanger and returned as liquid water by a pump to the boiler for heating, evaporation and subsequent overheating. In order to achieve higher and highest efficiencies in the steam power process, the steam power process is evolving towards ever higher live steam parameters. Due to these high live steam parameters, the condensation point of the system shifts deeper into the area of the wet steam and thus a partial condensation.

Übliche Dampfturbinenanlagen für höchste Wirkungsgrade weisen wenigstens einen Hochdruckteil auf. Zusätzlich können ein Mitteldruck- und ein oder mehrere Niederdruckteile zum Einsatz kommen. Im Niederdruckteil sinkt die Temperatur des Dampfes sehr stark ab, wodurch es zur teilweisen Kondensation des Dampfes kommt. Der Niederdruckteil ist jedoch sehr empfindlich, was den Nässegehalt des Dampfes betrifft. Erreicht der Dampf im Niederdruckteil der Turbine einen Nässeanteil von ca. 8 bis 10 Prozent, sind Maßnahmen zu ergreifen, die den Nässegehalt des Dampfes vor dem Eintritt in den Niederdruckteil und während der weiteren Entspannung in Selbigem auf ein zulässiges Maß reduzieren. Eine dieser Maßnahmen kann die Anwendung einer zusätzlichen Zwischenüberhitzung und/oder Trocknung des Dampfes sein. Durch diese Maßnahme wird der Dampf erneut zwischenüberhitzt und somit gleichzeitig der Wirkungsgrad des Dampfkraft-Prozesses erhöht.Conventional steam turbine plants for maximum efficiency have at least one high-pressure part. In addition, a medium-pressure and one or more low-pressure parts can be used. In the low-pressure part, the temperature of the steam drops very sharply, resulting in partial condensation of the steam. The low-pressure part is very sensitive, however, as far as the moisture content of the steam is concerned. If the steam in the low-pressure part of the turbine reaches a moisture content of about 8 to 10 percent, measures must be taken which reduce the moisture content of the steam to a permissible level before it enters the low-pressure part and during further expansion in the same. One of these measures can the application of additional reheating and / or drying of the steam. By this measure, the steam is re-reheated and thus simultaneously increases the efficiency of the steam power process.

Zur Dampftrocknung / Zwischenüberhitzung wird der gesamte Dampfmassenstrom vor dem Eintritt in den Mittel- bzw. Niederdruckteil vollständig aus der Turbine entnommen und erneut dem Dampfkessel zugeführt. In der Zwischenüberhitzung wird die Dampftemperatur in der Regel erneut auf die des Frischdampfes angehoben, sodass der Nässegehalt am Entspannungsendpunkt sinkt. Anschließend wird der Dampf zurück in die Turbinenanlage geführt. Ohne eine solche Zwischenüberhitzung kann die Dampfturbinenanlage nicht dauerhaft bei niedrigsten Abdampfdrücken (ca. 50...25 mbar) betrieben werden, da auskondensierte Wassertropfen auf die sich rotierenden Turbinenschaufeln auftreffen und dadurch Schaden an der Beschaufelung verursachen.For steam drying / reheating the entire steam mass flow is completely removed from the turbine before entering the middle or low pressure part and fed again to the boiler. In reheating, the steam temperature is usually raised again to that of the live steam, so that the moisture content at the expansion end point decreases. Subsequently, the steam is fed back into the turbine plant. Without such intermediate reheating, the steam turbine plant can not be operated permanently at lowest exhaust steam pressures (about 50 to 25 mbar), since condensed water droplets impinge on the rotating turbine blades and thereby cause damage to the blading.

Bei mehrgehäusigen Dampfturbinenanlagen kann zwischen den einzelnen Teilturbinen eine solche Zwischenüberhitzung/ Trocknung des Wasserdampfs durchgeführt werden.
Eine solche mehrgehäusige Dampfturbinenanlage ist beispielsweise in der US 3 206 166 A offenbartIn multi-chamber steam turbine plants, such reheating / drying of the water vapor can be carried out between the individual turbine sections.
Such a multi-stage steam turbine plant is for example in the US Pat. No. 3,206,166 A disclosed

Das Gehäusematerial im Einströmbereich der Turbine wird durch den sehr heißen Dampf in seinen Festigkeitseigenschaften stark geschwächt, so dass es den im Inneren herrschenden Drücken nicht mehr entgegenwirken kann. Eine Aufdickung der Gehäusewand ist nur bedingt möglich, da bei sehr dicken Gehäusen unzulässig hohe, thermisch bedingte Spannungen in der Gehäusewand infolge von Temperaturänderungen auftreten. Im Bereich der Beaufschlagung mit dem zwischenüberhitzten Dampf herrschen dieselben Temperaturen, daher wird auch hier das Gehäusematerial stark geschwächt. Damit unterscheiden sich Turbinenanlagen mit Zwischenüberhitzung von herkömmlichen Anlagen durch zwei Punkte im Entspannungsverlauf, die durch extrem hohe Temperaturen gefährdet sind.The housing material in the inflow area of the turbine is greatly weakened by the very hot steam in its strength properties, so that it can no longer counteract the pressures prevailing in the interior. A thickening of the housing wall is only conditionally possible, since in very thick housings unacceptably high, thermally induced stresses in the housing wall due to temperature changes occur. In the area of exposure to the reheated steam prevail the same temperatures, therefore, here too, the housing material is greatly weakened. Turbine systems with reheating of conventional systems are thus distinguished by two points in the course of the expansion, which are endangered by extremely high temperatures.

Bei einer eingehäusigen Dampfturbine mit Zwischenüberhitzung wird an zwei Stellen stark überhitzter Dampf in die Turbine geleitet. Dabei wird das Turbinenaußengehäuse durch die auftretenden Temperaturen und Drücke an zwei Punkten thermisch stark belastet.For a steam turbine with intermediate reheating, superheated steam is sent to the turbine in two places. In this case, the turbine outer housing is thermally stressed by the temperatures and pressures occurring at two points.

Dampfturbinen mit Zwischenüberhitzung wurden bisher entweder als zweigehäusige Turbinenanlagen ausgeführt oder es wurden geringere Dampfparameter verwendet, so dass das einschaliges Turbinenaußengehäuse nicht überlastet wurde.Steam turbines with reheat were previously either designed as zweigehäusige turbine systems or lower steam parameters were used, so that the single-shell turbine outer casing was not overloaded.

Die auftretenden, erforderlichen Parameter liegen jedoch häufig über den möglichen Parametern einschaliger Turbinengehäuse.However, the required parameters that occur occur frequently above the possible parameters of single-shell turbine housings.

