WO2012143272A1 - Système de transfert de chaleur et procédé pour chauffer un gaz de travail - Google Patents

Système de transfert de chaleur et procédé pour chauffer un gaz de travail Download PDF

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Publication number
WO2012143272A1
WO2012143272A1 PCT/EP2012/056518 EP2012056518W WO2012143272A1 WO 2012143272 A1 WO2012143272 A1 WO 2012143272A1 EP 2012056518 W EP2012056518 W EP 2012056518W WO 2012143272 A1 WO2012143272 A1 WO 2012143272A1
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WO
WIPO (PCT)
Prior art keywords
turbine
heat exchanger
gas
working gas
heat
Prior art date
Application number
PCT/EP2012/056518
Other languages
German (de)
English (en)
Inventor
Holger HERTWIG
Original Assignee
Siemens Aktiengesellschaft
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 Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Publication of WO2012143272A1 publication Critical patent/WO2012143272A1/fr

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Classifications

    • 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
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • F02C6/16—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads for storing compressed air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • 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
    • 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
    • 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
    • F03G6/02—Devices for producing mechanical power from solar energy using a single state working fluid
    • F03G6/04—Devices for producing mechanical power from solar energy using a single state working fluid gaseous
    • 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
    • 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
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids

Definitions

  • the present invention relates to a cageübertrageranord ⁇ tion for heating a working gas for a turbine of a compressed air storage power plant.
  • the present invention relates to a compressed air storage power plant.
  • the present invention relates to a method for heating a working gas for a turbine of a compressed air ⁇ memory power plant.
  • renewable energy sources such as by solar energy or wind energy ⁇ .
  • the power generated by power plants using renewable energy sources fluctuates due to the effects of weather, such as Windän ⁇ alteration or fluctuating sunshine durations.
  • a surplus of energy produced is temporarily stored and, if necessary, retrieved for power generation.
  • Known storage power plant types are, for example, pumped storage power plants and compressed air storage power plants.
  • pumped storage power plant water is pumped with the surplus energy generated in a high-level reservoir. When energy is needed, the water is removed from the high-level NEN memory via downpipes further downstream turbines supplied to operate a power generator.
  • a compressed air storage (CAES) power plant operates with the excess energy a compressor that pumps in compressed air in a pressure space, such as an underground cavern. If there is a higher power demand, the compressed air from the pressure space is used to operate a turbine, which in turn operates a coupled power generator.
  • a compressor that pumps in compressed air in a pressure space, such as an underground cavern. If there is a higher power demand, the compressed air from the pressure space is used to operate a turbine, which in turn operates a coupled power generator.
  • a conventional process of a compressed air storage ⁇ cherkraftwerks is shown.
  • the working fluid for example compressed air
  • the working fluid is supplied to a conventional heat exchanger 500 from a pressure chamber 501, such as an underground cavity, before entering a turbine 502.
  • the working fluid when entering the heat exchanger 500, has a first inlet temperature T E i.
  • the heat exchanger 500 is a first heat energy Q to , i supplied.
  • the object is achieved by a heat exchanger arrangement for heating a working gas for a turbine of a compressed air ⁇ memory power plant, by a compressed air storage power plant and by a method for heating a working gas for a turbine of a compressed air storage power plant according to the inde pendent ⁇ claims.
  • a heat exchanger arrangement for heating a working gas for a turbine of a storage power plant, in particular a compressed air storage power plant.
  • Heat ⁇ trageranaku has a first gas inlet, a first outlet, a second gas intake and a second gas outlet.
  • the first gas inlet is coupled to a pressure chamber, so that a working gas with a first input ⁇ temperature from the pressure chamber to the heat exchanger assembly can be fed.
  • the first gas outlet is LAD ⁇ Pelbar with the turbine, so that the working gas can be supplied with a first Auslasstempe ⁇ temperature of the heat exchanger arrangement to the turbine.
  • the second gas inlet can be coupled to the turbine, so that the working gas can be supplied to the turbine of the heat exchanger arrangement with a second inlet temperature.
  • the second gas outlet can be coupled to the turbine, so that the working gas can be supplied to the turbine with a second outlet temperature from the heat exchanger arrangement.
  • a heating means can be supplied in such a way that the working gas can be heated from the first inlet temperature to the first outlet temperature. The working gas is further heated from the second input temperature to the second outlet temperature by means of a heating means.
  • a compressed air storage power plant has a pressure space, a turbine and the above-described heat exchanger arrangement.
  • a method for heating a working gas for a Turbi ⁇ ne of a compressed air energy storage power plant is described.
  • a first working gas having a first inlet temperature is supplied from a pressure space to a first gas inlet of a heat exchanger arrangement.
  • the working gas is heated from the first inlet temperature to the first outlet temperature by means of a heating means in the heat exchanger assembly.
