WO2003104629A1 - Groupe de turbines a gaz - Google Patents

Groupe de turbines a gaz Download PDF

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Publication number
WO2003104629A1
WO2003104629A1 PCT/EP2003/050181 EP0350181W WO03104629A1 WO 2003104629 A1 WO2003104629 A1 WO 2003104629A1 EP 0350181 W EP0350181 W EP 0350181W WO 03104629 A1 WO03104629 A1 WO 03104629A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
fluid
process fluid
temperature
gas turbine
Prior art date
Application number
PCT/EP2003/050181
Other languages
German (de)
English (en)
Inventor
Hans Ulrich Frutschi
Hans Wettstein
Original Assignee
Alstom (Switzerland) Ltd
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 Alstom (Switzerland) Ltd filed Critical Alstom (Switzerland) Ltd
Priority to AU2003238526A priority Critical patent/AU2003238526A1/en
Publication of WO2003104629A1 publication Critical patent/WO2003104629A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G6/00—Devices for producing mechanical power from solar energy
    • F03G6/06—Devices for producing mechanical power from solar energy with solar energy concentrating means
    • F03G6/064—Devices for producing mechanical power from solar energy with solar energy concentrating means having a gas turbine cycle, i.e. compressor and gas turbine combination
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/05—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly characterised by the type or source of heat, e.g. using nuclear or solar energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/36—Open cycles
    • F02C3/365—Open cycles a part of the compressed air being burned, the other part being heated indirectly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, 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
    • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S90/00—Solar heat systems not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/10—Particular cycles
    • Y—GENERAL 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/46—Conversion of thermal power into mechanical power, e.g. Rankine, Stirling or solar thermal engines

