EP2431570A1 - Steam turbine with a dummy piston and wet steam blockage - Google Patents
Steam turbine with a dummy piston and wet steam blockage Download PDFInfo
- Publication number
- EP2431570A1 EP2431570A1 EP10177090A EP10177090A EP2431570A1 EP 2431570 A1 EP2431570 A1 EP 2431570A1 EP 10177090 A EP10177090 A EP 10177090A EP 10177090 A EP10177090 A EP 10177090A EP 2431570 A1 EP2431570 A1 EP 2431570A1
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- European Patent Office
- Prior art keywords
- steam
- steam turbine
- pressure
- balance piston
- thrust balance
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- 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.)
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Classifications
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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
- 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
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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
- F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
- F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
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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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/007—Preventing corrosion
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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
- F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
- F01D3/02—Machines or engines with axial-thrust balancing effected by working-fluid characterised by having one fluid flow in one axial direction and another fluid flow in the opposite direction
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- 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
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- 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
- F05D2260/00—Function
- F05D2260/60—Fluid transfer
- F05D2260/608—Aeration, ventilation, dehumidification or moisture removal of closed spaces
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- 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
- F05D2260/00—Function
- F05D2260/95—Preventing corrosion
Definitions
- the invention relates to a steam turbine comprising a rotatably mounted rotor, an inner housing and arranged between the rotor and the inner housing high pressure flow channel, the rotor having a thrust balance piston, the steam turbine having a thrust balance piston line, the thrust balance piston line opens into a thrust balance piston antechamber.
- steam turbines are divided into several sub-turbines, such as e.g. a high pressure, medium pressure and low pressure turbine part.
- the aforementioned sub-turbines differ essentially in that the steam parameters such as temperature and pressure of the incoming steam are different.
- a high-pressure turbine part experiences the highest steam parameters and is thus subjected to the highest thermal load.
- the effluent from the high-pressure turbine section steam is reheated via a reheater and flowed in a medium-pressure turbine section, the steam flows after flowing through the medium-pressure turbine section in the low-pressure turbine section without reheating.
- each turbine section has its own housing.
- the high-pressure turbine section and the medium-pressure turbine part in a common outer housing are housed.
- part turbines in which the medium-pressure part and the low-pressure part are arranged together in an outer housing.
- the turbine sections are formed with a rotor, an inner housing arranged around the rotor and an outer housing.
- the rotor comprises moving blades, which form a flow channel with the guide vanes arranged in the inner housing.
- the high-pressure turbine sections are designed to be single-flow, with the result that a comparatively high thrust as a result of the steam pressure on the rotor leads in one direction. Therefore, the rotors are usually formed with thrust balance piston. By flow of the thrust balance piston at a defined location, a pressure is generated, which leads to a counter thrust, which holds the rotor substantially force-free in the axial direction.
- the high temperatures require the use of materials that withstand the high temperatures and pressures.
- Nickel base based steels or high percentage chromium steels are also suitable for use at high temperatures.
- the components of a steam turbine must be made relatively resistant to corrosion, since some components are flown with wet steam at the same time high flow velocity of the steam. Such components would result in corrosion and erosion upon exposure to wet steam coupled with high flow velocity. This issue is currently addressed by taking relatively costly measures.
- One of the measures would be, for example, the use of high-chromium materials or the use of coatings, which are applied to the components and thus avoid corrosion and erosion.
- the steam flowing out of the flow channel which is essentially a wet steam
- the object of the invention is to avoid corrosion and erosion damage caused by wet steam.
- a steam turbine comprising a rotatably mounted rotor, an inner housing and a first flow channel arranged between the rotor and the inner housing, the rotor having a thrust balance piston, the steam turbine having a thrust balance steam line, wherein the thrust balance steam line opens into a thrust balance piston antechamber the steam turbine has a wet steam line which produces a fluidic connection between a gap space and a first pressure space, wherein the gap space is arranged between the rotor and the inner housing.
- the thrust balance steam line directs steam into a thrust balance piston anvil which, as a result of the pressure, exerts a force on the rotor to compensate for thrust.
- the thrust balance piston is typically a portion of the rotor with a radius ideally selected for the desired thrust balance at an axial location corresponding pressure level.
- the vestibule is located in front of a radial lateral surface.
- the thrust balance steam line is connected to a source of steam having a particular vapor at a pressure and a temperature. This steam mixes with the effluent from the high-pressure turbine section steam and passes between the thrust balance piston and the inner housing in a space between the inner housing and the outer housing.
- the steam turbine is now carried out with a wet steam line.
- This wet steam line opens into a gap, which is located between the inner housing and the rotor.
- the wet steam flowing out of the high-pressure turbine part flow channel flows in the direction of the thrust balance piston.
- This wet steam line is fluidically connected to a first pressure chamber, wherein in this first pressure chamber, a lower pressure prevails than in the gap. As a result, the wet steam present in this gap space is virtually completely sucked off and removed in the wet steam line.