Ausgehend von der zuvor beschriebenen Problematik bei Dampfturbinen lag der Erfindung die Aufgabe zugrunde, die Belastung, insbesondere die Temperaturbelastung und Druckbelastung, eines Turbinenaußengehäuses einer Dampfturbine zu verringern.Based on the problem described above in steam turbines, the invention was based on the object of reducing the load, in particular the temperature load and pressure load, of a turbine outer casing of a steam turbine.

Diese Aufgabe wird durch eine Dampfturbine mit den Merkmalen des unabhängigen Patentanspruchs 1 gelöst. Weitere Merkmale und Details der Erfindung ergeben sich aus den abhängigen Patentansprüchen, der Beschreibung und den Zeichnungen.This object is achieved by a steam turbine having the features of independent patent claim 1. Further features and details of the invention will become apparent from the dependent claims, the description and the drawings.

Das heißt, die Aufgabe der Erfindung wird durch eine Dampfturbine mit einem Turbinengehäuse mit einer Außenwand, einer in dem Turbinengehäuse drehbar um eine Turbinenachse gelagerten Turbinenwelle, einem ersten Turbinenteil, wenigstens einem zweiten Turbinenteil, welches in Axialrichtung der Turbinenwelle nach dem ersten Turbinenteil angeordnet ist, wobei die Entspannungsrichtung für durch die Dampfturbine geleiteten Dampf vom ersten Turbinenteil zum zweiten Turbinenteilverläuft, gelöst. Der erste Turbinenteil ist vorzugsweise als Hochdruckturbinenteil, der zweite Turbinenteil ist vorzugsweise als Mitteldruckturbinenteil und/oder als Niederdruckturbinenteil ausgebildet. Der Niederdruckturbinenteil kann auch als nebenstehendes weiteres Turbinengehäuse (mehrflutig) ausgeführt sein. Sind beispielsweise zwei zweite Turbinenteile vorgesehen, sind dem ersten Turbinenteil vorzugsweise ein Mitteldruckturbinenteil und diesem vorzugsweise ein oder mehrere Niederdruckturbinenteile nachgeordnet.That is, the object of the invention is a steam turbine having a turbine housing with an outer wall, a turbine shaft rotatably mounted in the turbine housing about a turbine axis, a first turbine part, at least a second turbine part, which is arranged in the axial direction of the turbine shaft after the first turbine part, wherein the relaxation direction for steam guided by the steam turbine runs from the first turbine part to the second turbine part, solved. The first turbine part is preferably designed as a high-pressure turbine part, the second turbine part is preferably designed as a medium-pressure turbine part and / or as a low-pressure turbine part. The low pressure turbine part can also be designed as a neighboring turbine housing (multi-flow). If, for example, two second turbine parts are provided, the first turbine part is preferably followed by a middle-pressure turbine part and, preferably, one or more low-pressure turbine parts.

Die Dampfturbine ist durch nachfolgende Merkmale gekennzeichnet:

  • Zwischen dem ersten Turbinenteil und dem zweiten Turbinenteil ist eine zusätzliche Dichtschale, auch als Trennwand bezeichnet, in dem Turbinengehäuse, insbesondere an der Innenseite des Turbinenaußengehäuses, drehfest angeordnet. Die Dichtschale ist über Dichtelemente, beispielsweise Bürsten- oder Labyrinthdichtungen, zu der Turbinenwelle hin abgedichtet.
  • In dem ersten Turbinenteil ist an der Innenseite der Außenwand, das heißt an der der Turbinenwelle zugewandten Seite der Außenwand, ein erstes Innengehäuse rotationssymmetrisch um die und abgedichtet zu der Turbinenwelle hin angeordnet. Das erste Innengehäuse weist einen ersten Dichtungsbereich auf. Der erste Dichtungsbereich unterteilt das erste Turbinenteil bezogen auf die Entspannungsrichtung in einen vorderen Teil und einen hinteren Teil. Ferner weist das erste Innengehäuse einen zur Turbinenachse parallelen beziehungsweise annähernd parallelen ersten Schaufelbereich auf.
  • An der der Turbinenwelle zugewandten Innenwandung des ersten Schaufelbereichs ist eine erste Leitbeschaufelung angeordnet. An der Turbinenwelle ist eine zur ersten Leitbeschaufelung korrespondierende erste Laufbeschaufelung angeordnet. Die erste Leitbeschaufelung und die erste Laufbeschaufelung bilden eine erste Beschaufelungstrommel.
  • In dem zweiten Turbinenteil ist an der Innenseite der Außenwand ein zweites Innengehäuse rotationssymmetrisch um die und abgedichtet zu der Turbinenwelle hin angeordnet. Das zweite Innengehäuse weist einen zweiten Dichtbereich auf, der das zweite Turbinenteil bezogen auf die Entspannungsrichtung in einem vorderen Teil und einen hinteren Teil unterteilt. Ferner weist das zweite Innengehäuse einen zweiten Schaufelbereich auf.
  • An der der Turbinenwelle zugewandten Innenwandung des zweiten Schaufelbereichs des zweiten Innengehäuses ist eine zweite Leitbeschaufelung angeordnet. An der Turbinenwelle ist entsprechend eine zur zweiten Leitbeschaufelung korrespondierende zweite Laufbeschaufelung angeordnet. Die zweite Leitbeschaufelung und die zweite Laufbeschaufelung bilden eine zweite Beschaufelungstrommel.
  • Die Schaufelbereiche der Innengehäuse erstrecken sich jeweils entgegen der Entspannungsrichtung von den jeweiligen Dichtbereichen weg. Das bedeutet, der erste Schaufelbereich des ersten Innengehäuses erstreckt sich von der Seite des ersten Dichtbereiches des ersten Innengehäuses weg, die der Dichtschale abgewandt ist.
  • Die Dampfturbine weist zumindest eine Frischdampfleitung auf, durch die Frischdampf von außenhalb des Turbinengehäuses durch die Außenwand des Turbinengehäuses und durch den ersten Schaufelbereich des ersten Innengehäuses in den Bereich zwischen dem ersten Schaufelbereich und dem ersten Dichtbereich, der Turbinenwelle und der ersten Beschaufelung geführt werden kann. Die Außenwand und der erste Schaufelbereich weisen zur Anbindung der Frischdampfleitung Öffnungen auf. Die Frischdampfleitung ist an dem ersten Innengehäuses befestigt. Die Frischdampfleitung ist abgedichtet durch die Öffnung in der Außenwand des Turbinengehäuses hindurchgeführt.
The steam turbine is characterized by the following features:
  • Between the first turbine part and the second turbine part, an additional sealing shell, also referred to as a partition, in the turbine housing, in particular on the inside of the turbine outer housing, rotatably arranged. The sealing shell is sealed via sealing elements, for example brush or labyrinth seals, towards the turbine shaft.
  • In the first turbine part, on the inside of the outer wall, that is to say on the side of the outer wall facing the turbine shaft, a first inner housing is arranged rotationally symmetrically about and sealed to the turbine shaft. The first inner housing has a first sealing area. The first sealing region divides the first turbine part relative to the expansion direction into a front part and a rear part. Furthermore, the first inner housing has a first blade area parallel or approximately parallel to the turbine axis.
  • At the turbine shaft facing inner wall of the first blade portion, a first Leitbeschaufelung is arranged. At the turbine shaft corresponding to the first Leitbeschaufelung first run blading is arranged. The first vane and the first vane form a first blading drum.
  • In the second turbine part, a second inner housing is arranged on the inside of the outer wall rotationally symmetrical about and sealed to the turbine shaft. The second inner housing has a second sealing area, the divided the second turbine part relative to the relaxation direction in a front part and a rear part. Furthermore, the second inner housing has a second blade area.
  • At the turbine shaft facing inner wall of the second blade portion of the second inner housing, a second Leitbeschaufelung is arranged. At the turbine shaft corresponding to the second Leitbeschaufelung corresponding second run blading is arranged accordingly. The second vane and the second vane form a second blading drum.
  • The blade regions of the inner casings each extend counter to the direction of expansion away from the respective sealing regions. This means that the first blade area of the first inner housing extends away from the side of the first sealing area of the first inner housing, which faces away from the sealing shell.
  • The steam turbine has at least one live steam line through which live steam can be guided from the outside of the turbine housing through the outer wall of the turbine housing and through the first blade area of the first inner housing into the area between the first blade area and the first sealing area, the turbine shaft and the first blading. The outer wall and the first blade area have openings for connecting the main steam line. The main steam line is attached to the first inner housing. The main steam line is sealed through the opening in the outer wall of the turbine housing passed.

