EP2611995B1 - Système de turbine à vapeur à alimentation en vapeur variable - Google Patents

Système de turbine à vapeur à alimentation en vapeur variable Download PDF

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Publication number
EP2611995B1
EP2611995B1 EP11771088.9A EP11771088A EP2611995B1 EP 2611995 B1 EP2611995 B1 EP 2611995B1 EP 11771088 A EP11771088 A EP 11771088A EP 2611995 B1 EP2611995 B1 EP 2611995B1
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EP
European Patent Office
Prior art keywords
steam
pressure
feed
inlet
turbine
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
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EP11771088.9A
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German (de)
English (en)
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EP2611995A1 (fr
Inventor
Norbert Pieper
Michael Wechsung
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Siemens AG
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Siemens AG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/101—Regulating means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/106—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
    • F01K23/108—Regulating means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/18—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbine being of multiple-inlet-pressure type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/18—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbine being of multiple-inlet-pressure type
    • F01K7/20—Control means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
    • F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines

Definitions

  • the invention relates to a steam turbine plant with variable steam feed.
  • Steam turbine plants are usually dimensioned from an economic point of view.
  • steam turbine plants which are used in electrical energy production, is worked to achieve maximum efficiency with very large power units.
  • the efficiency should also be constant over the largest possible power range.
  • it is known to feed a Zudampf, in particular a low-pressure Zudampf, in a medium or low-pressure steam turbine. If the steam turbine is driven, for example, in part-load operation, the Zudampf must be throttled at the feed point, if this is available at constant pressure.
  • WO-A1-2011 / 030285 is a steam turbine plant known with a high pressure, medium pressure and low pressure turbine.
  • the medium-pressure and low-pressure turbines each have a diverting station to be able to vary the amount of steam above the respective turbines.
  • From the DE 102 27 709 A1 is a steam turbine plant with one between high-pressure turbine and medium-pressure or low-pressure turbine arranged reheater known.
  • a check valve is arranged between high-pressure turbine outlet and reheater inlet.
  • a safe and fast startup from the cold state or a load shutdown is made possible by the fact that further provided an overflow, which, bridging the reheater connects the high-pressure exhaust steam line of the high-pressure turbine with the medium-pressure turbine.
  • From the JP 60 166 704 A a steam turbine with a condenser is known in which a circuit is provided to leave the condenser after the shutdown of the steam turbine at low pressure.
  • a control unit is provided, the valves accordingly sets and closes.
  • the invention has for its object to provide a steam turbine plant, in which the above problems are overcome and in particular throttle losses are largely avoided. It is another object of the invention to propose a method for operating the steam turbine plant, in which throttle losses are largely avoided.
  • the Zudampfsammel Arthur is introduced at a Zudampfeinleitstelle the Zudampf effetsabitess in the exhaust steam of the steam turbine and a feed steam device is provided on the steam turbine with a changeover, with the upstream of the Zudampfeinleitstelle the feed steam device is connected to the Zudampf niesabêt and which is switchable such that when the Abdampf réelle is less than a target pressure in the Zudampf niesabterrorism, the Zudampf endeavorsabterrorism is vapor-connected to the feed steam device and is interrupted between the changeover valve and the Zudampfeinleitstelle, and otherwise the feed steam device from the Zudampf effetsabexcellent is disconnected.