- the mixing of the wet steam with the steam in the thrust balance piston antechamber is thereby drastically reduced.
- An outflow of a mixed vapor formed from the wet steam and the steam in the thrust balance piston antechamber is thereby almost prevented, so that virtually no mixing steam flows between the thrust balance piston and the inner housing to the outer housing.
- the outer housing can thus be made of a material having a lower corrosion and erosion resistance. This will lead to a cheaper version of the outer housing.
- the turbine has a second flow channel, wherein the thrust balance steam line is fluidically connected to the second inflow region or another pressure chamber.
- a vapor which may be superheated steam, passes from the second flow passage via the thrust balance piston steam line to the thrust balance piston antechamber.
- the first pressure chamber is arranged in the second flow channel, wherein the first pressure chamber has a pressure which is less than the pressure in the gap space. This leads to that in the Gap was wet steam from the high-pressure turbine section via the wet steam line flows into the first pressure chamber. Thus, the unwanted wet steam, before it could ever reach the outer housing, sucked and discharged into the second flow channel.
- the FIG. 1 shows a cross-section of a steam turbine 1.
- the steam turbine 1 comprises a combined high-pressure and medium-pressure turbine part 2.
- the essential feature of the steam turbine 1 is that a common outer housing 3 is arranged around the high-pressure and medium-pressure turbine section 2.
- the steam turbine 1 comprises a rotor 4, on which a first blading region 5, which is arranged in a high-pressure flow channel 6.
- the rotor 5 further comprises a second blading region 7, which is arranged in a medium-pressure flow channel 8.
- Both the high-pressure flow channel 6 and the medium-pressure flow channel 8 comprise a plurality of rotor blades 4, which are not provided with reference numerals, and guide vanes, which are not provided with reference symbols, arranged in an inner housing 9.
- high pressure and medium pressure turbine parts refer to the steam parameters of the incoming steam.
- the pressure of the incoming into the high-pressure turbine section steam is greater than the pressure of the in the medium-pressure turbine section incoming steam.
- high-pressure and medium-pressure turbine sections also differ in that the steam flowing out of the high-pressure turbine section is reheated in a reheater and then flows into the medium-pressure turbine section.
- steam turbine 1 is characterized by a common inner housing 9 for the first blading region 5 and the second blading region 7.
- steam flows into a high-pressure inflow region 10. From there, the steam flows through the first impingement region 5 in a first flow direction 11. After flowing through the first blading region 5, the steam flows out into a high-pressure outflow region 12 out of the steam turbine.
- the steam present in the high-pressure outflow region 12 has temperature and pressure values which differ from the temperature and pressure values of the steam in the high-pressure inflow region 10. In particular, the temperature and pressure values have become lower due to expansion of the steam.
- the steam present in the high-pressure outflow region 12 has such temperature and pressure values that this steam can be referred to as wet steam.
- this wet steam contains the smallest condensed water particles. These smallest water particles in the wet steam at high speeds in an impact on a component of the steam turbine 1 lead to erosion and corrosion damage.
- the majority of the wet steam flows out of the steam turbine 1 via the high-pressure outflow region 12.
- a residual leakage flow remains, which is arranged in a gap 13 between the rotor 4 and the inner housing 9.
- This wet steam located in the gap 13 flows in the first flow direction 11 and strikes a thrust balance piston 14.
- the thrust balance piston 14 has a thrust balance piston antechamber 15, in which a superheated steam flows.
- This superheated steam is located in the thrust balance piston antechamber 15, which is arranged between the thrust balance piston 14 and a rear wall 16 of the inner housing 9.
- the superheated steam located in the thrust balance piston antechamber 15 leads to an axially acting force on the thrust balance piston 14 and thus on the rotor 4.
- a gap 17 Between the inner housing 9 and the rotor 4 in the region of the thrust balance piston 14 is a gap 17. Through this gap, a vapor can flow, which passes into a gap 18 which is located between the outer housing 3 and the inner housing 9. A wet steam present in the gap 17 could lead to an increased risk of corrosion and erosion of the outer housing 3.
- a wet steam line 19 is now arranged in the steam turbine 1, which establishes a fluidic connection between the gap space 13 and a first pressure space 20, the gap space 13 being arranged between the rotor 4 and the inner housing 9.
- the first pressure chamber 20 is located in the second Beschaufelungs Scheme 7, in particular in a second flow channel 21. Das in FIG. 1 illustrated embodiment shows that the first pressure chamber 20 is arranged in the region of the second flow channel 21. Also, the pressure in this first pressure chamber 20 should be such that the pressure for the wet steam in the gap 13 is greater than in the first pressure chamber 20, so that a pressure gradient in the wet steam line 19 prevails, which causes the wet steam from the gap 13 to first pressure chamber 20 passes.
- the thrust balance piston 14 extends in a radial direction 22, which is formed substantially perpendicular to the rotation axis 23.