  • the working gas is supplied to the turbine at a first outlet temperature from the heat exchanger assembly.
  • the working ⁇ gas is heated by the second input temperature to the second outlet by means of a heating medium.
  • the Ar ⁇ gas is supplied with a second outlet temperature of the heat exchanger assembly to the turbine.
  • a compressed air storage power plant which has the above-described pressure chamber, the turbine and the above-described heat exchanger arrangement.
  • the heat exchanger assembly may include one or more heat transfer devices (recuperators).
  • a recuperator is used to preheat the working gas by means of a Wär ⁇ meffens or by several different heat medium.
  • a working gas from a pressure chamber, such as from a
  • the working gas from the pressure chamber has a high pressure.
  • the working gas relaxes, so that the energy of the working gas is converted into mechanical work becomes.
  • the turbine in turn drives a power generator, which generates electricity. If less power is required, the working gas is fed into the pressure chamber, for example by means of a compressor, so that the pressure in the pressure chamber increases. In the pressure chamber, the working gas is stored under high pressure.
  • the turbine has, for example egg ⁇ ne first turbine stage (resp. A first thermodynamic relaxation area), a second turbine stage (or a second thermodynamic relaxation area) or more additional turbine stages (or more thermodynamic Ent ⁇ voltage ranges) on.
  • the second turbine stage is downstream of the first turbine stage with respect to a flow direction of the working gas in the turbine downstream of the first Turbi ⁇ ne or arranged.
  • the working gas is heated in the heat exchanger assembly of the first input temperature (temperature of the working gas in the pressure chamber) to a first outlet temperature, which is higher than the first input Tempe ⁇ rature, by means of a heating means.
  • the working gas for example after the first or the second turbine stage of the turbine, removed and fed to the second gas inlet of the heat exchanger assembly.
  • This interim removal of the working gas from the turbine, the interim heating and the subsequent return of the working gas with the second outlet temperature ⁇ tur leads to an increase in the efficiency of the turbine.
  • the pressure of the working gas between the Ab ⁇ draw-off from the turbine, the supply to the second gas inlet and the supply of the heated working gas is in the second gas outlet, which in turn gekop ⁇ pelt with the turbine, kept almost constant. With such Zvi ⁇ rule warming the efficiency of the turbine is increased.
  • the intermediate heating can be carried out at several turbine stages of the turbine.
  • the working gas can be taken out and fed again to the heat exchanger arrangement.
  • the supplied working gas is heated after ⁇ and supplied as supply air back to the turbine. This increases the efficiency of the turbine.
  • more heat can be drawn into the heat medium in the heat exchanger arrangement and thus an efficient heating of the working gas can be made possible.
  • the heating means can for example be taken from a heat-generating ⁇ the device.
  • the heating means is for example an exhaust gas of a gas turbine.
  • the heat ⁇ meffen be a heated oil or heated water, which is warmed up, for example by solar power.
  • the heat exchanger arrangement further has a further second gas inlet, which can be coupled to the turbine, so that the working gas can be supplied to the heat exchanger arrangement with a further second inlet temperature from the turbine.
  • the heat exchanger arrangement in a further second gas outlet which can be coupled with the turbine, so that the working gas with egg ⁇ ner further second outlet of the heat exchanger arrangement can be fed to the turbine.
  • the heating means can be supplied in such a way that the working gas can be heated from the further second inlet temperature to the further second outlet temperature.
  • a plurality of taps at the turbine can be set at ⁇ play to tap working gas and supplied to the heat exchanger arrangement. The tapped working gas is heated in each case in the heat exchanger arrangement and then fed back to the turbine.
  • the heat exchanger arrangement has a first heat exchanger device.
  • the first heat transfer device has the first gas inlet, the first gas outlet and a first heat medium inlet.
  • the heat exchanger arrangement has a second or a multiplicity of further second heat exchanger devices, which in each case has the second gas inlet, the second gas outlet and a second heat inlet.
  • the first heat transfer device may be structurally separate from the second heat transfer device.
  • the first and the second Heat Transf ⁇ gervoriques may be co-located in a common housing.
  • the first heat medium inlet and the second heat medium inlet can be coupled to a common heat-generating device.
  • the first and the second are configured to share a common heat medium, which is heated by the common blazeer ⁇ forming apparatus.
  • a gas turbine may supply hot exhaust gas to the first heat transfer device and the second heat transfer device.
  • the first heat exchanger device has a heat medium outlet for discharging the heating medium with a first waste heat.
  • the furnishedffenauslass and the second heat medium inlet are coupled together such that the heating means with the first waste heat can be supplied to the second heat medium inlet.
  • the first heat medium inlet can be coupled to the heat-generating device and the second heat medium inlet can be coupled to a further heat-generating device.
  • the first must be operated with a second heat medium.
  • the exhaust gas of a gas turbine can be used as a heat-generating device.
  • exhaust gas of a white ⁇ direct gas turbine and / or hot oil or hot water may, for example, which has been heated more than blazeer ⁇ generating device in a solar power plant, are used.
  • the first gas outlet of the heat exchanger arrangement is coupled to the turbine such that the working gas can be supplied to the first outlet temperature of the first turbine stage.