  • the changeover valve is switched in the Zudampf founded founded upon by a feed steam via the feed steam device. If the exhaust steam pressure of the steam turbine is equal to or greater than the target value, the feed steam device is separated from the steam exhaust line section and the steam turbine receives no feed steam via the feed steam device.
  • the Zudampf can be introduced via the feed steam device upstream and relaxed in the steam turbine means of Umschaltarmatur.
  • the feed steam device preferably has a plurality of steam feed points at different stages of the steam turbine and the feed steam device can be controlled such that the feed steam is fed in only at that steam feed point at which the pressure at the introduction position within the steam turbine is higher than that of the feed steam itself However, the pressure difference is minimal.
  • the feed steam is thus fed into the steam turbine such that any necessary throttling of the feed steam is dispensable, whereby the steam turbine plant according to the invention is free from unnecessary throttling losses.
  • the feed steam device is preferably controlled such that, starting from the Dampfeinspeisestelle which is formed on a steam side arranged stage of the steam turbine, the feed steam device controls that Dampfeinspeisestelle formed at an adjacent, upstream stage of the steam turbine.
  • the feed steam device is thus formed in this embodiment, to redirect at load reduction of the medium-pressure steam turbine from the controlled at one stage of the medium-pressure steam turbine steam feed to an adjacent, upstream steam feed.
  • the feed steam device is controlled with load increase of the steam turbine such that, starting from a steam feed, which is formed at an upstream stage of the steam turbine, the feed steam device that steam feed point controls, which is formed on an adjacent, steam side arranged stage of the steam turbine.
  • a medium or low pressure steam turbine is preferably provided as a steam consumer of the steam turbine plant.
  • the feed steam device is designed to control the increase in load of the medium-pressure steam turbine from the steam feed point controlled at one stage of the medium-pressure steam turbine to an adjacent, steam feed point arranged downstream.
  • the opening degree characteristic of the switching valve for connecting and disconnecting the feed steam device and / or the opening degree characteristic for connecting and disconnecting the steam pipe section are preferably linear, progressive or degressive.
  • a method for operating the steam turbine plant preferably has the steps of: providing the steam turbine plant; Setting a target pressure for the steam manifold; Switching the changeover valve so that when the exhaust pressure is lower than the target pressure in the Zudampf niesabites, the Zudampf effetsabites is vapor-connected to the feed steam device and is interrupted between the changeover valve and the Zudampfeinleitstelle; or switching the changeover valve so that when the exhaust steam pressure is equal to or higher than the target pressure in the Zudampf niesabterrorism, the feed steam device is separated from the changeover valve and is conveyed to the Zudampfeinleitstelle Zudampf directly from the Zudampf effet effet.
  • the feed steam device preferably has a plurality of steam feed points at different stages of the steam turbine and the feed steam device is controlled such that the feed steam is fed only at the steam feed point at which the pressure difference between the feed position within the steam turbine and the feed steam is minimal is.
  • the feed steam device is preferably controlled such that, starting from the Dampfeinspeisestelle which is formed on a steam side arranged stage of the steam turbine, the feed steam device controls that Dampfeinspeisestelle formed at an adjacent, upstream stage of the steam turbine.
  • the feed steam device When load of the steam turbine, the feed steam device is preferably controlled such that, starting from a steam feed, which is formed at an upstream stage of the steam turbine, the feed steam device controls that steam feed, which is formed on an adjacent, steam side arranged stage of the steam turbine.
  • a steam turbine plant 1 is shown, which is coupled via a waste heat boiler 2 with a gas turbine plant 3.