Die Innengehäuse können über Stege mit dem Turbinengehäuse verbunden sein. Es ist denkbar, dass die Innengehäuse einstückig, insbesondere monolithisch, mit dem Turbinengehäuse ausgebildet sind.

  • Die Dichtbereiche weisen in dem der Außenwand zugewandten Bereich jeweils Öffnungen auf, durch die Dampf von dem jeweils vorderen Teil in den jeweiligen hinteren Teil der Turbinenteile gelangen kann. Das bedeutet, die Öffnungen sind an dem radial äußeren Bereich der Dichtbereiche der Innengehäuse, nahe der Außenwand des Turbinengehäuses, angeordnet.
  • In der Außenwand des Turbinengehäuses, im Bereich des hinteren Teils des ersten Turbinenteils ist zumindest eine erste Zwischendampföffnung vorgesehen, in der eine Zwischendampfleitung angeordnet ist. Über diese Zwischendampfleitung kann "erkalteter" Dampf aus dem hinteren Teil des ersten Turbinenteils herausgeführt und einem extern angeordneten Überhitzer zugeführt werden.
  • Ferner ist eine weitere Zwischendampföffnung in der Außenwand des Turbinengehäuses vorgesehen. Diese ist im Bereich des zweiten Innengehäuses in der Außenwand angeordnet. Über eine zweite Zwischendampfleitung, die durch Zwischendampföffnung hindurchgeführt ist, kann überhitzter Dampf durch die Außenwand des Turbinengehäuses und durch den zweiten Schaufelbereich des zweiten Innengehäuses in den Bereich zwischen dem zweiten Schaufelbereich und dem zweiten Dichtbereich, der Turbinenwelle und der zweiten Beschaufelung geführt werden. Der überhitzte Dampf kommt von dem extern angeordneten Überhitzer.
  • Des Weiteren ist zumindest eine Dampfauslassöffnung beziehungsweise eine Dampfauslassleitung in der Außenwand des Turbinengehäuses vorgesehen. Über die Dampfauslassleitung kann Abdampf aus dem hinteren Teil des zweiten Turbinenteils aus dem Turbinengehäuse herausgeführt werden.
The inner housing can be connected via webs with the turbine housing. It is conceivable that the inner housing are integrally formed, in particular monolithic, with the turbine housing.
  • In the region facing the outer wall, the sealing regions each have openings through which steam can pass from the respective front part into the respective rear part of the turbine parts. That is, the openings are arranged at the radially outer portion of the sealing portions of the inner housing, near the outer wall of the turbine housing.
  • In the outer wall of the turbine housing, in the region of the rear part of the first turbine part, at least one first intermediate steam opening is provided, in which an intermediate steam line is arranged. Via this intermediate steam line, "cooled" steam can be led out of the rear part of the first turbine part and fed to an externally arranged superheater.
  • Furthermore, a further intermediate steam opening is provided in the outer wall of the turbine housing. This is arranged in the region of the second inner housing in the outer wall. Superheated steam may be passed through the outer wall of the turbine housing and through the second vane area of the second inner housing into the area between the second vane area and the second sealing area, the turbine shaft and the second blading via a second intermediate steam line. The superheated steam comes from the external superheater.
  • Furthermore, at least one steam outlet opening or a steam outlet line is provided in the outer wall of the turbine housing. Via the steam outlet pipe, exhaust steam can be led out of the turbine housing from the rear part of the second turbine part.

Bei einer derartigen Dampfturbine mit Zwischenüberhitzung wird an zwei Stellen stark überhitzter Dampf in die Dampfturbine geleitet.In such a steam turbine with reheat superheated steam is fed into the steam turbine in two places.

Die Dampfturbine ist durch die beiden Innengehäuse im Bereich der Einleitung des Frischdampfe und des zwischenüberhitzten Dampfes zweischalig ausgeführt. Das heißt, in das Turbinengehäuse ist in dem ersten Turbinenteil ein erstes inneres Gehäuse und in dem zweiten nachgeordneten Turbinenteil ein zweites inneres Gehäuse eingesetzt. Das erste Innengehäuse schirmt das Turbinengehäuse, insbesondere die Außenwand des Turbinengehäuses, von den hohen Temperaturen des einströmenden Frischdampfes ab. Das zweite Innengehäuse schirmt das Turbinengehäuse, insbesondere die Innenwand des Turbinengehäuses, von den hohen Temperaturen des zwischenüberhitzten Dampfes ab. Gleichzeitig wird das Druckgefälle auf zwei Druckstufen aufgeteilt und ermöglicht damit sehr hohe Dampfparameter in den inneren Gehäusen.The steam turbine is designed by the two inner housing in the region of the introduction of the live steam and the reheated steam bivalves. That is, a first inner housing and in the second downstream turbine part, a second inner housing is inserted into the turbine housing in the first turbine part. The first inner housing shields the turbine housing, in particular the outer wall of the turbine housing, from the high temperatures of the incoming live steam. The second inner housing shields the turbine housing, in particular the inner wall of the turbine housing, from the high temperatures of the superheated steam. At the same time, the pressure gradient is split into two pressure stages, thus allowing very high steam parameters in the inner casings.