  • the second gas outlet of the heat exchanger arrangement is coupled to the turbine such that the working gas with the second inlet temperature between the first turbine stage and the second turbine stage can be removed and the heat transfer ⁇ ranix can be fed.
  • the second gas outlet of the heat exchanger assembly ⁇ is coupled to the turbine, that the working gas with the second outlet temperature before the second turbine stage can be fed.
  • the working gas may be mixed with the second exhaust Temperature can also be supplied to a subsequent, arranged after the second turbine stage, turbine stage.
  • a working gas is taken on the one hand from the pressure chamber and heated in the heat exchanger assembly.
  • a working gas is taken on the one hand from the pressure chamber and heated in the heat exchanger assembly.
  • the same heat exchanger arrangement is also another
  • the heat exchanger arrangement is formed from, for example, two or more heat exchanger devices, with a first heat exchanger device (a first recuperator) allowing initial heating of the working gas.
  • a first heat exchanger device a first recuperator
  • a wide ⁇ re Edmontonellervorraum another recuperator
  • receives at the bled from the turbine working gas is heated and the turbine, this leads to the working gas again.
  • this opens up the possibility of operating each heat exchanger device with an associated heat source (heat generating device).
  • the one heat ⁇ transmission device by means of a gas turbine and the other heat exchanger device by means of a solar power plant be ⁇ driven.
  • this opens the possibility that the various heat transfer devices can operate at different temperature levels, since each heating means can have a different temperature.
  • the heat exchanger arrangement ⁇ may comprise a plurality of gas inlets which receive the working gas from the pressure space or from different turbine stages of the turbine to heat the working gas.
  • FIG. 1 shows a schematic representation of a compressed-air storage power plant with a heat exchanger arrangement according to an exemplary embodiment of the present invention
  • Fig. 2 shows air-storage power station is a schematic representation of a printer in which the voltage aboard undergraduatetrageranord ⁇ a plurality of second gas inlets and a plurality of second Gasausläs ⁇ se has guide of the present invention according to an exemplary off;
  • FIG. 3 shows a schematic representation of a compressed air storage power plant with a heat exchanger arrangement, which has a first heat exchanger device and a second heat exchanger device according to an exemplary embodiment of the present invention
  • FIG. 4 shows a schematic representation of a compressed air storage power plant according to an exemplary exporting ⁇ approximate shape of the present invention wherein a heat exchanger arrangement a first compartmentübertragervorraum and egg ne second heat transfer device, which are coupled together; and
  • FIG. 5 shows a schematic representation of a conventional heat exchanger arrangement for a turbine.
  • Fig. 1 shows a heat exchanger arrangement 100 for heating a working gas for a turbine 130 of a Druck Kunststoffspei ⁇ cherkraftwerks 120.
  • a working gas can be taken from a pressure ⁇ space 160, such as an underground cavity and the heat exchanger arrangement 100 to a first gas inlet first with a Temperature T E i be supplied.
  • the heat exchanger assembly 100 is coupled to a heat generating device 140. From the heat generating device 140, a first heat energy supply Q zu , i can be provided.
  • a heat medium such as hot water or hot exhaust gas be ⁇ riding provided a gas turbine, the first heat medium inlet 103rd
  • the working gas passes first to the pressure chamber 160, the heat exchanger arrangement 100 and is discharged to a first training outlet temperature T A i to the first gas outlet 111 of the heat ⁇ transmitter arrangement 100th
  • the working gas is supplied to the turbine 130 at the first outlet temperature T A i.
  • the working gas passes through the individual turbine stages I to III in the direction of flow until it finally flows out of the turbine 130.
  • the energy of the working gas is converted into mechanical ⁇ cal work by means of the turbine 130 and thereby a generator 150, in particular for power generation, operated.
  • the turbine 130 is at least partially removed from the working gas at the second inlet temperature T E 2 and supplied to a second gas inlet 102 of the heat exchanger arrangement 100.
  • the working gas passes through again ⁇ around the heat exchanger arrangement 100 and heated to a second outlet temperature T A 2. From a second gas outlet 112, the working gas with the second outlet temperature TA2 of the turbine 130 is supplied again. This intermediate heating of the working gas increases the efficiency of the turbine 130.
  • the turbine 130 includes a first turbine stage I, a second turbine stage II, and a third turbine stage III (or another plurality of turbine stages).
  • the turbine stages I to III are each arranged successively in the flow direction of the working gas through the turbine 130.
  • the working gas which is partially removed from the pressure ⁇ space 160 and is provided after heating of the first gas outlet 111 with a first outlet temperature T A i, is generally the first turbine stage I supplied.
  • the tapping of the working gas and the supply to the second gas inlet 112 of the heat exchanger assembly 100 usually takes place in one of the following turbine stages II, III. For example, the working gas between see the first turbine stage I and the second Turbinenstu ⁇ Fe II taken and fed to the second gas inlet 102.
  • the working gas After heating of the working gas from the second inlet temperature T E 2 to the second outlet temperature T A 2, the working gas is warmed ⁇ it provides to the second outlet 112 and again overlapge- the turbine 130 is supplied.
  • the working gas with the second outlet temperature T A 2 example, ⁇ near the place of removal, that is supplied in the above example between the first turbine stage I and the second turbine stage II.