  • the waste heat boiler 2 comprises a high pressure steam system 4 with a live steam manifold 14, a medium pressure steam system 5 with a medium pressure steam manifold 15, a low pressure steam system 6 with a low pressure steam manifold 16 and a plurality of heat exchangers 7.
  • the heat energy of the hot exhaust gases of the gas turbine plant 3 is discharged by means of the heat exchanger 7 to a respective associated boiler system 8, 9 and 10 for generating steam.
  • the steam generated in the boiler systems 8, 9 and 10 is used to operate a high pressure steam turbine 11, a medium pressure steam turbine 12 and a low pressure steam turbine 13.
  • the high-pressure steam turbine 11 and the medium-pressure steam turbine 12 are each coupled by means of one of the steam manifolds 14 and 15 with the respectively corresponding steam system 4 and 5 respectively.
  • the medium-pressure Zudampfsammeltechnisch 15 further includes a reheater 20, by means of which a medium-pressure steam to increase the efficiency of the steam turbine plant 1 in the waste heat boiler 2 is overheated.
  • the medium-pressure steam is composed of the medium-pressure Zudampf generated in the boiler system 9 and the exhaust steam of the high-pressure steam turbine 11. From the reheater 20, the superheated medium-pressure steam flows via the medium-pressure steam manifold 22 to the medium-pressure steam turbine 12th
  • the low-pressure Zudampf flows from the boiler system 10 to a changeover valve 17.
  • the pressure of Zudampfs in the low-pressure Zudampfsammeltechnisch 16 is presently 4.2 bar.
  • the pressure of the low-pressure Zudampfs is increased such that condensation of sulfurous acid on the heat transfer surfaces of the heat exchanger 7 and thus corroding the heat exchanger surfaces is prevented. This results in the low-pressure steam manifold 16, a pressure of, for example, 8 bar.
  • the low-pressure steam collecting line 16 also has a low-pressure Zudampf niethylcholine 19, on which a Zudampfeinleitstelle 21 is formed. Via the Zudampfeinleitstelle 21 of the low-pressure Zudampf is fed via the low-pressure Zudampf effetsabites 19 with the exhaust steam of the medium-pressure turbine 12.
  • the reversing valve 17 is associated with a control device (not shown) which is set to switch the change-over valve 17 in such a way when the exhaust pressure of the medium-pressure steam turbine 12 falls below a predetermined desired value, for example 4 bar, caused in particular by a partial load operation of the medium-pressure steam turbine 12 in that the exhaust steam flows via the changeover valve 17 to a feed steam device 18. If, for example, the operating state of the medium-pressure steam turbine 12 drops from a full-load operation to a partial-load operation of 60% of the full load, the exhaust-steam pressure also drops accordingly, ie the exhaust-steam pressure drops to 60% of the exhaust-steam pressure at full load.
  • a control device not shown
  • the desired value is undershot and the change-over valve 17 is switched, whereby the spent steam flows to the feed steam device 18, via which it flows as feed steam into the medium-pressure turbine 12.
  • the Zudampf from the pressure level in the low-pressure Zudampfsammeltechnisch 16 is relaxed to the pressure level at the Zudampfeinleitstelle 21 in the medium-pressure turbine 12 and thus energetically utilized.
  • the feed steam device 18 has a plurality of steam feed points (not shown), of which only a maximum of one is activated. That is, the steam is always supplied only at a Dampfeinspeisestelle. In this case, that steam feed point is controlled, at which the pressure of the steam turbine process steam is approximately equal to the pressure of the feed steam. This allows almost unthrottled feeding the feed steam, whereby an additional throttle loss is avoided by throttling. Due to flow losses, the Zudampf after passing the changeover valve 17 at the Dampfeinspeisestelle a slightly lower pressure than in the low pressure Zudampfsammeltechnisch 16, for example, 4 bar.
  • the changeover valve 17 is switched such that the exhaust steam flow flows via the low-pressure Zudampf Obersabites 19 to the low-pressure steam turbine 13.
  • the low-pressure Zudampf nieitstelle 21 of the exhaust steam of the medium-pressure turbine 12 which was previously relaxed to 4 bar
  • the steam of the low pressure Zudampfsammeltechnisch 16 which in this case also has a pressure of 4 bar together and to the low-pressure turbine thirteenth ,

