US20010042367A1 - Method for operating a power plant including a co2 process - Google Patents

Method for operating a power plant including a co2 process Download PDF

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Publication number
US20010042367A1
US20010042367A1 US09/255,712 US25571299A US2001042367A1 US 20010042367 A1 US20010042367 A1 US 20010042367A1 US 25571299 A US25571299 A US 25571299A US 2001042367 A1 US2001042367 A1 US 2001042367A1
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Prior art keywords
setup
turbine
gas
circulation gas
water
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Abandoned
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US09/255,712
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English (en)
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Hans Ulrich Frutschi
Hans Wettstein
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Alstom SA
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Alstom SA
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Assigned to ASEA BROWN BOVERI AG reassignment ASEA BROWN BOVERI AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FRUTSCHI, HANS ULRICH, WETTSTEIN, HANS
Publication of US20010042367A1 publication Critical patent/US20010042367A1/en
Assigned to ALSTOM reassignment ALSTOM ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ASEA BROWN BOVERI AG
Priority to US10/852,656 priority Critical patent/US7089743B2/en
Abandoned legal-status Critical Current

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    • 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
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas
    • F01K21/042—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas pure steam being expanded in a motor somewhere in the plant
    • 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
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas
    • F01K21/047—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas having at least one combustion gas turbine
    • 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
    • F02C1/10—Closed 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
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery
    • 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
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a method for operating a CO 2 plant according to the preamble of claim 1 .
  • the invention also relates to setups for carrying out this method.
  • the supply of energy is, at the present time, determined by the use of fossil fuel energies in internal combustion engines, the highly diluted CO 2 being disposed of into the atmosphere.
  • one object of the invention is to provide a novel method and a setup of the type initially mentioned, to dispose in an environmentally friendly way of the CO 2 which occurs, and, at the same time, here, the object of the invention is to eliminate the atmospheric nitric oxides which likewise occur.
  • the method proceeds from a CO 2 process with internal combustion, in which, in order to heat the CO 2 mass located in the circuit, said heating preferably being carried out by means of a gaseous fuel, only that necessary oxygen quantity which is required for oxidizing this very fuel is supplied.
  • the degree of charging and, consequently, the power of the process can be regulated continuously by means of an appropriate extraction of CO 2 from the circuit at a suitable point.
  • Another essential advantage of the invention is to be seen in that the method can be carried out by means of several types of gas turbine setups, the setup described in each case constituting a specific optimum solution as a function of the predetermined parameters.
  • Another essential advantage of the invention is to be seen in that it provides a remedy against the fact that all air-breathing internal combustion engines also generate nitric oxides which act as air pollutants and the production of which requires costly measures to combat it, not least in light of the internationally restrictive laws on permissible pollutant emissions. Since no atmospheric nitrogen enters the flame in the recirculation mode with pure oxygen, NO x is also not generated. Admittedly, if the fuel carries bound nitrogen with it, a slight formation of NO x must be expected. However, since the excess gas represents a much smaller quantity than the exhaust gas in the air mode, its retreatment is simpler and less expensive.
  • FIG. 1 shows a gas turbine with a closed circuit, with heat exchangers for the separation of water and CO 2 ,
  • FIG. 2 shows a gas turbine according to FIG. 1 with additional compression intermediate cooling
  • FIG. 3 shows a gas turbine with a closed circuit and with a steam circuit
  • FIG. 4 shows a setup according to FIG. 3 with additional compression intermediate cooling
  • FIG. 5 shows a setup according to FIG. 3, a plurality of steam turbines being integrated into the steam circuit
  • FIG. 6 shows a setup according to FIG. 4, a plurality of steam turbines being integrated into the steam circuit
  • FIG. 7 shows a further gas turbine setup with a plurality of recuperators and intermediate coolers
  • FIG. 8 shows a gas turbine process with an isothermal compressor and with recuperation
  • FIG. 9 shows a piston engine process with a final purpose according to one of the preceding setups.
  • FIG. 1 shows a gas turbine with a closed circuit.