  • the heated working gas can also be supplied to a subsequent turbine stage, for example between the second turbine stage II and the third turbine stage III.
  • the heating medium flows through the heat exchanger arrangement 100 and leaves it with a first waste heat Q a b, i.
  • FIG. 2 shows a further exemplary embodiment of the present invention, in which the working gas is taken from the turbine 130 at several points and is heated up by means of the heat exchanger arrangement 100.
  • the working gas having a first inlet temperature T E i from the pressure chamber 160 is made available to the first gas inlet 101 of the heat exchanger arrangement 100.
  • the heat exchanger arrangement 100 heated by the heating medium, the Ar ⁇ beitsgas to the first outlet temperature T A i and makes the working gas ⁇ ses ready the first gas outlet 111th From the first gas outlet 111, the thus-heated working gas is supplied to the first turbine stage I.
  • the heating means is again provided by a heat generating device 140 and supplied to the heat medium inlet 103 with a first heat energy Qzu.
  • the working gas is taken from the turbine 130.
  • This working gas is provided at a second inlet temperature T E2 at the second gas inlet 102 of the heat exchanger arrangement 100 and heated therein.
  • the working gas has the second outlet temperature T A2 , which is higher than the second inlet temperature T E2 .
  • the working gas is supplied to the turbine 130 at the second outlet temperature T A2 .
  • the thus heated working gas in the vicinity of the working gas sampling supplied, that is also between the first turbine stage I and the second turbine stage II.
  • the pressure of the working gas is formed between the Ent ⁇ acquisition after the first turbine stage I and re Alloca- tion of the second turbine stage II kept almost constant, thus avoiding energy loss.
  • Fig. 2 shows a further removal (a part of) the working gas to the second turbine stage II.
  • the working ⁇ gas is again drawn off after the second turbine stage II and supplied with a third inlet temperature T E 3 the further second gas inlet 201 of the heat exchanger arrangement 100th
  • the heating medium heats the working gas to the third outlet temperature T A 3.
  • the working gas with the third outlet temperature T A 3 between the second turbine stage II and the third turbine stage III is supplied.
  • a common heat means heat exchanger assembly 100 may inter-warm the working gas between a plurality of turbine stages I-III to thereby produce high turbine 130 efficiency.
  • FIG. 3 shows a further exemplary embodiment of the present invention, in which the heat exchanger arrangement 100 has a first heat exchanger device 301 and a second heat exchanger device 302.
  • the first heat exchanger device draws the working gas with the first inlet temperature T E i from the pressure chamber 160. Furthermore, a heat ⁇ medium with a first heat energy Q to , i from the summeerzeu ⁇ ing device 140 at the first heat inlet 103.
  • the working gas flows between the first gas inlet 101 to the first gas outlet 111 and is heated from the first input temperature T E i by means of the heating means to the first outlet temperature T A i. From the first gas outlet 111, the working fluid flows to the turbine 130 and in particular to the first turbine stage I, to operate the Turbi ⁇ ne 130th
  • FIG. 3 shows a second heat transfer device 302.
  • the heat transfer device 302 has the second gas inlet 102 and the second gas outlet 112.
  • the working gas can be tapped and provided by means of the second input temperature T E 2 the second gas inlet 102. After heating the working gas to the second outlet temperature T A 2, the working gas is provided to the second gas outlet 112 and supplied to the turbine 130 again.
  • the working gas is taken from the second turbine stage II and fed again to the subsequent third turbine stage III.
  • the second heat ⁇ tragervoriques 302 may let through a second choirffenein- 303, for example, the heating means with the first heat ⁇ power supply Q to refer i from the heat generating device 140th
  • one and the same heat generating device 140 may supply a plurality of heat transfer devices 301, 302 with heat.
  • a further heat-generating device 340 may be provided, which provides a further heat means with a second heat energy Q to , 2 the further heat medium inlet. After heating the working gas from the second input temperature T E 2 to the second outlet temperature T A 2, the further heating means with a second waste heat Q a b, 2 discharged from the second choirübertrager- device 302.
  • the heat-generating device 140 may represent a gas turbine and supply hot exhaust gas to the first heat exchanger device 301.
  • the further heat generating device 340 may represent, for example a so ⁇ larkraftwerk, and by solar energy a further heating means, such as to heat for example water or oil, and this out as a second thermal energy input Q to, 2 of the second jacketübertragervorraum 302nd
  • Fig. 4 shows a further exemplary embodiment, wel ⁇ che substantially the same features of the execution form of Fig. 3 has.
  • the heat exchanger assembly 100 includes the first heat transfer device 301 and the second heat transfer device 302.
  • the heat medium after it heats the working gas in the first Wär ⁇ meübertragervortechnik 301 with a first waste heat Qab, i dissipated.
  • the cardboardstoffauslass 401 and the second heat medium inlet 303 are in such a manner gekop ⁇ pelt that the heating means with the first waste heat Q ab, i the second heat medium inlet 303 is fed.
  • the heating means with the first waste heat Q a b, i from the first heat exchanger ⁇ device 301 is thus supplied as a heating means with a second heat energy Q to , 2.
  • the heat with ⁇ tel is withdrawn more heat energy in the overall process and the unge ⁇ took advantage of waste heat reduces.
  • the overall efficiency of the heat ⁇ transfer assembly 100 and thus the compressed air storage power ⁇ plant 120 is thereby increased.