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Turbines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Claims (9)

  1. Installation (1) de turbine à vapeur comprenant une turbine (12) à vapeur de moyenne pression, à laquelle est couplé un conduit (15) collecteur de vapeur d'apport de moyenne pression et comprenant un autre conduit (16) collecteur de vapeur d'apport, ayant un tronçon (19) de conduit de vapeur d'apport, pour l'alimentation de la turbine (12) à vapeur de moyenne pression ou d'une turbine (13) à vapeur de pression basse,
    caractérisée en ce que le conduit (16) collecteur de vapeur d'apport est introduit, en un point (21) d'introduction de vapeur d'apport du tronçon (19) de conduit de vapeur d'apport, dans le courant de vapeur d'échappement de la turbine (12) à vapeur de moyenne pression et il est prévu un dispositif (18) de vapeur d'injection, ayant au moins un point d'injection de vapeur, constitué sur un étage disposé du côté de la vapeur d'échappement de la turbine à vapeur de moyenne pression et ayant un robinet (17) de commutation, par lequel, en amont du point (21) d'injection de vapeur d'apport, le dispositif (18) de vapeur d'injection est raccordé au tronçon (19) de conduit de vapeur d'apport et qui peut être commuté, de manière à ce que, si la pression de la vapeur d'échappement est inférieure à une pression de consigne dans le tronçon (19) de conduit de vapeur d'apport, le tronçon (19) de conduit de vapeur d'apport communique, de manière à conduire de la vapeur, avec le dispositif (18) de vapeur d'injection et est interrompu entre le robinet (17) de commutation et le point (21) d'injection de vapeur d'apport, tandis que sinon, le dispositif (18) de vapeur d'injection est séparé du tronçon (19) de conduit de vapeur d'apport.
  2. Installation (1) de turbine à vapeur suivant la revendication 1,
    dans laquelle le dispositif (18) de vapeur d'injection a une pluralité de points d'injection de vapeur à des étages différents de la turbine (12) à vapeur de moyenne pression et le dispositif (18) de vapeur d'injection peut être commandé, de manière à ce que l'injection de la vapeur d'injection ne s'effectue qu'aux points d'injection de vapeur où la différence de pression, entre la pression en la position d'injection au sein de la turbine (12) à vapeur de moyenne pression et la vapeur d'injection soi-même, est minimum.
  3. Installation (1) suivant la revendication 2,
    dans laquelle le dispositif (18) de vapeur d'injection est constitué de manière à passer, s'il se produit une diminution de charge de la turbine (12) à vapeur de moyenne pression, d'un point d'injection de vapeur, commandé sur un étage de la turbine (12) à vapeur de moyenne pression, à un point d'injection de vapeur voisin en amont.
  4. Installation (1) suivant la revendication 2 ou 3, dans laquelle le dispositif (18) de vapeur d'injection est constitué de manière à passer, s'il y a une augmentation de charge de la turbine (12) à vapeur de moyenne pression, d'un point d'injection de vapeur, commandé sur un étage de la turbine (12) à vapeur de moyenne pression, à un point d'injection de vapeur voisin en aval.
  5. Installation (1) suivant l'une des revendications 1 à 4,
    dans laquelle la courbe caractéristique de degré d'ouverture du robinet (17) de commutation, pour la liaison et la séparation du dispositif (18) à vapeur d'injection et/ou la courbe caractéristique du degré d'ouverture, pour la liaison et la séparation du tronçon (19) de conduit de vapeur d'apport, sont linéaires, croissante ou décroissante.
  6. Procédé pour faire fonctionner une installation (1) de turbine à vapeur suivant l'une des revendications 1 à 5, comprenant les stades :
    - on se procure l'installation (1) de turbine à vapeur suivant l'une des revendications 1 à 5 ;
    - on fixe une pression de consigne pour le conduit (16) collecteur de vapeur d'apport ;
    - on commute le robinet (17) de commutation, de manière à ce que, si la pression de la vapeur d'apport est plus basse que la pression de consigne dans le tronçon (19) de conduit de vapeur d'apport, le tronçon (19) de conduit de vapeur d'apport communique, d'une manière à conduire de la vapeur, avec le dispositif (18) d'injection de vapeur et soit interrompu entre le robinet (17) de commutation et le point (21) d'injection de vapeur d'apport ; ou
    - on commute le robinet (17) de commutation, de manière à ce que, si la pression de la vapeur d'échappement est supérieure ou égale à la pression de consigne dans le tronçon (19) de conduit de vapeur d'apport, le dispositif (18) de vapeur d'injection soit séparé du robinet (17) de commutation et, au point (21) d'injection de vapeur d'apport, de la vapeur d'apport soit transportée directement du tronçon (19) de conduit de vapeur d'apport.
  7. Procédé suivant la revendication 6,
    dans lequel le dispositif (18) de vapeur d'injection a une pluralité de points d'injection de vapeur à des étages différents de la turbine (12) à vapeur et on commande le dispositif (18) de vapeur d'injection de manière à ce que l'injection de la vapeur d'injection ne s'effectue qu'aux points d'injection de vapeur où la différence de pression, entre la position d'injection au sein de la turbine à vapeur et la vapeur d'injection, est minimum.
  8. Procédé suivant la revendication 6 ou 7,
    dans lequel, si la charge de la turbine (12) à vapeur de moyenne pression diminue, on passe, du point d'injection de vapeur commandé sur un étage de la turbine (12) à vapeur de moyenne pression, à un point d'injection de vapeur voisin en amont.
  9. Procédé suivant l'une des revendications 6 à 8,
    dans lequel, si la charge de la turbine (12) à vapeur augmente, on passe, d'un point d'injection de vapeur commandé sur un étage de la turbine (12) à vapeur de moyenne pression, à un point d'injection de vapeur voisin en aval.
EP11771088.9A 2010-10-29 2011-10-12 Système de turbine à vapeur à alimentation en vapeur variable Not-in-force EP2611995B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11771088.9A EP2611995B1 (fr) 2010-10-29 2011-10-12 Système de turbine à vapeur à alimentation en vapeur variable