  • This gas turbine or gas turbo set consists, in terms of assemblies, of a compressor unit 1 , of a generator 4 coupled to this compressor unit, of a turbine 2 coupled to the compressor unit and of a combustion chamber 3 acting between the compressor unit 1 and turbine 2 .
  • the turbomachines 1 and 2 can be coupled by means of a common shaft 5 .
  • the circuit medium 6 which is sucked in by the compressor unit 1 and which is predominantly CO 2 , flows, after compression has taken place, into the combustion chamber 3 , in which the heat treatment of this medium is carried out, said medium then acting as hot gases 10 on the turbine 2 .
  • the compressor unit 1 may also, via a starting flap 7 , suck in air 8 , the nitrogen of which is discharged successively via an outlet flap 40 as said nitrogen is displaced by CO 2 which occurs.
  • a first secondary stream 11 is introduced as a coolant into the cooling paths of the assemblies to be cooled.
  • the combustion chamber 3 and turbine 2 are the components primarily to be cooled, and cooling can be carried out in closed and/or open flow paths.
  • a second secondary stream 12 of the order of magnitude of 4-8% of the entire compressed circulation gas is additionally branched off. In this case, this compressed CO 2 has the pressure which is necessary for condensation.
  • this CO 2 fraction is discharged from the closed circuit.
  • This circulation gas consists predominantly of CO 2 , but may possibly also contain parasitic gases which have been entrained with the oxygen and fuel and, during startup, with air, as well as transformation products of said gases, for example NO x .
  • this condensed CO 2 mass flow 15 is discharged in order to be disposed of, for example and/or preferably on the ocean floor or into a worked-out deposit of natural gas.
  • This disposal at a suitable location by suitable means constitutes a quick and lasting solution to the problem of the greenhouse effect caused by the constant emission of gaseous CO 2 into the atmosphere.
  • the parasitic gases are likewise separated in cooperation with said cooler 14 , and this very small mass flow 16 may be subjected to further separation or be discharged into the atmosphere.
  • the oxygen quantity 18 produced in an air separation plant 17 is recompressed in a compressor 19 and introduced via a regulating member 20 to the combustion chamber 3 .
  • a fuel 21 which is appropriately coordinated via a regulating member 22 and which is preferably natural gas, or else other hydrocarbons or CO or mixtures of these, also flows into the combustion chamber 3 , the heat treatment of the compressed circulation gas 9 being carried out by means of the added oxygen quantity 18 .
  • the hot gas coming from the combustion chamber is subsequently expanded into the downstream turbine 2 .
  • the exhaust gases 23 flowing out of the turbine 2 are led through a heat exchanger 24 before being supplied once again for the compression which has already been described.
  • the water 25 which occurs is separated from this heat exchanger 24 via a regulating member 26 .
  • the setup shown here is, strictly, a quasi closed circuit which is designed to be pressure resistant, vacuum resistant circuit routing also being possible in various operating modes.
  • the excess gas valve 13 By the excess gas valve 13 being throttled or opened, the circuit is charged or discharged automatically, the circulating mass flow and the power increasing correspondingly.
  • this valve 13 When this valve 13 is opened, the pressure in the circuit falls, and the vacuum may be generated in the return.
  • the plant has approximately constant efficiency in the entire pressure mode, that is to say in a design pressure range with respect to the return of 0.5 to 5 bar in the power range of 10-100%. In the lower pressure range, the condensation temperature in the heat exchanger 24 falls, thus also causing the efficiency to rise slightly.
  • FIG. 2 differs from FIG. 1 in that, here, one or more intermediate cooling stages are carried out in cooperation with compression.
  • Such intermediate cooling stages during compression are considered to be process improvements which are provided for the purpose of an efficiency rise and/or a power increase.
  • intermediate cooling results in a flattening of the efficiency curve and is particularly useful in plants with high pressure ratios.
  • the intermediate cooling illustrated here is the simplest possible setup, in that the circulation medium 6 to be compressed flows, downstream of a first precompressor stage 1 a / 27 , through an intermediate cooler 28 .