- the thrust balance piston steam line 24 is fluidly connected to a steam source 25.
- the inflow region 26 forms the steam source 25th
- This steam which flows into the medium-pressure turbine section in the inflow region 26, is a superheated steam which enters the thrust balance piston antechamber 15.
- the steam source 25 may also be arranged outside the steam turbine 1.
- the inner housing 9 has a feed opening 27, with which the wet steam line 19 can be connected.
- the FIG. 2 shows an enlarged section of the high pressure Ausström Schemes 12 of the high pressure turbine section.
- the inner housing 9 is designed such that a high-pressure outflow region 12 is enclosed and rests in the region of the gap space 13 with respect to the rotor 4.
- the gap 13 should be as small as possible so that the wet steam located in the high-pressure outflow region 12 does not flow out over the gap 13.
- the majority of the wet steam will pass through the high-pressure discharge area 12 to a reheater.
- a lesser part passes as leakage flow between the rotor 4 and the inner housing 9 in the gap space 13. Therefore, a not-shown cavity is arranged in the inner housing 9, which is connected to the gap space 13.
- the first pressure space 20 which has a lower pressure than the pressure in the gap space 13, serves as the drive for this suction. Further flow of the leakage flow formed in the gap 13 in the direction of the thrust balance piston chamber 15 is prevented by the greater part of the wet steam flowing in the wet steam line 19 is sucked off.
- the superheated steam entering the thrust balance piston antechamber 15 via a thrust balance piston line 24 will spread in two directions. First, the superheated steam will spread in the direction of the gap 17 and eventually hit the outer casing 3. Another part of the superheated steam flows in the direction of the gap 13 and, like the wet steam, is sucked out via the wet steam line 19 to the first pressure chamber 20.
Abstract
Description
Die Erfindung betrifft eine Dampfturbine umfassend einen drehbar gelagerten Rotor, einem Innengehäuse und einen zwischen dem Rotor und dem Innengehäuse angeordneten Hochdruck-Strömungskanal, wobei der Rotor einen Schubausgleichskolben aufweist, wobei die Dampfturbine eine Schubausgleichskolbenleitung aufweist, wobei die Schubausgleichskolbenleitung in einen Schubausgleichskolbenvorraum mündet.The invention relates to a steam turbine comprising a rotatably mounted rotor, an inner housing and arranged between the rotor and the inner housing high pressure flow channel, the rotor having a thrust balance piston, the steam turbine having a thrust balance piston line, the thrust balance piston line opens into a thrust balance piston antechamber.
Aus thermodynamischen Gründen werden Dampfturbinen bei vergleichsweise hohen Temperaturen eingesetzt. Die Entwicklung in letzter Zeit im modernen Strömungsmaschinenbau ging dahin, dass Temperaturen im Einströmbereich einer Hochdruck-Teilturbine von über 700°C, sogar über 720°C geplant sind. Solch hohe Temperaturen führen zu einer besonderen thermischen Beanspruchung der eingesetzten Materialien.For thermodynamic reasons, steam turbines are used at comparatively high temperatures. Recent developments in modern turbomachinery have meant that temperatures in the inflow area of a high-pressure turbine section of over 700 ° C, even over 720 ° C are planned. Such high temperatures lead to a special thermal stress on the materials used.
Herkömmlicherweise werden Dampfturbinen in mehrere Teilturbinen unterteilt, wie z.B. einer Hochdruck-, Mitteldruck- und Niederdruckteilturbine. Die vorgenannten Teilturbinen unterscheiden sich im Wesentlichen dadurch, dass die Dampfparameter wie Temperatur und Druck des einströmenden Dampfes unterschiedlich sind. So erfährt eine Hochdruck-Teilturbine die höchsten Dampfparameter und wird somit am stärksten thermisch belastet. Der aus der Hochdruck-Teilturbine ausströmende Dampf wird über einen Zwischenüberhitzer wieder erhitzt und in einer Mitteldruck-Teilturbine geströmt, wobei der Dampf nach Durchströmen der Mitteldruck-Teilturbine in die Niederdruckteilturbine ohne Zwischenüberhitzung einströmt.Conventionally, steam turbines are divided into several sub-turbines, such as e.g. a high pressure, medium pressure and low pressure turbine part. The aforementioned sub-turbines differ essentially in that the steam parameters such as temperature and pressure of the incoming steam are different. Thus, a high-pressure turbine part experiences the highest steam parameters and is thus subjected to the highest thermal load. The effluent from the high-pressure turbine section steam is reheated via a reheater and flowed in a medium-pressure turbine section, the steam flows after flowing through the medium-pressure turbine section in the low-pressure turbine section without reheating.
