EP2999869A1 - Centrale électrique à turbine à gaz rendue flexible - Google Patents

Centrale électrique à turbine à gaz rendue flexible

Info

Publication number
EP2999869A1
EP2999869A1 EP14725395.9A EP14725395A EP2999869A1 EP 2999869 A1 EP2999869 A1 EP 2999869A1 EP 14725395 A EP14725395 A EP 14725395A EP 2999869 A1 EP2999869 A1 EP 2999869A1
Authority
EP
European Patent Office
Prior art keywords
heat
gas turbine
line
fluid
heat storage
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.)
Withdrawn
Application number
EP14725395.9A
Other languages
German (de)
English (en)
Inventor
Christian Brunhuber
Carsten Graeber
Uwe Lenk
Klaus Werner
Gerhard Zimmermann
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
Original Assignee
Siemens AG
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 filed Critical Siemens AG
Publication of EP2999869A1 publication Critical patent/EP2999869A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/08Heating air supply before combustion, e.g. by exhaust gases
    • F02C7/10Heating air supply before combustion, e.g. by exhaust gases by means of regenerative heat-exchangers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/02Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being an unheated pressurised gas
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/20Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products
    • F02C3/30Adding water, steam or other fluids for influencing combustion, e.g. to obtain cleaner exhaust gases
    • F02C3/305Increasing the power, speed, torque or efficiency of a gas turbine or the thrust of a turbojet engine by injecting or adding water, steam or other fluids
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/14Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/18Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C9/00Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
    • F02C9/16Control of working fluid flow
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00Application
    • F05D2220/70Application in combination with
    • F05D2220/76Application in combination with an electrical generator
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02EREDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00Combustion technologies with mitigation potential
    • Y02E20/14Combined heat and power generation [CHP]
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02EREDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00Combustion technologies with mitigation potential
    • Y02E20/16Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Definitions