Definitions

  • the invention relates to a gas turbine group according to the preamble of claim 1.
  • the invention further relates to a method for generating useful power in a gas turbine group according to the invention.
  • a gas turbine group of the type mentioned at the outset, with preheating of the compressed combustion air by means of solar heat coupling, is from the article by Bück et al .: "Solar-Hybrid Gas Turbine-based Power Tower Systems (REFOS)", Proceedings of Solar Forum 2001, Solar Energy: The Power to Choose, April 21-25, 2001, Washington, DC.
  • REFOS Solar-Hybrid Gas Turbine-based Power Tower Systems
  • the entire combustion air mass flow must flow through the solar heat exchanger, which is associated with considerable pressure losses, even in times when the solar heat exchanger cannot make any contribution to hot gas generation.
  • the object of the invention is, based on the above-mentioned state of the art, to specify a gas turbine group which can avoid the disadvantages of the state of the art mentioned, and in particular enables efficient and low-loss coupling of solar heat. Furthermore, particularly favorable methods for operating a gas turbine group according to the invention are to be specified.
  • the essence of the invention is therefore a solar heat coupling means, in particular a solar collector, in one of the process gases
  • the solar heat coupling means is a solar collector; however, it can also be a further heat exchanger which is flowed through on the secondary side by the heat transport fluid and on the primary side by another, solar-heated fluid.
  • the arrangement of the solar heat coupling means in a separate preheating circuit enables a free choice of the heat transfer fluid. Through a suitable choice, the specific heat transport density can be chosen to be large, such that significantly lower volume flows have to flow through the solar heat coupling means than would be the case if the
  • Solar heat coupling agent would be flowed through directly by the process fluid.
  • the arrangement of a separate circuit for the solar heat coupling further enables a largely free choice of States of the heat transfer fluids.
  • By choosing a high pressure the volume flow of a gaseous or supercritical fluid can be further reduced.
  • helium is also suitable because good heat transfer coefficients can be achieved in a helium circuit and because helium has a high heat capacity, as a result of which the necessary volume flow is kept small. This results in a low pressure drop during the process, also in connection with the high speed of sound of helium
  • a throttling and / or shut-off shunt line between the feed line and the return line of the preheating circuit
  • a throttling and / or shut-off device is also advantageous, with which fluid separation of the solar collector from the rest of the preheating circuit is realized can be.
  • the solar heat coupling means is unable to make a contribution to the operation of the gas turbine group, or would even remove heat from it.
  • the temperature of the process fluid after the compressor is already some 100 ° C, for example 400 ° C to over 500 ° C under full load.
  • the heat transport fluid which flows over the return line, assumes approximately this temperature in the process fluid preheater. If the heat transport fluid flows into a solar collector at this temperature, for example, this can be the case on cold nights or on denser days Cloud cover lead to considerable heat losses, which are avoided if the heat transport fluid flows through the parallel shunt line instead of through the solar heat coupling means.
  • Preheating circuit Means for varying the circulating heat transfer fluid mass flow This can be, for example, a delivery blower or a delivery pump with a variable speed.
  • the preheating circuit in the return line in the flow path from the solar heat coupling means or from the shunt line to the process fluid preheater, has a further heat exchanger through which the heat transport fluid flows on the secondary side and the primary side with a non-solar heat source, in particular a fossil-fired firing device , communicates.
  • a non-solar heat source in particular a fossil-fired firing device
  • this additional heat exchanger via which heat from a non-solar heat source can be coupled into the preheating circuit, makes it possible to preheat the process fluid to a higher temperature level than would be possible with the solar heat coupling alone.
  • the non-solar additional preheating also enables the gas turbine group to be operated with preheating at times when there is no solar preheating option. This means that the main process of the gas turbine group is subject to far fewer variations depending on the time of day and weather than would be the case without an additional non-solar heat source.
  • the additional preheating by means of a non-solar heat source also makes it possible, regardless of the currently available solar heat potential, to preheat the process fluid, for example, to such an extent that the use of a combustion chamber with auto-ignition is possible, as is known, for example, from EP 669 500.
  • the one entering the combustion chamber Combustion air in the process fluid preheater are preheated to a sufficiently high temperature, for example 900 ° C. and more, in order to ensure spontaneous self-ignition of the fuel introduced into the combustion chamber. In this way, very low pollutant emissions can be achieved.
  • a gaseous process fluid that is to say air in the case of an open gas turbine group
  • the process fluid flows through the secondary side of a heat exchanger connected as a process fluid preheater, which is integrated on the primary side into a preheating circuit.
  • the process fluid is preheated and then flows into at least one combustion chamber.
  • Fuel is mixed in there, and combustion of the fuel generates a hot gas, which is expanded in a turbine to perform work.
  • a reheating of partially expanded hot gas and further expansion steps, each with the release of mechanical power can follow, as has become known from EP 620 362.
  • Intercooling steps can also be integrated in the compression process.
  • a heat transfer fluid is circulated in the preheating circuit. This absorbs heat in the solar heat coupling-in means and / or in a second non-solar heat exchanger, and transfers it to the process fluid flowing there on the secondary side when it flows through the primary side of the process fluid preheater.
  • the method measures the temperature of the process fluid downstream of the process fluid preheater or, alternatively or additionally, the temperature of the heat transport fluid in the feed line upstream of the process fluid preheater. If the temperature falls below a limit value, then an additional heat supply to the heat transport fluid takes place via the second heat exchanger, so there is in particular an additional firing arranged there to maintain a minimum temperature of the preheated process gas of the gas turbine group regulated.
  • an additional firing arranged in operative connection with the preheating circuit is operated in such a way that the temperature of the process fluid when it enters the combustion chamber does not fall below a required minimum temperature of, for example, 900 ° C.
  • the temperature of the process fluid is measured downstream of the process fluid preheater, and the mass flow of the heat transport fluid circulated in the preheating circuit is regulated as a function of this temperature, such that the mass flow of the heat transport fluid is reduced as the temperature of the process fluid increases and as the temperature of the process fluid falls Process fluid is increased.
  • This measure proves to be very advantageous, in particular in connection with the operation of an auxiliary firing, as described above in operative connection with the preheating circuit.
  • a setpoint of the temperature of the heat transport fluid when entering the process fluid preheater is set with the aid of the additional firing, and the temperature of the process fluid is kept to a minimum value by means of the mass flow control of the heat transport fluid.
  • the combination of the two control mechanisms ensures that the preheating operation is as efficient as possible, especially when there is insufficient solar heat coupling potential.
  • Heat transport fluids downstream of the solar heat coupling means or the temperature of a solar collector or an increase in temperature of the heat transport fluid via the solar heat coupling means is measured, and if the temperature falls below a limit of this measured value, the flow of the heat transport fluid through the solar heat coupling means is throttled or completely shut off. At least a partial flow of the heat transport fluid is then advantageously conducted via the shunt line, and heat is supplied to the heat transport fluid in the second heat exchanger.
  • a gas turbine group according to the invention, or a gas turbine group operated according to the method according to the invention, proves to be particularly suitable for use in a combination system, the gas turbine group being connected in a manner known per se to a person skilled in the art to be followed by a waste heat steam generator through which the exhaust gas of the gas turbine group flows, and with which Heat recovery steam generators generated steam is driven by a steam turbine group.
  • the gas turbine group can also be designed as a gas turbine group with sequential combustion of the type known from EP 620 362, regardless of the coupling of solar heat according to the invention.
  • Figure 1 shows a combination system with a gas turbine group according to a particularly advantageous embodiment of the invention
  • the gas turbine group is a gas turbine group with sequential
  • FIG. 2 shows an essentially identical power plant, in which the gas turbine group is designed with only one combustion chamber and one turbine.
  • FIG. 1 shows an example of a combination system which comprises a gas turbine group according to the invention.
  • the gas turbine group comprises a compressor 1, combustion chambers 2a, 2b, and turbines 3a, 3b.
  • the compressor sucks in air 11 from the environment.
  • the mass flow of the intake air is next to the ambient pressure and the ambient temperature are significantly influenced by the position of the adjustable inlet line 101 of the compressor.
  • the pilot series position is controlled in a manner known per se and not essential to the invention.
  • the air 12 compressed in the compressor 1 flows into a process fluid preheater 31, in which the compressed air is preferably preheated by means of solar heat, which will be explained in detail below.