In der Regel werden die Teilturbinen separat ausgebildet, das bedeutet, dass jede Teilturbine ein eigenes Gehäuse umfasst. Es sind allerdings auch Bauformen bekannt, in denen die Hochdruck-Teilturbine und die Mitteldruck-Teilturbine in einem gemeinsamen Außengehäuse untergebracht sind. Genau so bekannt sind Teilturbinen, in denen der Mitteldruckteil und der Niederdruckteil gemeinsam in einem Außengehäuse angeordnet sind.As a rule, the turbine sections are formed separately, which means that each turbine section has its own housing. However, there are also known designs in which the high-pressure turbine section and the medium-pressure turbine part in a common outer housing are housed. Just as well known are part turbines in which the medium-pressure part and the low-pressure part are arranged together in an outer housing.
Besonders im Hochdruck- und Mitteldruckbereich, werden die Teilturbinen mit einem Rotor, einem um den Rotor angeordneten Innengehäuse und einen Außengehäuse ausgebildet. Der Rotor umfasst Laufschaufeln, die mit den im Innengehäuse angeordneten Leitschaufeln einen Strömungskanal bilden. In der Regel werden die Hochdruck-Teilturbinen einflutig ausgebildet, was dazu führt, dass ein vergleichsweise hoher Schub in Folge des Dampfdruckes auf den Rotor in eine Richtung führt. Daher werden die Rotoren meistens mit Schubausgleichskolben ausgebildet. Durch Beströmen des Schubausgleichskolbens an einer definierten Stelle wird ein Druck erzeugt, der zu einem Gegenschub führt, der den Rotor im Wesentlichen kraftfrei in axialer Richtung hält.Particularly in the high-pressure and medium-pressure range, the turbine sections are formed with a rotor, an inner housing arranged around the rotor and an outer housing. The rotor comprises moving blades, which form a flow channel with the guide vanes arranged in the inner housing. As a rule, the high-pressure turbine sections are designed to be single-flow, with the result that a comparatively high thrust as a result of the steam pressure on the rotor leads in one direction. Therefore, the rotors are usually formed with thrust balance piston. By flow of the thrust balance piston at a defined location, a pressure is generated, which leads to a counter thrust, which holds the rotor substantially force-free in the axial direction.
Die hohen Temperaturen erfordern den Einsatz von Materialien, die den hohen Temperaturen und Drücken standhält. Auch nickelbasisbasierte Stähle oder hochprozentige chromige Stähle sind für den Einsatz bei hohen Temperaturen geeignet.The high temperatures require the use of materials that withstand the high temperatures and pressures. Nickel base based steels or high percentage chromium steels are also suitable for use at high temperatures.
Neben den hohen Temperaturen müssen die Komponenten einer Dampfturbine vergleichsweise korrosionsfest ausgebildet sein, da manche Komponenten mit Nassdampf beströmt werden bei gleichzeitig hoher Strömungsgeschwindigkeit des Dampfes. Solche Komponenten würden bei einer Konfrontation mit Nassdampf in Verbindung mit hoher Strömungsgeschwindigkeit zu Korrosion und Erosion führen. Dieses Problem wird derzeit dadurch behoben, dass vergleichsweise kostenintensive Maßnahmen ergriffen werden. Eine der Maßnahme wäre beispielsweise der Einsatz von hoch-chromigen Werkstoffen oder der Einsatz von Beschichtungen, die auf die Komponenten aufgetragen werden und somit eine Korrosion und Erosion vermeiden.In addition to the high temperatures, the components of a steam turbine must be made relatively resistant to corrosion, since some components are flown with wet steam at the same time high flow velocity of the steam. Such components would result in corrosion and erosion upon exposure to wet steam coupled with high flow velocity. This issue is currently addressed by taking relatively costly measures. One of the measures would be, for example, the use of high-chromium materials or the use of coatings, which are applied to the components and thus avoid corrosion and erosion.
Besonders bei Hochdruck-Teilturbinen ist der aus dem Strömungskanal ausströmende Dampf, der im Wesentlichen ein Nassdampf ist, das bedeutet, dass sich in den Dampf kleine Wasserpartikel gebildet haben, auf Komponenten in der Dampfturbine strömt, die zu einer Schädigung, wie z.B. einer Korrosion oder Erosion der Komponente führen. Es ist bekannt, durch Schutzschilde diesen Nassdampf von den Komponenten fern zu halten.Particularly in high-pressure turbine sections, the steam flowing out of the flow channel, which is essentially a wet steam This means that small amounts of water have formed in the steam, which flows to components in the steam turbine that cause damage, such as corrosion or erosion of the component. It is known to keep this wet steam away from the components by means of protective shields.
Die Erfindung hat es sich zur Aufgabe gestellt, durch Nassdampf verursachte Korrosions- und Erosionsschäden zu vermeiden.The object of the invention is to avoid corrosion and erosion damage caused by wet steam.