  • the present invention relates to a gas turbine power plant, which has a gas turbine, which is thermally connected to a recuperator for improved flexibility and a supply line for water. Furthermore, the present invention relates to a method for operating such a gas turbine power plant.
  • water or steam is introduced into the compressor or the combustion chamber of the gas turbine, which is possibly relaxed after transfer into the gas phase together with the combustion exhaust gases in the expander. Due to the increase in mass flow and the mechanical relaxation power is briefly increased, whereby for the time over which water or steam is injected into the gas turbine, an increased electrical power output follows.
  • a recuperator can be provided which further uses the thermal energy of the exhaust gas taken from the expander for the thermal treatment of other fluids.
  • the thermal energy which is still present in the exhaust gas of a gas turbine, can be used for steam preparation, which takes place in a steam process coupled to the gas turbine process for reconversion.
  • recuperator If the operation of such a recuperator is combined with the above-described injection of water into a gas turbine, a significant increase in efficiency can be achieved, as the gas injected into the gas turbine is heated in the gas turbine, and this heated water allows a high heat transfer rate in the recuperator , In this case, the heat transfer rate is greater than in the case of heat transfer from a "dry" exhaust gas at the same temperature, and the combination of injected water and recuperator can thus make a synergistic increase in efficiency. (RWI) - gas turbine process called.
  • This object of the invention is achieved by a gas turbine power plant according to claim 1 and a method for operating such a gas turbine power plant according to claim 10.
  • a gas turbine power plant comprising a ne a compressor, a combustion chamber and an expander having gas turbine, which is rotationally coupled to a Energetisticiansaku, wherein the Energetisticiansritt is designed for both a motorized operation of the compressor, as well as for generating current generating operation of the gas turbine, and further a recuperator, which is thermally connected with an exhaust pipe of the gas turbine such that during operation of the gas turbine heat from the exhaust stream in the exhaust pipe can be transferred to a fluid flow in a fluid line, which is supplied to the combustion chamber, further comprising a supply line for water, which fluidly such is connected to the gas turbine, that water of the gas turbine can be supplied to increase the operating mass flow during operation, and wherein the exhaust pipe is also thermally coupled with at least one heat storage, so that when operating the G asturbine the heat of the exhaust stream can be transferred to a heat storage medium for storage in the heat storage.
  • the object underlying the invention is achieved by a method for operating such a gas turbine power plant, which comprises the following steps: during a first operating phase:
  • the fluid flow is supplied to the combustion chamber, so that after introduction into the combustion chamber, the heat present in the fluid flow can be made available again for the gas turbine process.
  • the fluid flow may be, for example, an air flow, a humidified air flow or possibly also a mixture of air, water and fuel.
  • a pure fuel fluid stream eg, natural gas or methane may be included by the fluid flow.
  • heat from the exhaust gas flow is applied again to the fluid flow which is supplied to the combustion chamber.
  • the heat from the exhaust gas flow can also be transmitted by means of a first heat exchanger to a heat storage medium, which is temporarily stored in the first heat storage. Due to the intermediate storage, the thermal energy thus provided is also available at later points in time, and can then be converted back into electricity by a suitable process if required.
  • the heat accumulator can also provide heat for suitable applications for combined heat and power.
  • the heat accumulator can be interconnected with a district heating network or installations for industrial and domestic heat utilization.
  • the heat accumulator has a heat-technical and / or a fluid-technical connection for a combined heat and power plant (CHP), which in particular is a district heating network.
  • CHP combined heat and power plant
  • the feed line according to the invention for water leads water in possibly different physical states.
  • water can be conducted in liquid form or in vapor form or in a mixed form.
  • preference is given to the guidance of liquid water since this contributes to a cooling of the combustion gases after injection into the gas turbine.
  • the heat in the water is available for the gas turbine process with thermal relaxation in the expander.
  • water should be understood to mean both liquid and vapor water.
  • the supply line can open into the combustion chamber and / or into the compressor of the gas turbine.
  • the improved flexibility of the gas turbine power plant according to the present invention therefore results, on the one hand, from the plurality of different operating modes which the motor or generator operation of the energizing unit allows, as well as the time storage of thermal energy generated during a gas turbine process in a heat store.
  • the designated gas turbine process here refers to the plurality of different possible operating modes of the gas turbine.
  • the provision of the heat accumulator also allows the use of heat in further heat processes, in particular in conjunction with combined heat and power plants.
  • the fluid flow in the fluid line is substantially compressed air, wherein the fluid line is connected to the compressor fluidly.
  • the fluid line thus allows the discharge of compressed air from the compressor, and a subsequent supply after thermal treatment by means of the recuperator to the combustion chamber.
  • water in the form of vapor is added to the fluid flow. This can be performed in the fluid line, an air-water mixture, which can be burned together in the combustion chamber with a fuel together.
  • the water is used as a moderator in a combustion, but as a refrigerant in a relaxation.
  • the following embodiment is also particularly advantageous.
  • a water line which opens into the fluid line and can supply the fluid flow in the fluid line during operation of the gas turbine with water.
  • the water line can be water in liquid or gaseous form
  • the water line opens into the fluid line between the compressor and recuperator. This can also do that Water supplied via the water line of the fluid line can be thermally treated in the recuperator. After supplying the air-water mixture to the combustion chamber, according to the embodiment, no mixing of the individual constituents is necessary, since a mostly sufficient mixture has taken place in the fluid line.