  • the preheated air 13 flows into the combustion chamber 2a.
  • a first amount of fuel 19 is mixed in there and burned.
  • the resulting hot gas 14 is partially expanded in a first turbine 3a, typically with a pressure ratio of approximately 2.
  • the partially expanded hot gas 15 is still at a high temperature and a high residual oxygen content.
  • a further quantity of fuel 20 is admixed to this partially expanded flue gas in the second combustion chamber 2b, and the partially expanded gas is reheated by its combustion before the post-heated gas 16 flows into a second turbine 3b, where it is expanded to approximately ambient pressure.
  • a mechanical power is generated which is used to drive the compressor 1 and a generator 5.
  • the relaxed process fluid 17 is still at a high temperature, which in a gas turbine group of the type shown at full load is in the range from 550 ° C. to over 600 ° C.
  • the last turbine 3a is followed by a heat recovery steam generator 4 through which the relaxed process fluid 17 flows.
  • steam is generated from a quantity of feed water; heat is removed from the relaxed process fluid 17 and it finally flows out into the atmosphere as exhaust gas 18.
  • the water-steam cycle described below is very simplified and shown schematically.
  • a feed pump 9 first feeds feed water into a preheater 401 of the heat recovery steam generator 4, where the feed water 21 is ideally preheated to a little below the boiling temperature. This water flows into a steam drum 402.
  • Saturated water is circulated in the steam generator 403.
  • Saturated steam flows from drum 402 into superheater 404, from where superheated steam 22 flows to high-pressure steam turbine 6, and there work-relieving down to an intermediate pressure.
  • the partially expanded steam 23 flows into an intermediate superheater 405 and is heated again to the fresh steam temperature.
  • superheated medium-pressure steam 24 flows to the double-flow medium / low-pressure steam turbine 7, where it is expanded into a vacuum to perform work.
  • Relaxed steam 25 flows from the evaporative floods of the medium / low-pressure turbine 7 into the condenser 8; The steam is condensed there and the resulting condensate is conveyed back into the boiler by the feed pump 9.
  • the steam turbines are arranged on a common shaft and, together with the gas turbine group, drive a common generator 5 via an automatically acting clutch 10.
  • the process fluid preheater 31 is used to couple solar heat into the working process of the gas turbine group. By preheating the compressed process fluid 12, less fuel has to be supplied in the combustion chamber 2a in order to reach a certain temperature of the hot gas 14 at the entry into the turbine 3a. If, as is known from the prior art, the process fluid was passed directly through a solar collector with a mass flow of, for example, 500 kg / s, then considerable pressure losses would have to be expected, which are in no way tolerable.
  • the process fluid preheater 31 is therefore designed as a cross-countercurrent heat exchanger which is flowed through on the secondary side by the heat-absorbing process fluid 12 and on the primary side by a heat transport fluid which brings the heat to be coupled in, preferably solar heat.
  • the heat transport fluid is conducted in a circuit, whereby it absorbs heat in a solar collector 32 and couples it into the gas turbine process in the process fluid preheater 31.
  • the closed routing of the heat transfer fluid allows a free choice of a suitable medium.
  • the entire preheating circuit which includes at least the process fluid preheater 31, solar heat coupling means 32 - in the example, a solar collector -, a flow line 34 for guiding the heat transport fluid from the solar heat coupling means 32 to the process fluid preheater 31, and a return line 33 for guiding the heat transport fluid from Process fluid preheater 31 to the solar heat coupling means 32, designed as a two-phase circuit, is such that the coupling of solar heat into the preheating circuit is supported by the evaporation of the heat transport fluid, while the heat transfer to the process fluid in the process fluid preheater 31 is intensified by the condensation of the heat transport fluid.
  • the prevailing temperature levels must also be taken into account.
  • the temperature of compressed air 12 when it enters the process fluid preheater 31 is already around 500 ° C., which at the same time represents the lowest temperature in the preheating circuit.
  • the preheating circuit is to be designed as a water-steam circuit, it must basically be operated supercritically.
  • the temperature of the preheated process fluid 13 should preferably be at least 800 ° C. in order to use the preheating in a technically and economically sensible manner; Temperatures above 900 ° C are preferred for the reasons set out below. It is also conceivable, for example, to use unspecified oils, including synthetic oils, as pure liquids or with a phase change within the preheating circuit.
  • a gaseous medium for example helium under pressure
  • the advantages of helium for this application have been explained above.
  • the heat transfer fluid is circulated by a circulation fan 35 in the preheating circuit.
  • the circulation fan 35 is driven by a motor 36;
  • the mass flow of the circulated medium can be varied by regulating the speed of the motor.
  • the preheating circuit also includes a shunt line 37, which is arranged in terms of flow in parallel with the solar heat coupling means and which creates a direct connection between the flow line and the return line bypassing the solar heat coupling means , and a second heat exchanger 38.
  • the flow through the Solar heat coupling means 32 and the shunt line 37 can be shut off and / or throttled by shut-off and / or throttling elements 39, 40.
  • a second heat exchanger is also arranged within the flow line 34 leading from the solar collector 32 to the process fluid preheater 31, through which the heat transport fluid flows on the secondary side.
  • heat from a non-solar heat source 41 here a fossil-fired combustion device, can be coupled into the preheating circuit via the second heat exchanger 38.
  • the combustion chamber 41 is supplied with combustion air by a fresh air blower 42.
  • a corresponding amount of fuel is metered via the actuator 43.
  • the fresh air blower 42 is driven by a variable-speed motor 44.
  • the mass flow of the air conveyed by the blower 42 can be adapted to the needs of the firing device on the way by varying the speed.
  • the combustion air 46 conveyed by the blower 42 flows through an air preheater 45, which also continues from
  • Flue gas 47 flows through the firing device.
  • the combustion air 46 is preheated in the heat exchange with the flue gas 47, which ensures the best use of fuel.
  • a temperature measuring point 48 determines the temperature of the preheated one
  • Process fluids 13 of the gas turbine group This temperature is kept at or above a certain minimum value, for example 900 ° C or 1000 ° C.
  • a certain minimum value for example 900 ° C or 1000 ° C.
  • a second temperature sensor 49 is arranged in the flow line 34 between the second heat exchanger 38 and the process fluid preheater 31 and determines the temperature of the heat transport fluid immediately upstream of the process fluid preheater. This temperature is preferably set to a minimum value which is, for example, 20 ° C. above the minimum value of the temperature of the preheated process fluid. If the temperature falls below this minimum, the furnace 41 is put into operation.
  • the speed of the drive motor 44 of the combustion air blower 42 and the position of the actuator 43 are regulated so that the furnace heats the heat transfer fluid to this temperature setpoint. If the temperature falls below the temperature setpoint, the speed of the combustion air blower is increased and the actuator 43 is opened, with which more air and fuel flow into the firing device 41 and the firing performance is increased. Conversely, if the temperature setpoint is exceeded, the speed is reduced and the fuel actuator 43 of the firing device is closed further. This ensures that the process fluid can be preheated to the minimum temperature required for the auto-ignition of the fuel in the combustion chamber 2a even in the event of insufficient solar radiation.
  • Another temperature measuring point 50 is arranged on the solar collector 32. This temperature measuring point could also be arranged at a point downstream of the solar collector.
  • the temperature measuring point 50 is a measure of that in the solar collector heat introduced determined. If this temperature falls below a certain limit value, for example the temperature of the heat transport fluid in the return line 33, the throttle and shut-off element 39 of the solar collector is closed and the throttle and shut-off element 40 of the shunt line 37 is opened.
  • Heat transport fluid is then not wholly or partially conveyed through the solar collector but through the shunt line. This avoids heat loss through the solar panel, especially at night or when there is heavy cloud cover. Since the temperature of the heat transport fluid flowing out of the process fluid preheater is typically in the range from 350 ° C. to 550 ° C., depending on the pressure ratio of the compressor 1, these losses would be considerable and would therefore have a strongly negative effect on the entire process.
  • the firing device 41 can also be operated with fuels such as coal or heavy oil that are not or poorly suited for the direct firing of gas turbines.
  • fuels such as coal or heavy oil that are not or poorly suited for the direct firing of gas turbines.
  • a person skilled in the art is familiar with a low-pollutant design of this essentially atmospheric furnace.
  • the presence of the firing device 41 does not mean that the combustion chamber must then necessarily be of a self-igniting type; on the contrary, the combustion chamber 2a can then be designed as “conventional” or self-igniting.
  • Solar heat utilization is not necessarily the optimum. It is assumed below that the high-pressure combustion chamber 2a and the low-pressure combustion chamber 2b are essentially the same at full load Amounts of fuel are fired, that the temperature of the air 12 at the compressor outlet is 500 ° C, that the temperature of the hot gas 14 when it enters the high-pressure turbine 3a is approximately 1300 ° C, and that the compressed air in the process fluid preheater can only be preheated to 900 with solar heat ° C is achieved, this results in a fuel saving of about 25%. Assuming a somewhat idealized overall combined efficiency of, for example, 60%, this results in an "efficiency" of 80% based on the amount of fuel.