Die Aufgabe wird gelöst durch eine Dampfturbine umfassend einen drehbar gelagerten Rotor, ein Innengehäuse und einen zwischen dem Rotor und dem Innengehäuse angeordneten ersten Strömungskanal, wobei der Rotor einen Schubausgleichskolben aufweist, wobei die Dampfturbine eine Schubausgleichskolbendampfleitung aufweist, wobei die Schubausgleichskolbendampfleitung in einen Schubausgleichskolbenvorraum mündet, wobei die Dampfturbine eine Nassdampfleitung aufweist, die eine strömungstechnische Verbindung zwischen einem Spaltraum und einem ersten Druckraum herstellt, wobei der Spaltraum zwischen dem Rotor und dem Innengehäuse angeordnet ist.The object is achieved by a steam turbine comprising a rotatably mounted rotor, an inner housing and a first flow channel arranged between the rotor and the inner housing, the rotor having a thrust balance piston, the steam turbine having a thrust balance steam line, wherein the thrust balance steam line opens into a thrust balance piston antechamber the steam turbine has a wet steam line which produces a fluidic connection between a gap space and a first pressure space, wherein the gap space is arranged between the rotor and the inner housing.
Mit der Schubausgleichskolbendampfleitung wird Dampf in einen Schubausgleichskolbenvorraum gebracht, der in Folge des Druckes eine Kraft auf den Rotor ausübt, um einen Schub auszugleichen. Der Schubausgleichskolben ist in der Regel ein Teilstück des Rotors mit einem idealerweise speziell für den gewünschten Schubausgleich gewählten Radius an einer axialen Stelle entsprechenden Druckniveaus. Der Vorraum befindet sich vor einer radialen Mantelfläche. Die Schubausgleichskolbendampfleitung wird mit einer Dampfquelle verbunden, die einen bestimmten Dampf mit einem Druck und einer Temperatur aufweist. Dieser Dampf vermischt sich mit dem aus der Hochdruck-Teilturbine ausströmenden Dampf und gelangt zwischen dem Schubausgleichskolben und dem Innengehäuse in einen Zwischenraum zwischen dem Innengehäuse und dem Außengehäuse. An der Stelle, wo der Dampf zwischen dem Rotor und dem Innengehäuse ausströmt, wird das Außengehäuse in Bezug auf Erosion und Korrosion stark beansprucht. Erfindungsgemäß wird nun die Dampfturbine mit einer Nassdampfleitung ausgeführt. Diese Nassdampfleitung mündet in einen Spaltraum, der sich zwischen dem Innengehäuse und dem Rotor befindet. An dieser Stelle strömt der aus dem Hochdruck-Teilturbinen-Strömungskanal ausströmende Nassdampf in Richtung Schubausgleichskolben. Diese Nassdampfleitung wird mit einem ersten Druckraum strömungstechnisch verbunden, wobei in diesem ersten Druckraum ein geringerer Druck herrscht als in dem Spaltraum. Das führt dazu, dass der in diesen Spaltraum befindliche Nassdampf sozusagen nahezu komplett abgesaugt und in der Nassdampfleitung abgeführt wird. Das Vermischen des Nassdampfes mit dem Dampf im Schubausgleichskolbenvorraum wird dadurch drastisch reduziert. Ein Ausströmen eines Misch-Dampfes gebildet aus dem Nassdampf und dem Dampf im Schubausgleichskolbenvorraum ist dadurch nahezu verhindert, so dass praktisch kein Misch-Dampf zwischen dem Schubausgleichskolben und dem Innengehäuse auf das Außengehäuse strömt. Das Außengehäuse kann somit aus einem Werkstoff hergestellt werden, der eine geringere Korrosions- und Erosionsbeständigkeit aufweist. Dies wird zu einer günstigeren Variante des Außengehäuses führen.The thrust balance steam line directs steam into a thrust balance piston anvil which, as a result of the pressure, exerts a force on the rotor to compensate for thrust. The thrust balance piston is typically a portion of the rotor with a radius ideally selected for the desired thrust balance at an axial location corresponding pressure level. The vestibule is located in front of a radial lateral surface. The thrust balance steam line is connected to a source of steam having a particular vapor at a pressure and a temperature. This steam mixes with the effluent from the high-pressure turbine section steam and passes between the thrust balance piston and the inner housing in a space between the inner housing and the outer housing. At the point where the steam between the rotor and the inner casing flows out, the outer housing is heavily stressed in terms of erosion and corrosion. According to the invention, the steam turbine is now carried out with a wet steam line. This wet steam line opens into a gap, which is located between the inner housing and the rotor. At this point, the wet steam flowing out of the high-pressure turbine part flow channel flows in the direction of the thrust balance piston. This wet steam line is fluidically connected to a first pressure chamber, wherein in this first pressure chamber, a lower pressure prevails than in the gap. As a result, the wet steam present in this gap space is virtually completely sucked off and removed in the wet steam line. The mixing of the wet steam with the steam in the thrust balance piston antechamber is thereby drastically reduced. An outflow of a mixed vapor formed from the wet steam and the steam in the thrust balance piston antechamber is thereby almost prevented, so that virtually no mixing steam flows between the thrust balance piston and the inner housing to the outer housing. The outer housing can thus be made of a material having a lower corrosion and erosion resistance. This will lead to a cheaper version of the outer housing.