  • the exhaust pipe is thermally connected to a capacitor, which is designed and connected in each case to the supply line and / or water line, that water condensed therein again according to the supply line and / or water pipe can be supplied.
  • the condenser thus enables the separation of water in the exhaust gas, which can be used again in the flexibilized gas turbine power plant process. This results in an at least partial water cycle for environmentally friendly and efficient water use.
  • the exhaust pipe is thermally coupled with at least two heat accumulators
  • the first heat storage is provided with a first heat storage medium and the second heat storage with a second heat storage medium
  • the temperature level of the first heat storage unequal to the temperature level of the second heat storage.
  • the first heat storage for example, designed as a hot storage
  • the operating temperature is typically above ambient temperature, ie approximately between 30 ° C and 200 ° C
  • the second heat storage as a cold storage
  • the temperature level typically below the ambient temperature of about 0 ° C to 30th ° C is.
  • the temperature limits may vary depending on the ambient temperature. A fluctuation range of about 10 ° C can be assumed here.
  • the gas turbine power plant it is thus possible to provide heat (through the exhaust gas flow of the gas turbine) or even cold (in the previously described embodiment of the cold expansion).
  • the heat which can be provided in each case at two different temperature levels, can be temporarily stored in two different heat accumulators, which are each provided with a heat storage medium.
  • the first heat accumulator is thermally connected to the exhaust pipe via a first heat exchanger
  • the second heat accumulator is thermally connected to the exhaust pipe via a second heat exchanger, wherein the first heat exchanger and the second heat exchanger are not identical are.
  • Both heat storage can therefore be addressed individually via separate heat exchanger or effect the heat exchange with the guided in the exhaust pipe medium. This will increase the flexibility of the gas turbine power plant. plant further increased, and ensures efficient heat storage.
  • first heat storage and the second heat storage are thermally connected via a first heat exchanger with the exhaust pipe.
  • Both heat accumulators can therefore only absorb thermal energy via a heat exchanger (first heat exchanger) or possibly also release it. This component reduction improves the construction and thus the cost.
  • a bypass line which is fluidically connected to the fluid line and which allows at least a portion of the fluid flow guided in the fluid line to pass around the recuperator without that it absorbs heat in the recuperator or gives off.
  • the bypass line allows, in particular during motor operation of the energizing unit, the bypassing of the recuperator, so that the
  • Combustion chamber supplied compressed fluid flow substantially retains its heat content. If the fluid line were in fact passed over the recuperator, it would be possible to reduce the heat content since the exhaust gas discharged from the exhaust gas line has a lower temperature level. According to another particularly preferred embodiment of the invention it is provided that the fluid line is also fluidly connected to a branch line, which allows at least a portion or even the entirety of the fluid flow guided in the fluid line to lead directly to the first heat exchanger or second heat exchanger for heat exchange ,
  • the branch line may in this case be arranged upstream or downstream with respect to the recuperator.
  • the fluid stream taken from the compressor which has been heated substantially adiabatically due to the compression, can be led directly to the first heat exchanger or the second heat exchanger for heat transfer to the first heat store or second heat store. Consequently, all the heat energy present in the fluid flow due to the adiabatic heating is available for heat exchange. Further thermal conditioning, especially towards a lower temperature level, can be avoided in this case.
  • the motor drive of the compressor allows the withdrawal of surplus electricity from the power supply networks to economically advantageous conditions, as well as the implementation of this electrical energy into thermal energy which can be cached in the first heat storage.
  • the thermal energy thus generated is available for further applications, in particular for applications in the field of combined heat and power, as far as the heat storage is connected with suitable devices for this purpose.
  • the provision of thermal energy by means of the compressed air flow can also be within relatively short Achieve time periods (less minutes), whereby the operation assumes an improved degree of flexibilization.
  • the following steps are likewise encompassed during a further operating phase, which is not carried out at times of the first, second or third operating phase: operating the energizing unit for the motor drive of the compressor;
  • FIG. 1 shows a first embodiment of the gas turbine power plant 1 according to the invention according to a first possible operating phase of the method according to the invention
  • FIG. 2 shows the embodiment of the gas turbine power plant 1 according to the invention shown in FIG. 1 in accordance with a further operating phase of the method according to the invention
  • FIGS. 1 and 2 shows the embodiment of the gas turbine power plant 1 according to the invention shown in FIGS. 1 and 2 in accordance with a further operating phase
  • 4 shows the embodiment of the gas turbine power plant 1 according to the invention shown in FIGS. 1 to 3 according to a further operating phase
  • 5 shows a further embodiment of the gas turbine power plant 1 according to the invention corresponding to a first operating phase of the method according to the invention
  • FIG. 6 shows a flowchart representation of an embodiment of the method according to the invention for operating a gas turbine power plant 1 according to the embodiments described above or below.
  • the gas turbine power plant 1 shows a first embodiment of the gas turbine power plant 1 according to the invention according to a first operating phase of an embodiment of the method according to the invention for the operation thereof.
  • the gas turbine power plant 1 in this case comprises a gas turbine 10, which is rotationally coupled to an energizing unit 5.
  • the gas turbine 10 comprises a compressor 11, in which air L can be sucked in operation.
  • the compressor 11 can be supplied with water via a feed line 17 in the vapor phase or in the liquid phase. After compression of the air L or the air-water mixture to a compressed
  • Fluid this is supplied via a fluid line 16 as the fluid flow 15 of the combustion chamber 12.
  • a recuperator 20 is provided, by means of which the heat of the exhaust gas flow in the exhaust pipe 14 can be removed and transferred to the fluid flow 15.