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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)
  • High Energy & Nuclear Physics (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne une groupe de turbines à gaz dans lequel le fluide de processus est préchauffé à l'aide d'énergie solaire. Du fluide de processus (12) comprimé dans un compresseur (1) s'écoule côté secondaire dans un échangeur thermique à fluide de processus (31) avant de s'écouler dans une chambre de combustion (2a) à l'état préchauffé. L'échangeur thermique à fluide de processus est intégré à un circuit de préchauffage séparé, côté primaire. Dans le circuit de préchauffage, une soufflerie de recirculation (35) ou une pompe transporte un fluide caloporteur vers un élément d'apport de chaleur solaire (32). Dans ce dernier, le fluide caloporteur est préchauffé et retourné vers l'échangeur thermique à fluide de processus (31) dans lequel la chaleur est transférée au fluide de processus comprimé (12). Un échangeur thermique ultérieur (38) contenu dans le circuit de préchauffage permet l'apport de chaleur non solaire provenant d'une combustion supplémentaire (41) dans le circuit de préchauffage. La régulation adéquate du circuit de préchauffage et de la combustion supplémentaire permet un chauffage supplémentaire, et de maintenir à un niveau élevé et constant la température du fluide de processus préchauffé, comprimé (13), indépendamment du potentiel d'apport de chaleur solaire disponible, une chambre de combustion à allumage automatique pouvant ainsi être utilisée en tant que chambre de combustion haute pression (2a).
PCT/EP2003/050181 2002-06-07 2003-05-21 Groupe de turbines a gaz WO2003104629A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003238526A AU2003238526A1 (en) 2002-06-07 2003-05-21 Gas turbine group