  • the intermediately compressed and cooled medium 29 is subsequently finish compressed in a second compressor stage 1 b .
  • This intermediate cooling may also be designed in such a way that a condensed part quantity 30 of the CO 2 can already be discharged here. Further intermediate cooling, which results in a considerable rise in the efficiency of the plant and better condensing-out of the CO 2 to be discharged, can be achieved by aiming for isothermal or quasi-isothermal cooling in the region of the compression process.
  • water injections are carried out in the compressor, these being arranged in each case in the plane of the guide blading and extending over the entire height of the compressor duct through which the flow passes. This measure makes it possible to dispense with additional components having pressure losses, this precaution resulting in the possibility of injecting the water according to the particular flow.
  • FIG. 3 shows a gas turbo set with a steam circuit.
  • the gas turbo set operates in a closed circuit.
  • the exhaust gases 23 from the turbine 2 flow through a waste-heat steam generator 31 , in which the counterflow of a water quantity 33 provided by a feed pump generates a steam quantity 34 which is used mainly for acting on a steam turbine 32 .
  • the expanded steam is subsequently introduced via a regulating member 36 into the combustion chamber 3 , and, if required, a part quantity 37 of this expanded steam is branched off downstream of said regulating member 36 and introduced into the turbine 2 .
  • This introduction is preferably employed for cooling the parts of this turbomachine which are subjected to high thermal load and is then fed into the flow.
  • the efficiency can be further improved if the steam in the waste-heat steam generator 31 is generated at as high a pressure as possible and is discharged via a steam turbine with power output to the main shaft 5 of the gas turbo set or to a separate generator not illustrated in any more detail.
  • a steam turbine with power output to the main shaft 5 of the gas turbo set or to a separate generator not illustrated in any more detail.
  • Such a setup is shown and described in more detail with reference to FIGS. 5 and 6.
  • a part quantity 39 of the circulation gas 38 cooled in the waste-heat steam generator 31 said part quantity being regulated via an outlet flap 40 , is branched off upstream of the heat exchanger 24 belonging to the closed or quasi closed circuit.
  • FIG. 4 starts from a basic setup according to FIG. 3 and, as regards intermediate cooling in the region of the compressor unit 1 , follows FIG. 2. The statements made in respect of the two figures mentioned are also applicable here and are an integral part of this FIG. 4.
  • FIG. 5 is based closely on FIG. 3, here the steam turbine 41 , operating in cooperation with the waste-heat steam generator 31 , being coupled to the main shaft 5 of the gas turbo set, the power output taking place directly.
  • the steam 42 expanded from this steam turbine 41 is introduced (reference 44 ) via a regulating member 43 into the combustion chamber 3 and/or into the turbine 2 .
  • the power density thereby rises sharply.
  • This steam may, of course, also be introduced at other locations in the circuit of the gas turbo set.
  • it is possible, by means of this steam 42 for those parts of said assemblies 2 / 3 which are subjected to high thermal load to be cooled in the closed and/or open flow path.
  • the steam 34 can be generated directly at the necessary pressure or else can be expanded to a higher pressure and then, via the regulating member 43 already mentioned or correspondingly via the steam turbine 41 , to the pressure level required for injection.
  • the setup shown here has, for the charged mode, additional extraction of an exhaust gas quantity 47 from the waste-heat steam generator 31 and extraction of a further exhaust gas quantity 45 downstream of the waste-heat steam generator 31 .
  • Both exhaust gas quantities 45 / 47 act on an expander 46 and, after this, are discharged 48 , their reuse being ensured specifically in each individual case.
  • an optimum pressure for charging the circuit can be set via this expander 46 , and, in such a case, quantity regulation must be provided.
  • this pressure regulation if required, interdependent regulation of the pressure of the main steam quantity 34 can also be achieved.
  • the setup just described may also be designed along the lines of a combined plant, the gas turbine circuit shown according to this FIG. 5, whether with or without intermediate cooling, forming the basic setup for a combined plant, one of these being disclosed in EP-0,767,290 A1, and this publication forming an integral part of the present description.