  • the thus compressed fluid flow 15 is mixed with the combustion chamber 12 supplied fuel B and burned in the combustion chamber 12.
  • the combustion products are fed to the expander 13, via which a thermal expansion takes place with simultaneous mechanical working line.
  • the recuperator 20 In addition to the heat transfer from the exhaust gas flow in the exhaust pipe 14 by means of the recuperator 20 further takes place a heat transfer Transmission by means of the first heat exchanger 32, which may optionally include a capacitor 40 (not expressly drawn in the present case).
  • the heat accumulator 30 can have a suitable thermal connection with a district heating network 50, or another form of heat utilization device.
  • a water supply by means of a water line 18 can be carried out, which supplies the water in the vapor phase of the fluid line 16.
  • the expander can also be inserted directly via a branch not provided with reference symbols from the fluid line 16
  • Partial flow of the fluid stream 15 are added. This supports the conversion of thermal energy into rotational energy.
  • FIG. 2 shows the embodiment of the gas turbine power plant 1 according to the invention already shown in FIG. 1, which is operated in a second operating phase of an embodiment of the method according to the invention for operating a gas turbine power plant.
  • the energizing unit 5 is operated by a motor so that air is sucked into the compressor 11 and supplied as a compressed fluid flow 15 in the fluid line 16 to the combustion chamber 12. Due to the adiabatic heating by compression in the compressor 11, the fluid flow has a temperature level above the ambient temperature (up to 250 ° C). In the combustion chamber 12, the compressed fluid stream 15 is burned with fuel B.
  • no supply of fuel B and a subsequent combustion in the combustion chamber 12 (shown here).
  • the combustion products discharged from the combustion chamber 12 are expanded in the expander 13 and fed via the exhaust gas line 14 to the first heat exchanger 32.
  • a corresponding heat exchange can take place here in the recuperator 20, depending on the present temperature levels of fluid flow 15 and exhaust gas flow.
  • the first heat exchanger 32 the heat is in turn transmitted to a first heat storage medium 35 in the first heat storage 30.
  • the heat utilization is again available to a suitable consumer, for example a district heating network 50.
  • FIG. 3 shows the embodiment of the gas turbine power plant 1 already described in FIGS. 1 and 2, which is operated in a further operating phase which is not identical to the first and second operating phases.
  • the energy-generating unit 5 again receives electrical energy and drives the compressor 11 during engine operation.
  • the sucked air L is compressed and guided as fluid flow 15 in the fluid line 16.
  • the fluid flow 15 is fed to the first heat exchanger 32 for heat transfer by means of the branch line 46, which is preferably connected to the fluid line 16 via an actuating means (valve) not further provided with reference symbols.
  • a supply of the fluid flow 15 to the combustion chamber 12 is not provided here.
  • no heat exchange via the recuperator 20 is provided.
  • the heat transferred to the first heat storage medium 35 by means of the first heat exchanger 32 can in turn be temporarily stored in the first heat storage 30, and made available to a suitable user, for example the district heating network 50.
  • FIG. 4 shows the gas turbine power plant 1 already described in FIGS. 1 to 3, which is operated in a further operating phase which is not identical to the above-described operating phases according to FIGS. 1 to 3. Accordingly, electric energy E is again generated by the energy Captured unit 5 and used for rotary mechanical drive of the compressor 11. At the same time, water can be added to both the compressor 11 and / or the fluid line 16 by means of the supply line 17 or water line 18. The air L or the air-water mixture is compressed by means of the compressor 11 and the fluid flow 15 in the
  • Fluid line 16 of the combustion chamber 12 is supplied.
  • Bypass line 45 which is fluidly connected to the fluid line 16, allows bypassing the recuperator 20. Insofar, there is no heat transfer from or to the fluid flow 15. It is essential for the illustrated operating phase of the execution method that the combustion chamber 12 fed fluid flow 15 moist is, that has a proportion of water vapor. This proportion is preferably more than 10% by mass and preferably not more than 30% by mass. In the combustion chamber 12 there is no further combustion, so that this fluid flow 15 is the expander 13 fed directly to the relaxation. Due to the relaxation and the high water content in the fluid flow, the exhaust gas flow cools to temperatures well below the ambient temperature. Temperatures of 0 to 30 ° C are typical here. Also, temperatures of less than 0 ° C can be achieved, but this should be avoided because by crystallization of the water in the fluid flow 15 solids are formed, which can damage the components of the expander 13.
  • the exhaust gas flow guided in the exhaust gas line 14 can only deliver part of its heat (negative thermal energy, cold) via the recuperator 20 to a further fluid flow.
  • the second heat storage 31 may in this case in turn be connected to a suitable installation for use of cold, such as a district cooling system 51.
  • a suitable installation for use of cold such as a district cooling system 51.
  • the first heat storage 30 and the second heat storage 31 are identical, but charged at different times to a different temperature level.
  • the gas turbine power plant 1 differs from the embodiment shown in FIG. 1 only in that the recuperator 20 is connected not only to a single heat accumulator but to two heat accumulators 30 and 31.
  • the first is preferred Heat storage 30 for storing heat by means of the first heat storage medium 35 provided at a first temperature level Tl
  • the second heat storage 31 for storing heat by means of the second heat storage medium 36 at a second temperature level T2. Both heat storage 30, 31 are individually connected via a heat exchanger 32, 33 with the exhaust pipe 14.
  • the exhaust pipe 14 as shown in the present case, has a branch. Depending on the operating phase, heat or cold can thus be supplied to one of the two heat accumulators 30, 31. Consequently, two heat storage at different temperature levels Tl, T2 may be available for use during operation of the gas turbine power plant.
  • FIG. 6 shows a flowchart representation of an embodiment of the method according to the invention for operating a gas turbine power plant 1 described above, which comprises the following steps during a first operating phase B1:
  • second method step 102 Compressing fluid by means of the compressor 11 and directing the compressed fluid flow 15 by means of the fluid line 16 to the combustion chamber 12 (third method step 103);

