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EP1320665B1 - Procede pour l'exploitation d'une installation de turbines a vapeur et a gaz et installation correspondante - Google Patents

Procede pour l'exploitation d'une installation de turbines a vapeur et a gaz et installation correspondante Download PDF

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Publication number
EP1320665B1
EP1320665B1 EP01978376A EP01978376A EP1320665B1 EP 1320665 B1 EP1320665 B1 EP 1320665B1 EP 01978376 A EP01978376 A EP 01978376A EP 01978376 A EP01978376 A EP 01978376A EP 1320665 B1 EP1320665 B1 EP 1320665B1
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EP
European Patent Office
Prior art keywords
pressure
steam
gas
condensate
water
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP01978376A
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German (de)
English (en)
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EP1320665A1 (fr
Inventor
Erich Schmid
Werner Schwarzott
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to EP01978376A priority Critical patent/EP1320665B1/fr
Publication of EP1320665A1 publication Critical patent/EP1320665A1/fr
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Publication of EP1320665B1 publication Critical patent/EP1320665B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01K23/106—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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F25/00—Flow mixers; Mixers for falling materials, e.g. solid particles
    • B01F25/30—Injector mixers
    • B01F25/31—Injector mixers in conduits or tubes through which the main component flows
    • B01F25/313—Injector mixers in conduits or tubes through which the main component flows wherein additional components are introduced in the centre of the conduit
    • B01F25/3132—Injector mixers in conduits or tubes through which the main component flows wherein additional components are introduced in the centre of the conduit by using two or more injector devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F23/00—Mixing according to the phases to be mixed, e.g. dispersing or emulsifying
    • B01F23/40—Mixing liquids with liquids; Emulsifying
    • B01F23/45—Mixing liquids with liquids; Emulsifying using flow mixing
    • B01F23/451—Mixing liquids with liquids; Emulsifying using flow mixing by injecting one liquid into another
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F23/00—Mixing according to the phases to be mixed, e.g. dispersing or emulsifying
    • B01F23/40—Mixing liquids with liquids; Emulsifying
    • B01F23/49—Mixing systems, i.e. flow charts or diagrams
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F35/00—Accessories for mixers; Auxiliary operations or auxiliary devices; Parts or details of general application
    • B01F35/71—Feed mechanisms
    • B01F35/717—Feed mechanisms characterised by the means for feeding the components to the mixer
    • B01F35/71805—Feed mechanisms characterised by the means for feeding the components to the mixer using valves, gates, orifices or openings