Vorteilhafte Weiterbildungen sind in den Unteransprüchen angegeben.Advantageous developments are specified in the subclaims.
In einer ersten vorteilhaften Weiterbildung weist die Turbine einen zweiten Strömungskanal auf, wobei die Schubausgleichskolbendampfleitung mit dem zweiten Einströmbereich oder einem anderen Druckraum strömungstechnisch verbunden ist. Somit gelangt ein Dampf, der ein überhitzter Dampf sein kann, aus dem zweiten Strömungskanal über die Schubausgleichskolbendampfleitung in den Schubausgleichskolbenvorraum.In a first advantageous development, the turbine has a second flow channel, wherein the thrust balance steam line is fluidically connected to the second inflow region or another pressure chamber. Thus, a vapor, which may be superheated steam, passes from the second flow passage via the thrust balance piston steam line to the thrust balance piston antechamber.
In einer besonderen vorteilhaften Weiterbildung ist der erste Druckraum im zweiten Strömungskanal angeordnet, wobei der erste Druckraum einen Druck aufweist, der geringer ist als der Druck im Spaltraum. Dies führt dazu, dass der in den Spaltraum gelangte Nassdampf aus der Hochdruck-Teilturbine über die Nassdampfleitung in den ersten Druckraum strömt. Somit wird der unerwünschte Nassdampf, bevor er überhaupt an das Außengehäuse gelangen könnte, abgesaugt und in den zweiten Strömungskanal abgeführt.In a particular advantageous development of the first pressure chamber is arranged in the second flow channel, wherein the first pressure chamber has a pressure which is less than the pressure in the gap space. This leads to that in the Gap was wet steam from the high-pressure turbine section via the wet steam line flows into the first pressure chamber. Thus, the unwanted wet steam, before it could ever reach the outer housing, sucked and discharged into the second flow channel.
Die Erfindung wird nun anhand eines Ausführungsbeispiels näher beschrieben. Die Komponenten mit dem gleichen Bezugszeichen weisen im Wesentlichen die gleiche Funktionsweise auf.The invention will now be described with reference to an embodiment. The components having the same reference number have substantially the same operation.
Es zeigen:
- Figur 1
- einen Querschnitt durch eine erfindungsgemäße Dampfturbine;
Figur 2- einen vergrößerter Ausschnitt im Bereich des Schubausgleichskolbens der Dampfturbine aus
Fig. 1 .
- FIG. 1
- a cross section through a steam turbine according to the invention;
- FIG. 2
- an enlarged section in the region of the thrust balance piston of the steam turbine
Fig. 1 ,
Die
Eine einheitliche Definition von Hochdruck- und Mitteldruck-Teilturbinen wird in der Fachwelt nicht verwendet.A common definition of high pressure and medium pressure turbine parts is not used in the art.
Die in
Zwischen dem Innengehäuse 9 und dem Rotor 4 im Bereich des Schubausgleichskolbens 14 ist ein Spalt 17. Durch diesen Spalt kann ein Dampf strömen, der in einen Zwischenraum 18 gelangt, der sich zwischen dem Außengehäuse 3 und dem Innengehäuse 9 befindet. Ein im Spalt 17 befindlicher Nassdampf könnte zu einer erhöhten Korrosions- und Erosionsgefahr des Außengehäuses 3 führen.Between the
Erfindungsgemäß wird nun eine Nassdampfleitung 19 in der Dampfturbine 1 angeordnet, die eine strömungstechnische Verbindung zwischen dem Spaltraum 13 und einem ersten Druckraum 20 herstellt, wobei der Spaltraum 13 zwischen dem Rotor 4 und dem Innengehäuse 9 angeordnet ist. Der erste Druckraum 20 befindet sich im zweiten Beschaufelungsbereich 7, insbesondere in einem zweiten Strömungskanal 21. Das in
Der Schubausgleichskolben 14 erstreckt sich in einer radialen Richtung 22, die im Wesentlichen senkrecht zur Rotationsachse 23 ausgebildet ist.The
Die Schubausgleichskolben-Dampfleitung 24 ist mit einer Dampfquelle 25 strömungstechnisch verbunden. Wie in
Das Innengehäuse 9 weist eine Einspeiseöffnung 27 auf, mit der die Nassdampfleitung 19 verbunden werden kann.The
Die
Claims (12)
wobei der Rotor (4) einen Schubausgleichskolben (14) aufweist,
wobei die Dampfturbine (1) eine Schubausgleichskolbenleitung (24) aufweist,
wobei die Schubausgleichskolbenleitung (24) in einen Schubausgleichskolbenvorraum (15) mündet,
dadurch gekennzeichnet, dass
die Dampfturbine (1) eine Nassdampfleitung (19) aufweist, die eine strömungstechnische Verbindung zwischen einem Spaltraum (13) und einem ersten Druckraum (20) herstellt, wobei der Spaltraum (13) zwischen dem Rotor (4) und dem Innengehäuse (9) angeordnet ist.Steam turbine (1) comprising a rotatably mounted rotor (4), an inner housing (9) and a between the rotor (4) and the inner housing (9) arranged high-pressure flow channel (6),
the rotor (4) having a thrust balance piston (14),
the steam turbine (1) having a thrust balance piston line (24),
wherein the thrust balance piston line (24) opens into a thrust balance piston antechamber (15),
characterized in that
the steam turbine (1) has a wet steam line (19) which produces a fluidic connection between a gap space (13) and a first pressure space (20), wherein the gap space (13) is arranged between the rotor (4) and the inner housing (9) is.