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne une centrale électrique à turbine à gaz (1), comprenant une turbine à gaz (10), laquelle comporte un compresseur (11), une chambre de combustion (12) et un expanseur (13) et est couplée mécaniquement en rotation à une unité d'énergétisation (5). L'unité d'énergétisation (5) st réalisée aussi bien pour un fonctionnement motorisé du compresseur (11) que pour un fonctionnement de la turbine à gaz (10) produisant du courant, en mode générateur. La centrale électrique à turbine à gaz comprend en outre un récupérateur (20) qui est câblé d'un point de vue thermique à une conduite d'évacuation de gaz d'échappement (14) de la turbine à gaz (10) de telle manière que lors du fonctionnement de la turbine à gaz (10) de la chaleur provenant du flux des gaz d'échappement peut être transférée dans la conduite d'évacuation des gaz d'échappement (14) sur un flux de fluide (15) dans une conduite de fluide (16), lequel flux de fluide peut être amené à la chambre de combustion (12). En outre, l'invention prévoit une conduite d'arrivée (17) pour l'eau, qui est branchée selon la technique des fluides à la turbine à gaz (10) de telle manière que l'eau peut être acheminée à la turbine à gaz (10) lors du fonctionnement pour augmenter le flux massique de service. La conduite des gaz d'échappement (14) est en outre d'un point de vue thermique couplée à au moins un accumulateur de chaleur (30) de sorte que lors du fonctionnement de la turbine à gaz (10) de la chaleur du flux des gaz d'échappement peut être transférée sur un milieu accumulateur de chaleur (35) aux fins du stockage dans l'accumulateur de chaleur (30).
EP14725395.9A 2013-08-01 2014-05-08 Centrale électrique à turbine à gaz rendue flexible Withdrawn EP2999869A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013215083.0A DE102013215083A1 (de) 2013-08-01 2013-08-01 Flexibilisiertes Gasturbinenkraftwerk
PCT/EP2014/059454 WO2015014508A1 (fr) 2013-08-01 2014-05-08 Centrale électrique à turbine à gaz rendue flexible

Publications (1)

Publication Number Publication Date
EP2999869A1 true EP2999869A1 (fr) 2016-03-30

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Family Applications (1)

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EP14725395.9A Withdrawn EP2999869A1 (fr) 2013-08-01 2014-05-08 Centrale électrique à turbine à gaz rendue flexible

Country Status (4)

Country Link
US (1) US20160177827A1 (fr)
EP (1) EP2999869A1 (fr)
DE (1) DE102013215083A1 (fr)
WO (1) WO2015014508A1 (fr)

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DE102020201068A1 (de) 2020-01-29 2021-07-29 Siemens Aktiengesellschaft Anlage mit thermischem Energiespeicher, Verfahren zum Betreiben und Verfahren zur Modifikation

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DE102013215083A1 (de) 2015-02-05
US20160177827A1 (en) 2016-06-23

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