Definitions

  • the invention relates to a method of operation a gas and steam turbine plant, in which the one from both with gas as well as oil operable gas turbine exiting Flue gas is passed through a heat recovery steam generator, its heating surfaces in the water-steam cycle of a Number of pressure stages having steam turbine connected are, wherein in the heat recovery steam generator preheated condensate as compared to this under high pressure feed water heated and fed as steam to the steam turbine becomes.
  • a gas and steam turbine plant In a gas and steam turbine plant is in the relaxed Working fluid or flue gas contained in the gas turbine Heat for generating steam for in a water-steam cycle switched steam turbine used.
  • the heat transfer takes place in one of the gas turbine downstream Heat recovery steam generator or boiler, in which heating surfaces in Form of pipes or tube bundles are arranged. These in turn are connected in the water-steam cycle of the steam turbine.
  • the water-steam cycle usually includes several, for example two or three, pressure stages, in each pressure stage as heating surfaces, a preheater and an evaporator and a superheater are provided.
  • a Such gas and steam turbine plant is, for example EP 0 523 467 B1.
  • the total amount of water carried in the water-steam cycle is thereby dimensioned such that the leaving the heat recovery steam generator Flue gas due to heat transfer to a temperature is cooled from about 70 ° C to 100 ° C.
  • the hot flue gas exposed heating surfaces and provided for a water-steam separation pressure drums are designed for full load or nominal operation, at which achieves plant efficiency of currently around 55% to 60% becomes.
  • the temperatures of the individual heating surfaces guided and under different pressure Feed water as close as possible to the temperature profile of the along the heat recovery steam generator due to the heat exchange cooling flue gas.
  • the goal here is the temperature difference between the guided over the individual heating surfaces Feedwater and the flue gas in each area of the To keep heat recovery steam generator as low as possible.
  • the highest possible proportion of the amount of heat contained in the flue gas implement is in addition in the heat recovery steam generator a condensate preheater for heating condensed water provided from the steam turbine.
  • the gas turbine of such a gas and steam turbine plant can be designed for operation with different fuels be. Is the gas turbine designed for heating oil and natural gas, so is fuel oil as fuel for the gas turbine only for one short operating time, for example, for 100 to 500h / a, as so-called backup provided for natural gas.
  • the gas and Steam turbine plant usually urgent for natural gas operation the gas turbine designed and optimized. In order to in fuel oil operation, especially when changing from gas operation on the oil operation, a sufficiently high inlet temperature of the condensate flowing into the heat recovery steam generator can ensure the necessary heat to different Be removed from the heat recovery steam generator itself.
  • an effective degassing of the condensate to ensure the condensate temperature in the feedwater tank usually in a temperature range between 130 ° C and 160 ° C held.
  • This is usually a preheat condensate over one with low pressure steam or Provided hot water from an economizer-fed preheater, so that the warm-up period of the condensate in the feedwater tank kept as small as possible.
  • It is in particular in two- or three-pressure systems a hot water extraction from the high-pressure economizer required to heat enough to provide.
  • Three-pressure systems or circuits have the considerable disadvantage that an external, additional condensate preheater needed which is responsible for the high pressures and high temperatures or high temperature differences must be designed. These Method is therefore already due to the considerable costs and the additional space required for the condensate preheater extremely undesirable.
  • the invention has for its object to provide a method for Operating a gas and steam turbine of the above-mentioned Specify type, the same at low equipment and operating expenses in more effective and in terms of plant efficiency favorable way a change of Gas operation on oil operation of the gas turbine under cover of a wide temperature range of the inlet temperature of in Ensures the heat recovery steam generator inflowing condensate. Furthermore, one for carrying out the method particularly suitable gas and steam turbine plant indicated become.
  • the object is achieved according to the invention by the features of claim 1.
  • the invention is based on the consideration that on a additional heat exchanger, which is the water-steam cycle withdrawn heated feed water or hot water before its pressure reduction to the temperature level of the condensate system should cool down, can be waived, if by injecting the hot water into the cold condensate one targeted evaporation of hot water and a subsequent Kondensaticn the forming water-steam mixture takes place.
  • a additional heat exchanger which is the water-steam cycle withdrawn heated feed water or hot water before its pressure reduction to the temperature level of the condensate system should cool down
  • the heated feed water or hot water is expediently in a two-printing system, i. H. in a two-pressure system from a high-pressure drum and a three-pressure system or in a three-pressure system from the high-pressure drum and / or from a medium pressure drum as Feedwater partial flow taken.