Das im Bereich der Einleitung des zwischenüberhitzten Dampfes angeordnete zweite Innengehäuse ist ein eigenes Bauteil, das vom ersten Innengehäuse im Bereich der Frischdampfeinströmung getrennt ist. Damit ist es möglich das Turbineninnere und den Entspannungsverlauf variabel zu gestalten und beide Innengehäuse entgegen der Hauptentspannungsrichtung anzuordnen, so dass der Schub in der Dampfturbine nahezu vollkommen ausgeglichen werden kann.The arranged in the region of the introduction of the reheated steam second inner housing is a separate component, which is separated from the first inner housing in the region of Frischdampfeinströmung. This makes it possible to make the turbine interior and the relaxation process variable and to arrange both inner housing against the main expansion direction, so that the thrust in the steam turbine can be almost completely compensated.

Weiterhin werden durch die Anordnung und Ausgestaltung der beiden Innengehäuse diese jeweils von großen Dampfmengen allseitig umströmt und stellen dadurch ein gleichmäßiges Temperaturfeld sicher. Somit kann durch eine gleichmäßige Temperaturverteilung an der Außenwand des Turbinengehäuses eine Verkrümmung der selbigen minimiert werden.Furthermore, the arrangement and design of the two inner housing, these are each surrounded by large amounts of steam on all sides and thereby ensure a uniform temperature field safely. Thus, by a uniform temperature distribution on the outer wall of the turbine housing, a curvature of the same can be minimized.

Ein besonderer Vorteil ergibt sich aus der freien Anordnung der Innengehäuse, denn damit kann das Dichtungssystem der Turbine auf minimale Leckage-Verluste optimiert werden. Durch die gleichgerichtete Entspannungsrichtung der beiden Innengehäuse ist die Dichtschale zwischen dem ersten Turbinenteil und dem zweiten Turbinenteil erforderlich. Diese Dichtschale wird ausschließlich mit der Druckdifferenz zwischen der kalten und der heißen Leitung zur beziehungsweise von der Zwischenüberhitzung belastet. Im Bereich der Dichtschale entsteht deshalb nahezu keine Leckage.A particular advantage results from the free arrangement of the inner housing, because thus the sealing system of the turbine can be optimized for minimal leakage losses. Due to the rectified relaxation direction of the two inner housing, the sealing shell between the first turbine part and the second turbine part is required. This sealing cup is used exclusively with the pressure difference between the cold and hot line to or from the reheat burdened. Therefore, almost no leakage occurs in the area of the sealing shell.

In Entspannungsrichtung des Dampfes befindet sich bei der Dampfturbine im ersten Turbinenteil das erste Innengehäuse. In dieses strömt der Frischdampf über die Frischdampfleitung ein. Die erste Beschaufelung kann mehrere Beschaufelungstrommeln aufweisen. Eine Beschaufelungstrommel weist jeweils Leitbeschaufelung und Laufbeschaufelung auf. Der Frischdampf wird entgegen der Hauptentspannungsrichtung des Dampfes durch die Dampfturbine entspannt. Daraus ergeben sich zwei positive Effekte. Zunächst wird das erste Innengehäuse durch den umströmenden kälteren Dampf gekühlt und der Gesamtschub der Turbine wird verringert, da sich in diesem Bereich ein Gegenschub aufbaut. Nach dem Innengehäuse kann im hinteren Teil des ersten Turbinenteils zusätzlich eine weitere Trommelbeschaufelung angeordnet werden. Anschließend wird der Entspannungsverlauf durch die Dichtschale unterbrochen. Der kalte Zwischenüberhitzungsdampf im hinteren Teil des ersten Turbinenteils wird vollständig aus der Turbine geführt und im Überhitzer, insbesondere in einem Dampfkessel, erneut überhitzt. Anschließend strömt der überhitzte Dampf im zweiten Turbinenteil zurück in die Dampfturbine. An dieser Stelle ist der Dampf sehr heiß, so dass die Festigkeit eines einschaligen Turbinengehäuses überschritten würde. Deshalb wird der
Dampf in das zweite Innengehäuse eingeleitet. In diesem zweiten Innengehäuse wird der überhitzte Dampf soweit entspannt, bis er eine für das Turbinengehäuse, insbesondere die Außenwand des Turbinengehäuses, zulässige Temperatur erreicht hat.In the relaxation direction of the steam is located in the steam turbine in the first turbine part, the first inner housing. In this, the live steam flows through the main steam line. The first blading may include a plurality of blading drums. A blading drum has respective guide blading and blading. The live steam is expanded counter to the main expansion direction of the steam through the steam turbine. This results in two positive effects. First, the first inner housing is cooled by the flowing colder steam and the overall thrust of the turbine is reduced, since builds up in this area, a counter-thrust. After the inner housing, a further drum blading can additionally be arranged in the rear part of the first turbine part. Subsequently, the relaxation process is interrupted by the sealing shell. The cold reheat steam in the rear part of the first turbine part is completely led out of the turbine and superheated in the superheater, in particular in a steam boiler. Subsequently, the superheated steam in the second turbine part flows back into the steam turbine. At this point, the steam is very hot, so that the strength of a single-shell turbine housing would be exceeded. That is why the
Steam introduced into the second inner housing. In this second inner housing, the superheated steam is expanded until it has reached a temperature that is permissible for the turbine housing, in particular the outer wall of the turbine housing.

Durch die Entspannung des Frischdampfes in der ersten Beschaufelung innerhalb des erste Innengehäuses und die Entspannung des überhitzten Dampfes in der zweiten Beschaufelung innerhalb des zweiten Innengehäuses sind jeweils der Druck und die Temperatur im Bereich zwischen den Innengehäusen und der Außenwand des Turbinengehäuses niedriger als innerhalb der Innengehäuse. Hierdurch wird das Turbinenaußengehäuse weniger belastet. Hierdurch ist sichergestellt, dass das Turbinengehäuse beziehungsweise die Außenwand des Turbinengehäuses bei Betrieb der Dampfturbine nicht bzw. wenig gekrümmt wird. Durch die spezielle Anordnung und Ausgestaltung der Innengehäuse und der Beschaufelung in den Innengehäusen, wird erreicht, dass in Entspannungsrichtung vor und hinter der Dichtschale keine extremen Druck- und Temperaturparameter herrschen, so dass Leckagen durch die Dichtelemente der Dichtschale gering sind.By relaxing the live steam in the first bladder within the first inner housing and relaxing the superheated steam in the second bladder within the second inner housing, the pressure and temperature in the area between the inner housings and the outer wall of the turbine housing are lower than within the inner housing. As a result, the turbine outer housing is less stressed. This ensures that the turbine housing or the outer wall of the turbine housing is not or little curved during operation of the steam turbine. Due to the special arrangement and design of the inner housing and the blading in the inner housings, it is achieved that prevail in the relaxation direction in front of and behind the sealing shell no extreme pressure and temperature parameters, so that leakage through the sealing elements of the sealing shell are low.

