EP2601382B1 - Disabling circuit in steam turbines for shutting off saturated steam - Google Patents
Disabling circuit in steam turbines for shutting off saturated steam Download PDFInfo
- Publication number
- EP2601382B1 EP2601382B1 EP11761538.5A EP11761538A EP2601382B1 EP 2601382 B1 EP2601382 B1 EP 2601382B1 EP 11761538 A EP11761538 A EP 11761538A EP 2601382 B1 EP2601382 B1 EP 2601382B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- steam
- pressure
- steam turbine
- rotor
- dummy piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/007—Preventing corrosion
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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 disposed 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 casing and a first flow channel disposed between the rotor and the inner casing, the rotor having a thrust balance piston, the steam turbine having a thrust balance steam line, the thrust balance steam line leading into a thrust balance piston antechamber opens, wherein the steam turbine has a wet steam line, which produces a fluidic connection between a gap space and a first pressure chamber, wherein the gap space between the rotor and the inner housing is arranged.
- the turbine has a second flow channel and an inflow region assigned to the second flow channel, wherein the thrust equalization piston vapor line is fluidically connected to the second inflow region or to 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 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 steam source which has a certain 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 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 the wet steam entering the gap from the high-pressure turbine section flows via the wet steam line 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 casing 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 steam flowing into the high-pressure turbine part is greater than the pressure of the steam flowing into the medium-pressure turbine section.
- 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.
- 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, between the thrust balance piston 14 and a rear wall 16 of the inner housing 9 is arranged.
- 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 vapor source 25.
- This in the inflow region 26 in the medium-pressure turbine section incoming steam is superheated steam entering 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 a 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.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
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 disposed 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
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 gemäß Anspruch 1 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. Die Turbine weist erfindungsgemäß einen zweiten Strömungskanal und einen dem zweiten Strömungskanal zugeordneten Einströmbereich 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.The object is achieved by a steam turbine according to claim 1 comprising a rotatably mounted rotor, an inner casing and a first flow channel disposed between the rotor and the inner casing, the rotor having a thrust balance piston, the steam turbine having a thrust balance steam line, the thrust balance steam line leading into a thrust balance piston antechamber opens, wherein the steam turbine has a wet steam line, which produces a fluidic connection between a gap space and a first pressure chamber, wherein the gap space between the rotor and the inner housing is arranged. According to the invention, the turbine has a second flow channel and an inflow region assigned to the second flow channel, wherein the thrust equalization piston vapor line is fluidically connected to the second inflow region or to 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.
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 steam source which has a certain 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 flows out between the rotor and the inner housing, 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 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 the wet steam entering the gap from the high-pressure turbine section flows via the wet steam line 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 (11)
- Steam turbine (1) comprising a rotatably mounted rotor (4), an inner casing (9) and a high-pressure flow duct (6) arranged between the rotor (4) and the inner casing (9), wherein the rotor (4) has a dummy piston (14),
wherein the steam turbine (1) has a dummy piston line (24),
wherein the dummy piston line (24) opens into a dummy piston prechamber (15),
wherein the steam turbine (1) has a wet steam line (19), which establishes 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 casing (9),
characterized by
a second flow duct (21) and an inflow zone (26) assigned to the second flow duct (21), wherein the dummy piston line (24) is connected fluidically to the inflow zone (26). - Steam turbine (1) according to claim 1,
wherein the dummy piston (14) is designed to compensate for the thrust of the rotor (4) which occurs during operation. - Steam turbine (1) according to claim 1 or 2
wherein the dummy piston (14) extends in a radial direction (22). - Steam turbine (1) according to claim 3,
wherein the dummy piston prechamber (15) is formed between the dummy piston (14) and the inner casing (9). - Steam turbine (1) according to one of the preceding claims,
wherein the dummy piston line (24) is connected fluidically to a steam source (25). - Steam turbine (1) according to claim 5,
wherein the steam source (25) is arranged outside the steam turbine. - Steam turbine (1) according to one of the preceding claims,
wherein the second flow duct (21) has the first pressure space (20) and a feed opening (27) for feeding steam into the first pressure space (20). - Steam turbine (1) according to claim 7,
wherein the second flow duct (21) has a plurality of blade stages arranged in series in a direction of flow and comprising guide and rotor blades,
wherein the first pressure space (20) is arranged after one blade stage. - Steam turbine (1) according to one of the preceding claims,
wherein the gap space (13) is arranged between the dummy piston prechamber (15) and a high-pressure outflow zone (12) of the high-pressure flow duct (6). - Steam turbine (1) according to one of the preceding claims,
wherein the inner casing (9) has a cavity open toward the gap space (13). - Steam turbine (1) according to one of the preceding claims,
wherein the high-pressure duct (6) and the second flow duct (21) are arranged in a common inner casing (9).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11761538.5A EP2601382B1 (en) | 2010-09-16 | 2011-09-14 | Disabling circuit in steam turbines for shutting off saturated steam |
Applications Claiming Priority (3)