wobei der Schubausgleichskolben (14) zum Ausgleichen des im Betrieb auftretenden Schubs des Rotors (4) ausgebildet ist.Steam turbine (1) according to claim 1,
wherein the thrust balance piston (14) is designed to compensate for the thrust of the rotor (4) that occurs during operation.
wobei der Schubausgleichskolben (14) sich in einer radialen Richtung (22) erstreckt.Steam turbine (1) according to claim 1 or 2,
wherein the thrust balance piston (14) extends in a radial direction (22).
wobei der Schubausgleichskolbenvorraum (15) zwischen dem Schubausgleichskolben (14) und dem Innengehäuse (9) ausgebildet ist.Steam turbine (1) according to claim 3,
wherein the thrust balance piston antechamber (15) is formed between the thrust balance piston (14) and the inner housing (9).
wobei die Schubausgleichskolbenleitung (24) mit einer Dampfquelle (25) strömungstechnisch verbunden ist.Steam turbine (1) according to one of the preceding claims,
wherein the thrust balance piston line (24) is fluidly connected to a steam source (25).
wobei die Dampfquelle (25) außerhalb der Dampfturbine angeordnet ist.Steam turbine (1) according to claim 5,
wherein the steam source (25) is disposed outside of the steam turbine.
mit einem zweiten Strömungskanal (21) und einem dem zweiten Strömungskanal (21) zugeordneten Einströmbereich (26), wobei die Schubausgleichskolbenleitung (24) mit dem Einströmbereich (26) strömungstechnisch verbunden ist.Steam turbine (1) according to one of claims 1 to 4,
with a second flow channel (21) and an inlet region (26) assigned to the second flow channel (21), the thrust balance piston line (24) being fluidically connected to the inflow region (26).
wobei der zweite Strömungskanal (21) den ersten Druckraum (20) sowie eine Einspeiseöffnung (27) zum Einspeisen von Dampf in den ersten Druckraum (20) aufweist.Steam turbine (1) according to one of the preceding claims,
wherein the second flow channel (21) has the first pressure space (20) and a feed opening (27) for feeding steam into the first pressure space (20).
wobei der zweite Strömungskanal (21) mehrere in einer Strömungsrichtung hintereinander angeordnete Leit- und Laufschaufeln umfassende Schaufelstufen aufweist,
wobei der erste Druckraum (20) nach einer Schaufelstufe angeordnet ist.Steam turbine (1) according to claim 8,
wherein the second flow channel (21) has a plurality of blade and blade stages arranged in succession in a flow direction,
wherein the first pressure chamber (20) is arranged after a blade stage.
wobei der Spaltraum (13) zwischen dem Schubausgleichskolbenvorraum (15) und einem Hochdruck-Ausströmbereich (12) des Hochdruck-Strömungskanals (6) angeordnet ist.Steam turbine (1) according to one of the preceding claims,
wherein the gap space (13) is disposed between the thrust balance piston antechamber (15) and a high pressure discharge area (12) of the high pressure flow channel (6).
wobei das Innengehäuse (9) eine zum Spaltraum (13) hin geöffnete Kavität aufweist.Steam turbine (1) according to one of the preceding claims,
wherein the inner housing (9) has a cavity open towards the gap (13).
wobei der Hochdruck (6)- und zweite Strömungskanal (21) in einem gemeinsamen Innengehäuse (9) angeordnet sind.Steam turbine (1) according to one of the preceding claims,
wherein the high pressure (6) - and second flow channel (21) in a common inner housing (9) are arranged.