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP10189417A EP2447484A1 (fr) 2010-10-29 2010-10-29 Installation de turbine à vapeur dotée d'une alimentation en vapeur variable
PCT/EP2011/067811 WO2012055703A1 (fr) 2010-10-29 2011-10-12 Système de turbine à vapeur à alimentation en vapeur variable
EP11771088.9A EP2611995B1 (fr) 2010-10-29 2011-10-12 Système de turbine à vapeur à alimentation en vapeur variable

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EP2611995A1 EP2611995A1 (fr) 2013-07-10
EP2611995B1 true EP2611995B1 (fr) 2017-04-26

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EP10189417A Withdrawn EP2447484A1 (fr) 2010-10-29 2010-10-29 Installation de turbine à vapeur dotée d'une alimentation en vapeur variable
EP11771088.9A Not-in-force EP2611995B1 (fr) 2010-10-29 2011-10-12 Système de turbine à vapeur à alimentation en vapeur variable

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EP10189417A Withdrawn EP2447484A1 (fr) 2010-10-29 2010-10-29 Installation de turbine à vapeur dotée d'une alimentation en vapeur variable

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US (1) US9267394B2 (fr)
EP (2) EP2447484A1 (fr)
CN (1) CN103201464B (fr)
PL (1) PL2611995T3 (fr)
WO (1) WO2012055703A1 (fr)

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EP2808501A1 (fr) * 2013-05-27 2014-12-03 Siemens Aktiengesellschaft Procédé destiné au fonctionnement d'une centrale électrique à cycle combiné
WO2015068088A1 (fr) * 2013-11-07 2015-05-14 Sasol Technology Proprietary Limited Procédé et installation pour la cogénération de chaleur et d'énergie
AP2016009201A0 (en) * 2013-11-07 2016-05-31 Sasol Tech (Proprietary) Ltd Method and plant for co-generation of heat and power
AP2016009199A0 (en) * 2013-11-07 2016-05-31 Sasol Tech Pty Ltd Method and plant for co-generation of heat and power
EP2930320A1 (fr) * 2014-04-07 2015-10-14 Siemens Aktiengesellschaft Procédé de fonctionnement d'une turbine à vapeur

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PL2611995T3 (pl) 2017-09-29
US20130205749A1 (en) 2013-08-15
CN103201464A (zh) 2013-07-10
WO2012055703A1 (fr) 2012-05-03
US9267394B2 (en) 2016-02-23
CN103201464B (zh) 2016-02-03
EP2447484A1 (fr) 2012-05-02
EP2611995A1 (fr) 2013-07-10

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