Das zweite Innengehäuse mit der zweiten Beschaufelung wird, wie das erste Innengehäuse mit der ersten Beschaufelung, entgegen der Entspannungsrichtung des Dampfes eingesetzt. Daraus ergeben sich die gleichen positiven Effekte, wie beim ersten Innengehäuse, nämlich eine verbesserte Kühlung der Außenseite des zweiten Innengehäuses und der Innenseite der Außenwand des Turbinengehäuses sowie ein Schubausgleich. Da sich die Schubausgleichseffekte addieren, wird die Wirkung erheblich verstärkt, was sich positiv auf Lagerverluste und die Größe eines optional einsetzbaren in Entspannungsrichtung nachgeordneten Niederdruckteils in den dem Turbinengehäuse.The second inner housing with the second blading, as the first inner housing with the first blading, is used against the direction of relaxation of the vapor. This results in the same positive effects as in the first inner housing, namely an improved cooling of the outside of the second inner housing and the inside of the outer wall of the turbine housing and a thrust balance. Since the thrust balancing effects add up, the effect is significantly increased, which has a positive effect on bearing losses and the size of an optionally usable in the expansion direction downstream low-pressure part in the turbine housing.

Das zweite Innengehäuse wird durch den umströmenden Dampf gekühlt.The second inner housing is cooled by the steam flowing around.

Durch den Einsatz der beiden Innengehäuse kann eine normalerweise vollständig zweischalig ausgeführte Dampfturbine mit einem größtenteils einschaligen Turbinengehäuse ausgeführt werden. Hierdurch wird der konstruktive Bauaufwand der Dampfturbine erheblich reduziert. Wird dem Mitteldruckteil, das heißt dem zweiten Turbinenteil, eine Niederdruckteil nachgeordnet, ist es aufgrund der beiden Innengehäuse möglich, eine vollständige Kondensationsturbinenanlage mit Zwischenüberhitzung innerhalb eines einzigen Turbinengehäuses anzuordnen.Through the use of the two inner housing, a normally completely double-shell steam turbine with a largely single-shell turbine housing can be performed. As a result, the structural construction cost of the steam turbine is significantly reduced. If a low-pressure part is arranged downstream of the medium-pressure part, that is to say the second turbine part, it is possible on the basis of the two inner housings to arrange a complete condensation turbine installation with reheat within a single turbine housing.

Außerhalb des Turbinengehäuses der Dampfturbine wird ein Überhitzer angeordnet, der zur Überhitzung des aus der ersten Zwischendampfleitung austretenden "kalten" Dampfes und zur Weiterleitung des in dem Überhitzer überhitzen Dampfes zu der zweiten Zwischendampfleitung ausgebildet ist.Outside the turbine housing of the steam turbine, a superheater is arranged, which is used for overheating of the first Intermediate steam line exiting "cold" steam and for forwarding the overheated in the superheater steam to the second intermediate steam line is formed.

Um eine besonders gute Entspannung des Dampfes in der ersten Teilturbine zu erlangen, kann vorzugsweise bei einer Dampfturbine vorgesehen sein, dass im hinteren Teil des ersten Turbinenteils wenigstens eine dritte Beschaufelung mit einer Leitbeschaufelung an der Innenseite der Außenwand und einer korrespondierenden Laufbeschaufelung an der Turbinenwelle angeordnet ist. Diese dritte Beschaufelung ist nicht zwischen der Innenwand des Schaufelbereiches des ersten Innengehäuses und der Turbinenwelle angeordnet, sondern zwischen der Außenwand des Turbinengehäuses und der Turbinenwelle.In order to obtain a particularly good relaxation of the steam in the first turbine part, it may preferably be provided in a steam turbine that at least a third blading with a Leitbeschaufelung on the inside of the outer wall and a corresponding blade blading on the turbine shaft is arranged in the rear part of the first turbine part , This third blading is not located between the inner wall of the blade area of the first inner housing and the turbine shaft, but between the outer wall of the turbine housing and the turbine shaft.

Durch die gleichgerichtete Anordnung der Innengehäuse, das heißt der Schaufelbereiche der Innengehäuse, und die zusätzliche Dichtschale kann die dritte Beschaufelung zwischen dem ersten Innengehäuse und der Dichtschale installiert werden. Diese dritte Beschaufelung entlastet ebenfalls die Dichtschale. Die Möglichkeit eine weitere Beschaufelung einzufügen besteht allerdings nur innerhalb der technisch beherrschbaren Parameter des einschaligen Gehäusebereiches.By the rectified arrangement of the inner housing, that is, the blade portions of the inner housing, and the additional sealing shell, the third blading between the first inner housing and the sealing shell can be installed. This third blading also relieves the sealing shell. However, the possibility of inserting a further blading exists only within the technically controllable parameters of the single-shell housing area.

Ferner kann bei einer Dampfturbine vorgesehen sein, dass im hinteren Teil des zweiten Turbinenteils eine vierte Beschaufelung mit einer Leitbeschaufelung an der Innenseite der Außenwand und einer korrespondierenden Laufbeschaufelung an der Turbinenwelle angeordnet ist. Auch durch diese weitere Beschaufelung kann nochmals eine weitere Entspannung des durch die Dampfturbine geleiteten Dampfes erfolgen. Hierdurch kann die Belastung in diesem Bereich auf das Turbinengehäuse nochmals reduziert werden. Daher ist eine Dampfturbine vorteilhaft, bei der im hinteren Teil des zweiten Turbinenteils oder dem hinteren Teil des zweiten Turbinenteils in Entspannungsrichtung nachgeordnet ein drittes Turbinenteil, insbesondere ein Niederdruckturbinenteil, angeordnet ist.Furthermore, it may be provided in a steam turbine that in the rear part of the second turbine part, a fourth blading with a Leitbeschaufelung on the inside of the outer wall and a corresponding blade blading is arranged on the turbine shaft. Also by this further blading can be done again a further relaxation of the guided through the steam turbine steam. As a result, the load in this area can be further reduced to the turbine housing. Therefore, a steam turbine is advantageous in which arranged in the rear part of the second turbine part or the rear part of the second turbine part downstream in the expansion direction, a third turbine part, in particular a low-pressure turbine part is arranged.