  • a two-printing system i. H. in a two-pressure system from a high-pressure drum and a three-pressure system or in a three-pressure system from the high-pressure drum and / or from a medium pressure drum as Feedwater partial flow taken.
  • the removal the partial flow also at the outlet of the high-pressure Econo-mizers or the medium-pressure economizer done.
  • the pressure of the low-pressure system be raised to heat contained in the flue gas the low-pressure system downstream of this flue gas side Move condensate preheater out.
  • Essential here is that the water-steam cycle at a suitable place removed heated feed water in the form of a feedwater partial stream without prior warm-up, i. without heat exchange in an additional heat exchanger the cold condensate is mixed.
  • the plant comprises a mixing device, over the cold condensate one as heating surface in the Heat recovery steam generator arranged arranged condensate preheater is.
  • a mixing device over which the Condensate flows, at least one spray head is arranged, via a hot water pipe from the water-steam cycle withdrawn heated feed water or hot water can be fed.
  • Hot water mixer of the mixing device When the boiling conditions in the area of the spray nozzles are exceeded Part of the hot water is evaporated and thus the resulting mixture finely divided and the remaining Hot water cooled by evaporation. Through the injection and the very intimate mixing with the surrounding cold Condensate will be the upcoming small steam bubbles again condenses and together with the hot water to a mixing temperature brought under the pressure prevailing at this pressure Boiling temperature is. Depending on the necessary amount of hot water and the temperature are a corresponding number provided by spray heads, which then in a corresponding extended pipe section of a piping executed Hot water mixer of the mixing device are arranged.
  • each spray head is the by discharging the hot water as a result of its evaporation formed steam on especially many small openings of the respective spray head distributed within the mixing device lie below the condensate level. Thereby Only small steam bubbles enter through the condensate formed water bath.
  • the advantages achieved by the invention are in particular in that one required in oil operation of the gas turbine and increased compared to gas operation of the gas turbine Water inlet temperature in the heat recovery steam generator, too without additional heat exchanger or external condensate preheater by heat-exchanger-free spraying of high Pressurized feed water into the cold condensate with extra simple means is adjustable. It can by suitable embodiment of within a designated Mixing device arranged spray heads one below the Boiling temperature of the preheated or preheated condensate lying mixed temperature of the cold condensate In oil operation mixed partial flow on particularly simple and effective way. In addition, because of the recycled feed water throughput in the condensate preheater increases accordingly, can on previously required Kondensatum stiilzpumpen be waived. In particular, is without Circuit modification covering a wide temperature range the steam generator or boiler inlet temperature possible.
  • the gas and steam turbine plant 1 comprises a gas turbine plant 1a and a steam turbine plant 1b.
  • the gas turbine plant 1a comprises a gas turbine 2 with coupled Air compressor 4 and one of the gas turbine 2 upstream Combustion chamber 6, to a fresh air line 8 of the Air compressor 4 is connected.
  • In the combustion chamber. 6 opens a fuel line 10, via the combustion chamber. 6 optionally gas or oil as fuel B can be fed. This is under supply of compressed air L to the working medium or Fuel gas burned for the gas turbine 2.
  • the gas turbine 2 and the air compressor 4 and a generator 12 sit on one common turbine shaft 14.
  • the steam turbine installation 1 b comprises a steam turbine 20 coupled generator 22 and in a water-steam cycle 24 a steam turbine 20 downstream capacitor 26 and a heat recovery steam generator 30.
  • the steam turbine 20 has a first pressure stage or a high pressure part 20a and a second compression stage or a medium-pressure member 20b as well a third pressure stage or a low pressure part 20c on, via a common turbine shaft 32, the generator 22 drive.
  • Exhaust pipe 34 For supplying relaxed in the gas turbine 2 working fluid or flue gas AM in the heat recovery steam generator 30 is a Exhaust pipe 34 to an input 30 a of the heat recovery steam generator 30 connected. That is along the heat recovery steam generator 30 due to indirect heat exchange with the water-steam cycle 24 guided condensate K and feed water S cooling flue gas AM from the gas turbine 2 leaves the heat recovery steam generator 30 via its output 30b in the direction of a fireplace, not shown.
  • the heat recovery steam generator 30 comprises as heating surfaces Condensate preheater 36, the input side via a condensate line 38, in which a condensate pump 40 is connected, is fed with condensate K from the condenser 26.
  • Condensate preheater 36 is the output side to the suction side of a Feedwater pump 42 out.
  • a mixing device 44 with a tubular hot water mixer 46 switched.
  • the feedwater pump 42 is a high-pressure feed pump with Medium pressure taken trained. It brings the condensate K to one for a high-pressure part 20 a of the steam turbine 20 associated high-pressure stage 50 of the water-steam cycle 24th suitable pressure level of about 120 bar to 150 bar. About the Medium pressure is the condensate K by means of the feedwater pump 42 on a for a the medium-pressure part 20 b of Steam turbine 20 associated medium-pressure stage 70 suitable Pressure level from about 40 bar to 60 bar.