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  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
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  • Physics & Mathematics (AREA)
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  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

La présente invention concerne un système de transfert de chaleur (100) pour chauffer un gaz de travail pour une turbine (130) d'une centrale de stockage par air comprimé (120). Le système de transfert de chaleur (100) présente une première entrée de gaz (101) qui peut être accouplée à une chambre de pression (160) de la centrale de stockage par air comprimé (120) afin qu'un gaz de travail ayant une première température d'entrée (TE1) puisse être amené de la chambre de pression (160) au système de transfert de chaleur (100). Le système de transfert de chaleur (100) présente également une première sortie de gaz (111) qui peut être accouplée à la turbine (130) afin que le gaz de travail ayant une première température de sortie (TA1) puisse être amené du système de transfert de chaleur (100) à la turbine (130). Le système de transfert de chaleur (100) présente également une deuxième entrée de gaz (102) qui peut être accouplée à la turbine (130) afin que le gaz de travail ayant une deuxième température d'entrée (TE2) puisse être amené de la turbine (130) au système de transfert de chaleur (100). Le système de transfert de chaleur (100) présente également une deuxième sortie de gaz (112) qui peut être accouplée à la turbine (130) afin que le gaz de travail ayant une deuxième température de sortie (TA2) puisse être amené du système de transfert de chaleur (100) à la turbine (130). Un fluide caloporteur peut être fourni de telle manière que le gaz de travail puisse être chauffé de la première température d'entrée (TE1) à la première température de sortie (TA1) et que le gaz de travail puisse être chauffé de la deuxième température d'entrée (TE2) à la deuxième température de sortie (TA2).
PCT/EP2012/056518 2011-04-20 2012-04-11 Système de transfert de chaleur et procédé pour chauffer un gaz de travail WO2012143272A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011007753.7 2011-04-20
DE102011007753A DE102011007753A1 (de) 2011-04-20 2011-04-20 Mehrdruck CAES-Prozess

Publications (1)

Publication Number Publication Date
WO2012143272A1 true WO2012143272A1 (fr) 2012-10-26

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JPH0354327A (ja) * 1989-07-20 1991-03-08 Nkk Corp 余剰電力利用システム
DE4410440A1 (de) * 1994-02-03 1995-08-10 Israel Electric Corp Ltd Druckluftenergiespeicherverfahren und -system
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CN111396162B (zh) * 2020-04-20 2024-05-07 贵州电网有限责任公司 一种高效率的先进压缩空气储能系统及方法

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