  • FIG. 6 starts from a basic setup according to FIG. 5 and, as regards intermediate cooling in the region of the compressor unit 1 , follows FIG. 2. The statements made with regard to the two figures mentioned are also applicable here and are an integral part of this FIG. 6.
  • gas turbo set according to one of FIGS. 1 to 6 can be readily replaced by a sequentially fired plant according to EP-0,620,362 A1, this publication forming an integral part of the present description.
  • FIG. 7 shows a partly closed gas turbine process which is charged with CO 2 and which is operated in such a way that the fuel 21 , here as CH 4 , and the associated oxidant 18 , here as O 2 , are supplied to the combustion chamber 3 , the aim here, too, being to separate at a suitable location the excess CO 2 which has occurred and the H 2 O.
  • CO 2 is a relatively heavy gas. Its specific heat changes, in the semiideal gas state, from c p 0.84 at 15° C.
  • the first precompressor stage 1 a (LP compressor) is still in the undistorted gas, whilst the downstream intermediate cooler 50 is near the gas/steam/liquid boundary curve and, as a function of pressure, has extremely high specific heat.
  • the precompressed circulation medium 27 then flows through a recuperator 51 and, subsequently, the intermediate cooler 50 already mentioned, before it flows into the second compressor stage 1 b , in which final compression is carried out.
  • the excess CO 2 from the process can be extracted in liquid form in a very simple way by means of moderate further cooling or heat discharge.
  • the isobaric section in the region of the intermediate cooler 50 can be displaced into the wet zone, so that the excess CO 2 is then already condensed.
  • the finally compressed circulation gas 12 then flows via parallel lines 54 , 55 through recuperators 51 , 53 , likewise connected in parallel, in which combined intermediate preheating takes place.
  • Final preheating of the circulation gas 56 then takes place in a downstream recuperator 52 , through which the exhaust gases 23 from the turbine 2 flow.
  • these exhaust gases 23 are also relevant to the recuperator 53 already mentioned, whereas the recuperator 51 , connected in parallel to the lastmentioned recuperator 53 , has only the precompressed circulation gas 27 flowing through it.
  • FIG. 8 shows a gas turbine process with a downstream steam circuit, here the setup being extended by an isothermal compressor and recuperation.
  • this setup makes use of an isothermal compressor 49 operated by pressurized water or a gradient.
  • this isothermal compressor can at the same time perform the function of the recooler. There is therefore no need for a bladed conventional compressor.
  • circulation gas can be converted into a precompressed state within the framework of isothermal compression, in which the circulation gas can be comparatively highly compressed, without reaching high compression temperatures, so that, in the extreme case, said gas is available directly for driving the gas turbine, at least with a conventional compressor being avoided and therefore without the need to drive the compressor by means of the turbine.
  • This isothermal compression ensures that the maximum possible heat supply does not decrease with an increasing pressure ratio. The power density therefore remains high even in the case of a high pressure ratio. Moreover, recuperation is always possible. It is, of course, possible to deliver isothermally precompressed circulation gas to a conventional high-pressure compressor stage.
  • Such an isothermal compressor offers improved properties as regards utilizing the waste heat from the exhaust gases emerging from the turbine, especially since the temperature level of the highly compressed air, after it has emerged from a high-pressure compressor stage possibly located downstream of isothermal compression, is lower than in the case of compressors of conventional gas turbine plants.
  • a vertically running flow duct is provided, which has an upper inlet region and a lower outlet region, the diameter of the flow duct being greater in the region of the inlet than the diameter in the region of the outlet.
  • a water-atomizing nozzle arrangement Arranged in the inlet region of the flow duct is a water-atomizing nozzle arrangement which generates as great a number of very small water drops as possible in a large quantity.
  • water atomization in the inlet region of the flow duct, it is likewise necessary to ensure that the atomized water is thoroughly mixed with the circulation gas. Due to gravitation, the circulation gas/water mixture generated in this way falls through the flow duct, the inner contour of which is designed in such a way that the region near the inlet orifice has a largely uniform cross-sectional area along the vertical extent of the flow duct, so that the velocities of the flow of the circulating gas and of the falling cloud of drops are equated as quickly as possible by pulse transmission.