  • the feed water S is also partially under medium pressure via a check valve 71 and one of these downstream Valve 72 a feedwater or medium pressure economizer 73 supplied. This is the output side via a valve 74 connected to a medium-pressure drum 75. Analogous is as part of the low pressure part 20c of the steam turbine 20 associated low pressure stage 90 of the water-steam cycle 24 of the condensate preheater 36 on the output side via a Valve 91 is connected to a low-pressure drum 92.
  • the medium-pressure drum 75 is connected to a heat recovery steam generator 30 arranged medium-pressure evaporator 76 for the formation a water-steam circulation 77 connected.
  • Steam side is on the intermediate-pressure drum 75 is connected to a reheater 78, the output side (hot ZÜ) to an input 79th the medium-pressure part 20b is guided and in the input side (cold ZÜ) one with an outlet 80 of the high-pressure part 20a of the steam turbine 20 connected exhaust steam line 81 out is.
  • a steam line 95th connected to an input 96 of the low-pressure part 20c.
  • An output 99 of the low-pressure part 20c is via a steam line 100 connected to the capacitor 26.
  • the gas turbine 2 of the combined cycle power plant 1 is both operable with natural gas as well as fuel oil as fuel B
  • this has the heat recovery steam generator 30 supplied working fluids or flue gas AM a comparatively high purity, wherein the water-steam cycle 24 and the system components to this operating state designed and in terms of efficiency is optimized.
  • a partial flow t S heated by means of a valve 102 with upstream check valve 103 is supplied to the mixing device 44, 46 via a partial flow or hot water line 101 and into the interior 104 via a spray head arrangement 105 Condensate K mixed.
  • the partial flow ts of heated feed water S ' is taken off via a valve 106, preferably the high-pressure drum 54 on the water side.
  • the heated feed water S 'as an adjustable partial flow tS can also be removed via a valve 107 to the first high-pressure economizer 51 or via a valve 108 to the second high-pressure economizer 52 on the output side.
  • three-pressure system may alternatively or additionally as an adjustable partial flow tS also the medium-pressure economizer 73 on the output side via a valve 109 or the medium-pressure drum 75 water side via a valve 110th heated feed water S 'are removed.
  • the temperature is TS of the partial flow tS when it is removed as heated food water S 'from the high-pressure drum 54, for example, 320 ° C.
  • FIG. 2 shows a preferred embodiment of the mixing device 44 and the hot water mixer 46.
  • This has a the condensate line 38 connected to the inlet opening 111th for feeding the cold condensate K into the mixing device 44 and an outlet opening 112 through which the mixing device 44 connected to the condensate preheater 36 on the input side is.
  • the tubular heating water mixer 46 of the mixing device 44 is thus turned on in the condensate line 38.
  • Embodiment three spray heads 105 are in Embodiment three spray heads 105 arranged. Depending on necessary amount of heating water and the temperature can more or fewer such spray heads 105 within the hot water mixer 46 may be provided.
  • the respective spray head 105 via a mounting flange 113 with Vorsch doneende 114 through a flange 115 into the interior 104 of the hot water mixer 46 out and in the respective desired position held.
  • the spray head 105 is self-opening and points to a through a valve seat 116 and a valve plug 117 formed valve.
  • the valve cone 117 is due to the spring force of a Spring pack 118 sealing in the closed position of the valve guided against the valve seat 116.
  • Hot water or heated feed water S ' i. the set Partial flow TS by opening one or each spray head 105 upstream shut-off valve 119 (FIG 2) for flowing brought.
  • the thereby spring-loaded valve cone 117th pending differential pressure automatically lifts it from the valve seat 116 off.
  • hot water HW designated heated feed water S 'over one in the area the valve seat 117 provided annular space 120 and thus connected bores or valve channels 121 to a number of spray nozzles 122.
  • the flow of hot water HW through the narrow holes or valve channels 121 and spray nozzles 122 leads to an increasing Pressure reduction.
  • the boiling conditions are exceeded in the area of the spray nozzles 122 becomes a part of the hot water HW evaporates and thus finely distributes the resulting mixture.
  • the remaining hot water HW by evaporation cooled. Due to the injection of the partial flow ts heated Feedwater S 'or hot water HW and the effective Mixing with the spray heads 105 in the interior 104 Be the measuring device 44 surrounding cold condensate K resulting, small steam bubbles again condensed and together brought to a mixing temperature with the hot water HW, the below the prevailing at this pressure boiling temperature lies.
  • the spray heads 105 are each via a supply or intermediate line 123 with the hot water line 101 on the downstream side the shut-off valve 119 connected.
  • a supply or intermediate line 123 with the hot water line 101 on the downstream side the shut-off valve 119 connected.
  • Number of spray heads 105 provided or required a corresponding number of intermediate lines 123 to the Hot water line 101 are connected. This is both the constructive as well as the production or assembly technology Effort for the respective interpretation of the mixing device 44.46 particularly low.