Bevorzugt kann bei einer Dampfturbine vorgesehen sein, dass der erste Turbinenteil ein Hochdruckturbinenteil und der zweite Turbinenteil ein Mitteldruckturbinenteil oder ein Niederdruckturbinenteil sind.In the case of a steam turbine, it can preferably be provided that the first turbine part is a high-pressure turbine part and the second turbine part is a medium-pressure turbine part or a low-pressure turbine part.

Zur Vermeidung von Leckagen an den Innengehäusen sind die Dichtbereiche der Innengehäuse über Dichtelemente zur Turbinenwelle abgedichtet. Dies kann beispielsweise über Bürsten- oder Labyrinthdichtungen erfolgen.To avoid leaks on the inner housings, the sealing areas of the inner housings are sealed off via sealing elements to the turbine shaft. This can be done for example via brush or labyrinth seals.

Die vorliegende Erfindung wird anhand der beigefügten Zeichnungsfiguren näher erläutert. Es zeigen jeweils schematisch:

Figur 1
den Verlauf des Dampfes in einer ersten Ausführungsform einer erfindungsgemäßen Dampfturbine,
Figur 2
Dampfleitungen durch das Turbinengehäuse der Dampfturbine gemäß Figur 1,
Figur 3
den Verlauf des Dampfes in einer zweiten Ausführungsform einer erfindungsgemäßen Dampfturbine, und
Figur 4
Dampfleitungen durch das Turbinengehäuse der Dampfturbine gemäß Figur 2.
The present invention will be explained in more detail with reference to the accompanying drawing figures. Each show schematically:
FIG. 1
the course of the steam in a first embodiment of a steam turbine according to the invention,
FIG. 2
Steam lines through the turbine housing of the steam turbine according to FIG. 1 .
FIG. 3
the course of the steam in a second embodiment of a steam turbine according to the invention, and
FIG. 4
Steam lines through the turbine housing of the steam turbine according to FIG. 2 ,

In den Fig. 1 bis 4 sind Elemente mit gleicher Funktion und Wirkungsweise jeweils mit den gleichen Bezugszeichen versehen.In the Fig. 1 to 4 elements with the same function and mode of action are each provided with the same reference numerals.

In Fig. 1 ist schematisch der Verlauf des Dampfes 40 in einer ersten Ausführungsform einer erfindungsgemäßen Dampfturbine 1 dargestellt. Frischdampf 42 strömt von außerhalb des Turbinengehäuses 2 durch eine Frischdampfleitung 41 in das Innere des ersten Innengehäuses 11. Das erste Innengehäuse 11 ist in dem ersten Turbinenteil 10, der vorzugsweise ein Hochdruckteil ist, angeordnet. Das erste Innengehäuse 11 weist einen ersten Dichtbereich 12 und einen ersten Schaufelbereich 13 auf. Der erste Dichtbereich 12 erstreckt sich senkrecht zu der Turbinenachse 4. Dabei unterteilt der erste Dichtbereich das ersten Turbinenteil 10 in einen vorderen Teil 14 und einen hinteren Teil 15. Der erste Schaufelbereich 13 erstreckt sich parallel zu der Turbinenachse 4 entgegen der Hauptentspannungsrichtung 30 des Dampfes 40 durch die Dampfturbine 1 von dem ersten Dichtbereich 12 weg. An der der Turbinenwelle 5 zugewandten Seite des ersten Schaufelbereiches 13 ist eine erste Leitbeschaufelung 16 angeordnet. Korrespondierend zu dieser ist eine entsprechend ausgebildete erste Laufbeschaufelung 17 an der Turbinenwelle 5 angeordnet. Die erste Leitbeschaufelung 16 und die erste Laufbeschaufelung 17 bilden zusammen eine erste Beschaufelung beziehungsweise Beschaufelungstrommel. Der in das erste Innengehäuse 11 einströmende Frischdampf 42 wird durch die ersten Beschaufelung 16, 17 geführt, das heißt entgegen der eigentlichen Entspannungsrichtung 30 des Dampfes 40. Dabei entspannt der Frischdampf 42. Der Druck und die Temperatur des Frischdampfes nehmen in der ersten Beschaufelung 16, 17 ab, so dass in dem vorderen Teil 14 des ersten Turbinenteils 10 der Druck und die Temperatur geringer sind, als vor der Entspannung durch die erste Beschaufelung 16, 17. Der entspannte Dampf 40 umströmt das erste Innengehäuse 11 vollständig und kühlt dieses dadurch. Die Belastung der Außenwand 3 des Turbinengehäuses 2 ist ebenfalls reduziert durch die Entspannung des Frischdampfes 42 innerhalb des ersten Innengehäuses 11. Der entspannte Frischdampf strömt an der Außenseite des ersten Schaufelbereiches 13 entlang und wird durch Öffnungen 18 in dem ersten Dichtbereich 12 beziehungsweise durch Öffnungen 18 zwischen dem ersten Dichtbereich 12 und der Außenwand 3 des Turbinengehäuses 2 zu dem hinteren Teil 15 des ersten Turbinenteils 10 geleitet. In diesem hinteren Teil 15 ist der Dampf 40 erkaltet und der Druck des Dampfes 40 reduziert.In Fig. 1 schematically the course of the steam 40 is shown in a first embodiment of a steam turbine 1 according to the invention. Live steam 42 flows from outside the turbine housing 2 through a main steam line 41 into the interior of the first inner housing 11. The first inner housing 11 is arranged in the first turbine part 10, which is preferably a high-pressure part. The first inner housing 11 has a first sealing area 12 and a first blade area 13. The first sealing region 12 extends perpendicular to In this case, the first sealing region divides the first turbine part 10 into a front part 14 and a rear part 15. The first blade region 13 extends parallel to the turbine axis 4 against the main expansion direction 30 of the steam 40 through the steam turbine 1 from the first sealing region 12 away. At the turbine shaft 5 facing side of the first blade portion 13, a first Leitbeschaufelung 16 is arranged. Corresponding to this, a correspondingly designed first rotor blading 17 is arranged on the turbine shaft 5. The first guide blading 16 and the first blading 17 together form a first blading or blading drum. The fresh steam 42 flowing into the first inner housing 11 is guided through the first blading 16, 17, that is to say counter to the actual expansion direction 30 of the steam 40. The live steam 42 is thereby released. The pressure and the temperature of the live steam take place in the first blading 16, 17, so that in the front part 14 of the first turbine part 10, the pressure and the temperature are lower than before the relaxation by the first blading 16, 17. The expanded steam 40 flows around the first inner housing 11 completely and cools it thereby. The load of the outer wall 3 of the turbine housing 2 is also reduced by the expansion of the live steam 42 within the first inner housing 11. The relaxed live steam flows along the outside of the first blade area 13 and is interspersed through openings 18 in the first sealing area 12 and through openings 18, respectively the first sealing region 12 and the outer wall 3 of the turbine housing 2 to the rear part 15 of the first turbine part 10 passed. In this rear part 15 of the steam 40 is cooled and the pressure of the steam 40 is reduced.