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH9772002 2002-06-07
CH20020977/02 2002-06-07

Publications (1)

Publication Number Publication Date
WO2003104629A1 true WO2003104629A1 (fr) 2003-12-18

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WO (1) WO2003104629A1 (fr)

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WO2007141356A1 (fr) * 2006-06-06 2007-12-13 Francisco Javier Cans Vazquez Procédé thermosolaire de génération d'électricité par transfert d'énergie au débit hydraulique
CN100467974C (zh) * 2006-08-31 2009-03-11 张耀红 太阳能集热发电装置
CN102003359A (zh) * 2010-11-20 2011-04-06 王光顺 一种太阳能复合电站
ITMS20100005A1 (it) * 2010-06-25 2011-12-26 Technical Partners S A S Di Natalia Kozlova & C Centrale termoelettrica elioassistita
CN102305199A (zh) * 2011-07-20 2012-01-04 徐添贵 太阳能发电设备及太阳能连续发电的方法
CN102383881A (zh) * 2010-09-03 2012-03-21 阿尔斯通技术有限公司 蒸汽轮机设备
CN103470461A (zh) * 2013-10-10 2013-12-25 国电龙源电力技术工程有限责任公司 碟式太阳能-燃气蒸汽联合循环发电***
JP2014517207A (ja) * 2011-06-13 2014-07-17 ユーロタービン アクティエボラーグ 発電プラントおよび発電プラント運転方法
CN106523058A (zh) * 2016-12-05 2017-03-22 中冶华天工程技术有限公司 一种基于钢厂饱和蒸汽优化利用的汽动鼓风机***
US9726155B2 (en) 2010-09-16 2017-08-08 Wilson Solarpower Corporation Concentrated solar power generation using solar receivers
US10876521B2 (en) 2012-03-21 2020-12-29 247Solar Inc. Multi-thermal storage unit systems, fluid flow control devices, and low pressure solar receivers for solar power systems, and related components and uses thereof

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