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP10177090A EP2431570A1 (en) | 2010-09-16 | 2010-09-16 | Steam turbine with a dummy piston and wet steam blockage |
PCT/EP2011/065909 WO2012035047A1 (en) | 2010-09-16 | 2011-09-14 | Disabling circuit in steam turbines for shutting off saturated steam |
CN201180044360.6A CN103097663B (en) | 2010-09-16 | 2011-09-14 | Steam turbine |
EP11761538.5A EP2601382B1 (en) | 2010-09-16 | 2011-09-14 | Disabling circuit in steam turbines for shutting off saturated steam |
US13/823,143 US9726041B2 (en) | 2010-09-16 | 2011-09-14 | Disabling circuit in steam turbines for shutting off saturated steam |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP10177090A EP2431570A1 (en) | 2010-09-16 | 2010-09-16 | Steam turbine with a dummy piston and wet steam blockage |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2431570A1 true EP2431570A1 (en) | 2012-03-21 |
Family
ID=43598251
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10177090A Withdrawn EP2431570A1 (en) | 2010-09-16 | 2010-09-16 | Steam turbine with a dummy piston and wet steam blockage |
EP11761538.5A Not-in-force EP2601382B1 (en) | 2010-09-16 | 2011-09-14 | Disabling circuit in steam turbines for shutting off saturated steam |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11761538.5A Not-in-force EP2601382B1 (en) | 2010-09-16 | 2011-09-14 | Disabling circuit in steam turbines for shutting off saturated steam |
Country Status (4)
Country | Link |
---|---|
US (1) | US9726041B2 (en) |
EP (2) | EP2431570A1 (en) |
CN (1) | CN103097663B (en) |
WO (1) | WO2012035047A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2565419A1 (en) * | 2011-08-30 | 2013-03-06 | Siemens Aktiengesellschaft | Flow machine cooling |
EP2565401A1 (en) * | 2011-09-05 | 2013-03-06 | Siemens Aktiengesellschaft | Method for temperature balance in a steam turbine |
JP6132737B2 (en) * | 2013-10-09 | 2017-05-24 | 株式会社東芝 | Steam turbine |
DE102016215770A1 (en) | 2016-08-23 | 2018-03-01 | Siemens Aktiengesellschaft | Outflow housing and steam turbine with discharge housing |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2326112A (en) * | 1941-11-11 | 1943-08-10 | Westinghouse Electric & Mfg Co | Turbine apparatus |
EP1035301A1 (en) * | 1999-03-08 | 2000-09-13 | Asea Brown Boveri AG | Axial thrust compensating piston for a turbine shaft |
US6695575B1 (en) * | 1999-08-27 | 2004-02-24 | Siemens Aktiengesellschaft | Turbine method for discharging leakage fluid |
EP1624155A1 (en) * | 2004-08-02 | 2006-02-08 | Siemens Aktiengesellschaft | Steam turbine and method of operating a steam turbine |
EP1806476A1 (en) * | 2006-01-05 | 2007-07-11 | Siemens Aktiengesellschaft | Turbine for a thermal power plant |
EP2154332A1 (en) * | 2008-08-14 | 2010-02-17 | Siemens Aktiengesellschaft | Reduction of the thermal loading of an external casing for a fluid flow engine |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1344193A (en) * | 1918-09-05 | 1920-06-22 | Allis Chalmers Mfg Co | Balancing device |
US2920867A (en) * | 1957-01-22 | 1960-01-12 | Westinghouse Electric Corp | Reheat turbine apparatus |
DE19700899A1 (en) * | 1997-01-14 | 1998-07-23 | Siemens Ag | Steam turbine |
-
2010
- 2010-09-16 EP EP10177090A patent/EP2431570A1/en not_active Withdrawn
-
2011
- 2011-09-14 US US13/823,143 patent/US9726041B2/en not_active Expired - Fee Related
- 2011-09-14 EP EP11761538.5A patent/EP2601382B1/en not_active Not-in-force
- 2011-09-14 WO PCT/EP2011/065909 patent/WO2012035047A1/en active Application Filing
- 2011-09-14 CN CN201180044360.6A patent/CN103097663B/en not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2326112A (en) * | 1941-11-11 | 1943-08-10 | Westinghouse Electric & Mfg Co | Turbine apparatus |
EP1035301A1 (en) * | 1999-03-08 | 2000-09-13 | Asea Brown Boveri AG | Axial thrust compensating piston for a turbine shaft |
US6695575B1 (en) * | 1999-08-27 | 2004-02-24 | Siemens Aktiengesellschaft | Turbine method for discharging leakage fluid |
EP1624155A1 (en) * | 2004-08-02 | 2006-02-08 | Siemens Aktiengesellschaft | Steam turbine and method of operating a steam turbine |
EP1806476A1 (en) * | 2006-01-05 | 2007-07-11 | Siemens Aktiengesellschaft | Turbine for a thermal power plant |
EP2154332A1 (en) * | 2008-08-14 | 2010-02-17 | Siemens Aktiengesellschaft | Reduction of the thermal loading of an external casing for a fluid flow engine |
Also Published As
Publication number | Publication date |
---|---|
EP2601382B1 (en) | 2014-08-13 |
CN103097663A (en) | 2013-05-08 |
CN103097663B (en) | 2015-08-19 |
EP2601382A1 (en) | 2013-06-12 |
US9726041B2 (en) | 2017-08-08 |
WO2012035047A1 (en) | 2012-03-22 |
US20130170956A1 (en) | 2013-07-04 |
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