Der erste Turbinenteil 10 ist durch eine Dichtschale 6 von dem zweiten Turbinenteil 20 getrennt. Die Dichtschale 6 erstreckt sich zwischen der Außenwand 3 des Turbinengehäuses 2 und der Turbinenwelle 5. Dabei ist die Dichtschale 6 mittels Dichtelementen 8 zu der Turbinenwelle 5 abgedichtet. Der erkaltete, entspannte Dampf 44 wird aus dem hinteren Teil 15 durch eine erste Zwischendampfleitung 43 durch das Turbinengehäuse 2 herausgeführt zu einem externen Überhitzer 50, siehe Fig. 2. In dem Überhitzer 50 wird der Dampf überhitzt und dem zweiten Turbinenteil 20 wieder zugeführt. Das heißt, der überhitzte Dampf 46 wird durch eine zweite Zwischendampfleitung durch das Turbinengehäuse 2 in das Innere des in dem zweiten Turbinenteil 10 angeordneten zweiten Innengehäuses 21 geleitet. Innerhalb des zweiten Innengehäuses 21 ist eine zweite Beschaufelung 26, 27 vorgesehen. Das zweite Innengehäuse 21 ist ähnlich oder gleich aufgebaut wie das erste Innengehäuse 11. Ein zweiter Dichtbereich 22 des zweiten Innengehäuses 21 erstreckt sich senkrecht zu der Turbinenachse 4. An dem zweiten Dichtbereich 22 ist ein zweiter Schaufelbereich 23 angeordnet, der sich von diesem entgegen der Hauptentspannungsrichtung 30 des Dampfes 40 durch die Dampfturbine 1 erstreckt. Der überhitzte Dampf 46 wird durch die zweite Beschaufelung 26, 27 entspannt und dem vorderen Teil 24 des zweiten Turbinenteils 20 zugeführt. Der zweite Dichtbereich 22 des zweiten Innengehäuses trennt den vorderen Teil 24 von dem hinteren Teil 25. Der entspannte Dampf 40 kühlt sowohl das zweite Innengehäuse 21 als auch die Außenwand 3 des Turbinengehäuses 2. Hierdurch sind die Belastungen auf das einschalige Turbinengehäuse 2 reduziert. Über Öffnungen 28 in dem zweiten Dichtbereich 22 beziehungsweise über Öffnungen zwischen dem zweiten Dichtbereich 22 und der Außenwand 3 des Turbinengehäuses 2 gelangt der entspannte Dampf 40 in den hinteren Teil 25 des zweiten Turbinenteils 20. Von dort kann der erkaltete, nasse Abdampf 48 über eine Dampfauslassleitung 47 aus dem Turbinengehäuse abgeführt werden.The first turbine part 10 is separated from the second turbine part 20 by a sealing shell 6. The sealing shell 6 extends between the outer wall 3 of the turbine housing 2 and the turbine shaft 5. In this case, the sealing shell 6 is sealed by means of sealing elements 8 to the turbine shaft 5. The cold, Relaxed steam 44 is led out of the rear part 15 through a first intermediate steam line 43 through the turbine housing 2 to an external superheater 50, see Fig. 2 , In the superheater 50, the steam is superheated and returned to the second turbine part 20. That is, the superheated steam 46 is passed through a second intermediate steam line through the turbine housing 2 into the interior of the second inner housing 21 arranged in the second turbine section 10. Within the second inner housing 21, a second blading 26, 27 is provided. The second inner housing 21 is similar or the same as the first inner housing 11. A second sealing portion 22 of the second inner housing 21 extends perpendicular to the turbine axis 4. At the second sealing portion 22, a second blade portion 23 is arranged, which is opposite to the main expansion direction 30 of the steam 40 extends through the steam turbine 1. The superheated steam 46 is expanded by the second blading 26, 27 and fed to the front part 24 of the second turbine part 20. The second sealing area 22 of the second inner housing separates the front part 24 from the rear part 25. The expanded steam 40 cools both the second inner housing 21 and the outer wall 3 of the turbine housing 2. As a result, the loads on the single-shell turbine housing 2 are reduced. Via openings 28 in the second sealing region 22 or via openings between the second sealing region 22 and the outer wall 3 of the turbine housing 2, the expanded steam 40 enters the rear part 25 of the second turbine part 20. From there, the cooled, wet exhaust steam 48 via a Dampfauslassleitung 47 are discharged from the turbine housing.

Durch die spezielle Ausgestaltung und Anordnung der beiden Innengehäuse 11, 21 kann der Schub in der Dampfturbine 1 nahezu vollkommen ausgeglichen werden.Due to the special design and arrangement of the two inner housing 11, 21, the thrust in the steam turbine 1 can be almost completely compensated.

Das erste Innengehäuse 11 wird durch den umströmenden kälteren Dampf 40 gekühlt und der Gesamtschub der Dampfturbine 1 wird verringert, da sich in diesem Bereich ein Gegenschub aufbaut. Nach dem ersten Innengehäuse 11 kann im hinteren Teil 15 des ersten Turbinenteils 10 zusätzlich eine weitere Trommelbeschaufelung mit einer Leitbeschaufelung 60 und einer Laufbeschaufelung 61 angeordnet werden. Hierdurch entspannt der Dampf 40 weiter. Anschließend wird der Entspannungsverlauf durch die Dichtschale 6 unterbrochen. Der kalte Zwischenüberhitzungsdampf 44 im hinteren Teil 15 des ersten Turbinenteils 10 wird vollständig aus der Dampfturbine 1 geführt und im Überhitzer 50 erneut überhitzt. Anschließend strömt der überhitzte Dampf 46 in den zweiten Turbinenteil 20 zurück in die Dampfturbine 1. An dieser Stelle ist der Dampf 46 sehr heiß. Deshalb wird der überhitzte Dampf 46 in das zweite Innengehäuse 21 eingeleitet. In diesem zweiten Innengehäuse 21 wird der überhitzte Dampf 46 soweit entspannt, bis er eine für das Turbinengehäuse 2, insbesondere die Außenwand 3 des Turbinengehäuses 2, zulässige Temperatur erreicht hat. In dem hinteren Teil 25 des zweiten Turbinenteils 20 kann zusätzlich eine weitere Beschaufelung 70, 71 angeordnet werden, siehe Fig. 3 und 4. Diese kann zwischen der Außenwand 3 und der Turbinenwelle 5 angeordnet werden.The first inner housing 11 is cooled by the flowing colder steam 40 and the total thrust of the steam turbine 1 is reduced, since in this area a counter-thrust builds. After the first inner housing 11, a further drum blading with a guide blading 60 and a rotor blading 61 can additionally be arranged in the rear part 15 of the first turbine part 10. This relaxes the steam 40 on. Subsequently, the relaxation process is interrupted by the sealing shell 6. The cold reheat steam 44 in the rear part 15 of the first turbine part 10 is completely led out of the steam turbine 1 and overheated again in the superheater 50. Subsequently, the superheated steam 46 flows into the second turbine part 20 back into the steam turbine 1. At this point, the steam 46 is very hot. Therefore, the superheated steam 46 is introduced into the second inner housing 21. In this second inner housing 21, the superheated steam 46 is relaxed until it has reached a temperature permissible for the turbine housing 2, in particular the outer wall 3 of the turbine housing 2. In addition, a further blading 70, 71 can be arranged in the rear part 25 of the second turbine part 20, see 3 and 4 , This can be arranged between the outer wall 3 and the turbine shaft 5.