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  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Investigating, Analyzing Materials By Fluorescence Or Luminescence (AREA)

Abstract

L'invention concerne un procédé pour l'exploitation d'une installation de turbines à vapeur et à gaz (1) comprenant une turbine à gaz (2) exploitable aussi bien au gaz qu'à l'huile. Selon l'invention, lors du passage de l'exploitation au gaz à l'exploitation à l'huile, un flux partiel (tS) d'eau d'alimentation chauffée (S') est injecté dans le condensat froid (K) afin de préchauffer le condensat. A cet effet, l'installation (1) comprend un dispositif de mélange (44, 46) dans lequel se trouve au moins une tête de pulvérisation (105) raccordée à une conduite d'eau chaude (101) et servant à amener le flux partiel (tS).

Claims (10)

  1. Procédé pour faire fonctionner une installation (1) de turbine à gaz et de turbine à vapeur, dans lequel on envoie le gaz (AM) de fumée sortant d'une turbine (2) à gaz pouvant fonctionner tant au gaz qu'au pétrole sur un générateur (30) de vapeur à récupération de la chaleur perdue, dont des surfaces de chauffe sont montées dans le circuit (24) eau-vapeur d'une turbine (20) à vapeur ayant un certain nombre d'étages (20a, 20b, 20c) de pression du produit condensé préchauffé dans le générateur (30) de vapeur à récupération de la chaleur perdue étant chauffé en tant qu'eau (S) d'alimentation se trouvant sous une haute pression par rapport à celui-ci et étant envoyé en tant que vapeur (F) à la turbine (20) à vapeur,
       caractérisé en ce que lors d'un passage du gaz au pétrole, on injecte un courant (tS) partiel d'eau (S') d'alimentation réchauffée dans le produit condensé (K) froid.
  2. Procédé suivant la revendication 1, caractérisé en ce que l'on prélève le courant (tS) partiel d'un étage (50) haute pression et/ou d'un étage (70) moyenne pression du circuit (24) eau-vapeur.
  3. Procédé suivant la revendication 1 ou 2, caractérisé en ce que l'on prélève du côté de la sortie le courant (tS) partiel d'un économiseur (51, 52) haute pression ou d'un économiseur (73) moyenne pression prévu en tant que surface de chauffe dans le générateur (30) de vapeur à récupération de la chaleur perdue.
  4. Procédé suivant l'une des revendications 1 à 3, caractérisé en ce que l'on prélève le courant (tS) partiel d'un ballon (54) haute pression ou d'un ballon (75) moyenne pression monté dans le circuit (24) eau-vapeur.
  5. Installation (1) de turbine à gaz et de turbine à vapeur ayant une turbine (2) à gaz pouvant fonctionner tant au gaz qu'au pétrole et un générateur (30) de vapeur à récupération de la chaleur perdue monté en aval de celle-ci côté gaz d'échappement, dont des surfaces de chauffe sont montées dans le circuit (24) eau-vapeur d'une turbine (20) à vapeur comprenant au moins un étage (20c) basse pression et un étage (20b) haute pression, caractérisée par un dispositif (44, 46) de mélange comportant une chambre (104) intérieure et ayant une ouverture (111 ) d'entrée communiquant avec un conduit (38) pour du produit condensé destiné à apporter du produit (K) condensé et une ouverture (112) de sortie communiquant du côté entrée avec un préchauffeur (36) de produit condensé, disposé en tant que surface de chauffe dans le générateur (30) de vapeur à récupération de la chaleur perdue, ainsi qu'au moins une tête (105) de pulvérisation, qui est disposée dans la chambre (104) intérieure et à laquelle peut être envoyé, par un conduit (101) d'eau chaude communiquant du côté aval avec la tête et allant côté entrée sur un ballon (54, 75) de pression monté dans le circuit (24) eau-vapeur côté eau et/ou côté sortie sur un économiseur disposé en tant que surface de chauffe dans le générateur (30) de vapeur à récupération de la chaleur perdue, un courant (tS) partiel d'eau (S') d'alimentation chauffée réglable, prélevé du ballon (54, 75) sous pression ou de l'économiseur (51, 52, 73).
  6. Installation suivant la revendication 5, caractérisée en ce qu'il est monté dans la direction d'écoulement du courant (tS) partiel en amont du dispositif (44, 46) de mélange dans le conduit (101) pour de l'eau chaude une vanne (103) de réglage du courant (tS) partiel.
  7. Installation suivant la revendication 5 ou 6, caractérisée par un certain nombre de têtes (122) de pulvérisation qui communiquent avec le conduit (101) d'eau chaude par, respectivement, un conduit (123) intermédiaire.
  8. Installation suivant la revendication 7, caractérisé en ce qu'il est monté dans la direction de l'écoulement du courant (tS) partiel en amont du ou de chaque conduit (123) intermédiaire un robinet (119) d'arrêt dans le conduit (101) d'eau chauffe.
  9. Installation suivant l'une des revendications 5 à 8, caractérisée en ce que chaque tête (105) de pulvérisation a une vanne (116, 117) s'ouvrant automatiquement en raison de la différence de pression du courant (tS) partiel par rapport au produit (K) condensé froid.
  10. Installation suivant la revendication 9, caractérisée en ce que la vanne (116, 117) communique par au moins un canal (121) de vanne avec au moins une buse (122) de pulvérisation de la tête (105) de pulvérisation.
EP01978376A 2000-09-29 2001-09-17 Procede pour l'exploitation d'une installation de turbines a vapeur et a gaz et installation correspondante Expired - Lifetime EP1320665B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP01978376A EP1320665B1 (fr) 2000-09-29 2001-09-17 Procede pour l'exploitation d'une installation de turbines a vapeur et a gaz et installation correspondante