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 |
EP11761538.5A EP2601382B1 (en) | 2010-09-16 | 2011-09-14 | Disabling circuit in steam turbines for shutting off saturated steam |
PCT/EP2011/065909 WO2012035047A1 (en) | 2010-09-16 | 2011-09-14 | Disabling circuit in steam turbines for shutting off saturated steam |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2601382A1 EP2601382A1 (en) | 2013-06-12 |
EP2601382B1 true EP2601382B1 (en) | 2014-08-13 |
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 Before (1)
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 |
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 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1344193A (en) * | 1918-09-05 | 1920-06-22 | Allis Chalmers Mfg Co | Balancing device |
US2326112A (en) * | 1941-11-11 | 1943-08-10 | Westinghouse Electric & Mfg Co | Turbine apparatus |
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 |
EP1035301A1 (en) * | 1999-03-08 | 2000-09-13 | Asea Brown Boveri AG | Axial thrust compensating piston for a turbine shaft |
JP4522633B2 (en) | 1999-08-27 | 2010-08-11 | シーメンス アクチエンゲゼルシヤフト | Discharge method of turbine and its 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 |
-
2010
- 2010-09-16 EP EP10177090A patent/EP2431570A1/en not_active Withdrawn
-
2011
- 2011-09-14 WO PCT/EP2011/065909 patent/WO2012035047A1/en active Application Filing
- 2011-09-14 US US13/823,143 patent/US9726041B2/en not_active Expired - Fee Related
- 2011-09-14 CN CN201180044360.6A patent/CN103097663B/en not_active Expired - Fee Related
- 2011-09-14 EP EP11761538.5A patent/EP2601382B1/en not_active Not-in-force
Also Published As
Publication number | Publication date |
---|---|
US9726041B2 (en) | 2017-08-08 |
EP2601382A1 (en) | 2013-06-12 |
WO2012035047A1 (en) | 2012-03-22 |
EP2431570A1 (en) | 2012-03-21 |
CN103097663A (en) | 2013-05-08 |
CN103097663B (en) | 2015-08-19 |
US20130170956A1 (en) | 2013-07-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1774140B1 (en) | Steam turbine, and method for the operation of a steam turbine | |
DE102010046714B4 (en) | Steam turbine with relief groove on the rotor | |
EP2601382B1 (en) | Disabling circuit in steam turbines for shutting off saturated steam | |
CH702000A2 (en) | Swirl chambers to the gap flow control. | |
DE102015111843A1 (en) | Turbine with cooled turbine vanes | |
DE102016222720A1 (en) | Sealing system for an axial flow machine and axial flow machine | |
EP3130748A1 (en) | Rotor cooling for a steam turbine | |
EP1219779B1 (en) | Turbomachine component with inspection hole, and method for inspecting and cleaning such a component | |
DE102010012583A1 (en) | Method for operating a steam turbine with a pulse rotor and steam turbine for carrying out the method | |
EP2358979B1 (en) | Axial compressor for a gas turbine having passive radial gap control | |
WO2004003346A1 (en) | Steam turbine | |
EP2675999B1 (en) | Steam turbine with dummy piston sealing arrangement for blocking saturated steam | |
EP3155226B1 (en) | Steam turbine and method for operating a steam turbine | |
EP3274561B1 (en) | Rotor blade for a gas turbine, manufacturing process and post production process | |
EP2310633B1 (en) | Reducing the thermal load of an external housing for a turbo-machine | |
EP2877699B1 (en) | Low pressure turbine | |
EP3293356B1 (en) | Blade for turbomachine comprising a movably supported impingement baffle and corresponding assembly method | |
EP3587738A2 (en) | Seal arrangement for turbomachine engine components | |
WO2008025583A1 (en) | Method for cooling turbine blades of a blade ring and turbine blade segment for a turbine blade ring having at least two aerodynamically profiled blades | |
EP2211017A1 (en) | Rotor with cavity for a turbo engine | |
EP1561909A1 (en) | Diffuser, turbomachine and method of recovery of pressure in a turbomachine. | |
EP2824279B1 (en) | Turbomachine with sealing arrangement | |
EP1895094B1 (en) | Swirl cooled rotor welding seam | |
EP1674670B1 (en) | Turbine and method for cooling an external casing of a turbine | |
DE102016203731A1 (en) | steam turbine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20130305 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
DAX | Request for extension of the european patent (deleted) | ||
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20140304 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 682394 Country of ref document: AT Kind code of ref document: T Effective date: 20140815 Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502011004062 Country of ref document: DE Effective date: 20140925 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: NV Representative=s name: SIEMENS SCHWEIZ AG, CH |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: VDEP Effective date: 20140813 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141113 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141113 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141114 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141215 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141213 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502011004062 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140930 |
|
26N | No opposition filed |
Effective date: 20150515 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140914 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20150914 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20110914 Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140914 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150914 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 6 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 7 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PCOW Free format text: NEW ADDRESS: WERNER-VON-SIEMENS-STRASSE 1, 80333 MUENCHEN (DE) |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20170927 Year of fee payment: 7 Ref country code: CZ Payment date: 20170913 Year of fee payment: 7 Ref country code: FR Payment date: 20170918 Year of fee payment: 7 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 682394 Country of ref document: AT Kind code of ref document: T Effective date: 20160914 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160914 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: CH Payment date: 20171207 Year of fee payment: 7 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20180110 Year of fee payment: 7 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140813 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502011004062 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180914 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190402 Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180914 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180930 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180930 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180930 |