Claims (6)

  1. Steam turbine (1), comprising a turbine casing (2) with an outer wall (3), a turbine shaft (5) mounted rotatably about a turbine axis (4) in the turbine casing (2), a first turbine part (10), and at least one second turbine part (20) which is arranged downstream of the first turbine part (10) in the axial direction of the turbine shaft (5), wherein the expansion direction (30) for steam (40) conducted through the steam turbine (1) runs from the first turbine part (10) to the second turbine part (20),
    wherein between the first turbine part (10) and the second turbine part (20), a sealing shell (6) is arranged on the turbine casing (2), in particular on the inner side (7) of the outer wall (3) for rotation therewith, said sealing shell being formed in a sealing manner with respect to the turbine shaft (5) via sealing elements (8),
    - wherein in the first turbine part (10) a first inner casing (11) is arranged rotationally symmetrically about the and sealed with respect to the turbine shaft (5) on the inner side (7) of the outer wall (3), wherein the first inner facing (11) has a first sealing region (12) which is perpendicular or approximately perpendicular to the turbine axis (4) and divides the first turbine part (10) with respect to the expansion direction (30) into a front part (14) and a rear part (15), and has a first blade region (13) which is parallel or approximately parallel to the turbine axis (4),
    - and wherein a first guide vane blading (16) is arranged on the inner wall of the first blade region (13) which inner wall faces the turbine shaft (5), and a first rotor blading (17) corresponding to the first guide vane blading (16) is arranged on the turbine shaft (5),
    characterized
    - in that the second turbine part (20), a second inner casing (21) is arranged rotationally symmetrically about the part (20) with respect to the expansion direction (30) into a front part (24) and a rear part (25), and has a second blade region (23) which is parallel or approximately parallel to the turbine axis (4),
    - in that a second guide vane blading (26) is arranged on the inner wall of the second blade region (23), which inner wall faces the turbine shaft (5), and a second rotor blading (27) corresponding to the second guide vane blading (26) is arranged on the turbine shaft (5),
    - in that the blade regions (13, 23) of the inner casings (11, 21) each extend of a from the respective sealing regions (12, 22) counter to the expansion direction (30),
    - in that fresh steam (42) can be guided via at least one fresh steam line (41) through the outer wall (3) of the turbine casing (2) and through the first blade region (13) of the first inner casing (11) into the region between the first blade region (13) and the first sealing region (12), the turbine shaft (5) and the first blading (16, 17),
    - in that the sealing regions (12, 22) have, in the region facing the outer wall (3), respective openings (18, 28) through which steam (40) can pass from the front part (14, 24) in each case into the respective rear part (15, 25) of the turbine parts (10, 20),
    - in that cold steam (44) can be guided out of the rear part (15) of the first turbine part (10) via at least one first intermediate steam line (43),
    - in that superheated steam (46) can be guided via at least one second intermediate steam line (45) through the outer wall (3) of the turbine casing (2) and through the second blade region (23) of the second inner casing (21) into the region between the second blade region (23) and the second sealing region (22), the turbine shaft (5) of the second blading (26, 27), and
    - in that exhaust steam (48) from the rear part (25) of the second turbine part (20) can be guided out of the turbine casing (2) at least one steam outlet line (47) in the outer wall (3).
  2. Steam turbine (1) according to Claim 1, characterized in that at least one third blading with a guide vane blading (60) on the inner side (7) of the outer wall (3) and with a corresponding rotor blading (61) on the turbine shaft (5) is arranged in the rear part (15) of the first turbine part (10).
  3. Steam turbine (1) according to Claim 1 or 2, characterized in that a fourth blading with a guide vane blading (70) on the inner side (7) of the outer wall (3) and a corresponding rotor blading (71) on the turbine shaft (5) is arranged in the rear part (25) of the second turbine part (20).
  4. Steam turbine (1) according to one of the preceding claims, characterized in that a third turbine part, in particular a low-pressure turbine part, is arranged in the rear part (25) of the second turbine part (20) or downstream of the rear part (25) of the second turbine part (20) in the expansion direction (30).
  5. Steam turbine (1) according to one of the preceding claims, characterized in that the first turbine part (10) is a high-pressure turbine part and the second turbine part (20) is a medium-pressure turbine part or a low-pressure turbine part.
  6. Steam turbine (1) according to one of the preceding claims, characterized in that the sealing regions (12, 22) are sealed with respect to the turbine shaft (5) via sealing elements.
EP14753048.9A 2013-09-30 2014-08-12 Steam turbine Active EP2997236B1 (en)

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DE102013219771.3A DE102013219771B4 (en) 2013-09-30 2013-09-30 steam turbine
PCT/EP2014/067194 WO2015043815A1 (en) 2013-09-30 2014-08-12 Steam turbine

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US20160215623A1 (en) 2016-07-28
KR102319046B1 (en) 2021-10-29
US10227873B2 (en) 2019-03-12
CN105612314A (en) 2016-05-25
BR112016003647B1 (en) 2022-12-06
BR112016003647A2 (en) 2017-08-01
RU2016117168A (en) 2017-11-13
PL2997236T3 (en) 2017-09-29
EP2997236A1 (en) 2016-03-23
DE102013219771B4 (en) 2016-03-31
RU2016117168A3 (en) 2018-04-03
WO2015043815A1 (en) 2015-04-02
DE102013219771A1 (en) 2015-04-02
RU2659633C2 (en) 2018-07-03
JP6203948B2 (en) 2017-09-27

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