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP00121502 2000-09-29
EP00121502A EP1193373A1 (fr) 2000-09-29 2000-09-29 Méthode pour opérer une installation à turbines à gaz et à vapeur et installation correspondante
PCT/EP2001/010749 WO2002027154A1 (fr) 2000-09-29 2001-09-17 Procede pour l'exploitation d'une installation de turbines a vapeur et a gaz et installation correspondante
EP01978376A EP1320665B1 (fr) 2000-09-29 2001-09-17 Procede pour l'exploitation d'une installation de turbines a vapeur et a gaz et installation correspondante

Publications (2)

Publication Number Publication Date
EP1320665A1 EP1320665A1 (fr) 2003-06-25
EP1320665B1 true EP1320665B1 (fr) 2005-05-11

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EP00121502A Withdrawn EP1193373A1 (fr) 2000-09-29 2000-09-29 Méthode pour opérer une installation à turbines à gaz et à vapeur et installation correspondante
EP01978376A Expired - Lifetime EP1320665B1 (fr) 2000-09-29 2001-09-17 Procede pour l'exploitation d'une installation de turbines a vapeur et a gaz et installation correspondante

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Application Number Title Priority Date Filing Date
EP00121502A Withdrawn EP1193373A1 (fr) 2000-09-29 2000-09-29 Méthode pour opérer une installation à turbines à gaz et à vapeur et installation correspondante

Country Status (6)

Country Link
US (1) US6874322B2 (fr)
EP (2) EP1193373A1 (fr)
DE (1) DE50106221D1 (fr)
ES (1) ES2240527T3 (fr)
TW (1) TW541392B (fr)
WO (1) WO2002027154A1 (fr)

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US8359824B2 (en) * 2008-07-29 2013-01-29 General Electric Company Heat recovery steam generator for a combined cycle power plant
US8157512B2 (en) * 2008-07-29 2012-04-17 General Electric Company Heat pipe intercooler for a turbomachine
US8425223B2 (en) * 2008-07-29 2013-04-23 General Electric Company Apparatus, system and method for heating fuel gas using gas turbine exhaust
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EP1320665A1 (fr) 2003-06-25
US20040011049A1 (en) 2004-01-22
US6874322B2 (en) 2005-04-05
WO2002027154A1 (fr) 2002-04-04
EP1193373A1 (fr) 2002-04-03
ES2240527T3 (es) 2005-10-16
TW541392B (en) 2003-07-11
DE50106221D1 (de) 2005-06-16

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