  • the cross section of the fall well is narrowed somewhat more slowly, as compared with the lastmentioned formula.
  • the profile of the narrowing is selected as just sufficient to ensure that the braking action of the circulation gas on the cloud of drops leads to a constant relative velocity difference between the drops and the circulation gas.
  • the provision of the compressed circulation gas is initiated by a water pump 58 which is located on the turbine rotor shaft 5 , that is to say is driven by the turbine 2 .
  • the water 59 brought to pressure, flows into an injector 60 , in which compression of the exhaust gas 23 from the turbine 2 , said exhaust gas previously having been cooled by means of a recuperator 64 , takes place.
  • the expanded water 65 then flows from here back into the pump 58 again.
  • Air 61 flowing via a regulating member 62 is simultaneously provided, in this injector, for starting the process.
  • the compressed circulation gas 63 then flows through the recuperator 64 , already mentioned, and there absorbs the heat discharged by the exhaust gases 23 , before said gas then flows as treated circulation gas 66 into the combustion chamber.
  • a part quantity 67 of the circulation gas 63 compressed in the injector is branched off upstream of the recuperator 64 and led through a cooler 14 , in which the condensation of the CO 2 takes place in the way already described.
  • the discharge 15 of the condensed CO 2 and of the parasitic gases 16 is subsequently carried out.
  • the remaining elements of this figure correspond to the setup according to FIG. 5, here the steam line 47 from the recuperator 64 also being equipped with a regulating member 68 .
  • FIG. 9 shows a setup which is based on a piston engine 69 / 70 .
  • Engines having a multipiston system may, of course, also be used here.
  • the piston 70 moves upward, and a recirculation gas is sucked in from the line 74 and/or from the storage volume 71 , during the start itself air 72 being sucked in from the surroundings.
  • These operations during intake or starting are controlled by means of corresponding regulating members 73 , 75 .
  • the piston 70 closes (piston 70 downward).
  • the separately compressed fuel 78 is injected by means of the regulating member 79 and oxygen 76 by means of the regulating member 77 in a near-stoichiometric ratio, being ignited spontaneously or by spark, depending on the pressure ratio, with the result that expansion (piston 70 upward) is initiated.
  • the piston 70 moves downward; in the operating mode with recirculation, only the valve 81 to the cooler is open.
  • the piston engine is started up and ignited and then the exhaust gas valve 85 is throttled, with the result that the recirculation line 80 and its branch 84 are supplied with exhaust gas.
  • the air intake valve 73 is also gradually throttled and recirculation is enriched with circulation gas predominantly consisting of CO 2 .
  • the two valves 73 , 85 which are operatively connected during starting, are closed completely and the engine is in the recirculation mode.
  • the excess circulation gas, namely CO 2 can be extracted from the cycle basically in two ways: at the lowest pressure level via a line 82 , which is provided with a regulating member 83 and which branches off from the ejection string, or by means of a valve, not shown in any more detail in the figure, which is arranged upstream of the cooler 24 .
  • Another possibility for extracting the excess circulation gas from the cycle is to branch it off under pressure in a suitable section of the compression cycle, recool it and condense it.
  • the circulation gas extracted in this case contains only a little water to be discharged, insofar as the setup has good dewatering 25 / 26 downstream of the cooler 24 .
  • this piston engine does not require any charging in order to achieve a power increase. If less excess gas is extracted from the closed or quasi closed circuit, the process pressure in the return through the line 74 and in the storage volume 71 rises automatically, and vice versa.
  • the engine present here also needs a hydrocarbon or hydrogen as fuel and, correspondingly, also oxygen, either in the pure form or as oxygen-enriched air. In the case of operation with relatively pure oxygen, no nitrogen enters the flame, with the result that NO x formation, known in piston engines, is eliminated completely.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Hydrogen, Water And Hydrids (AREA)
US09/255,712 1998-02-25 1999-02-23 Method for operating a power plant including a co2 process Abandoned US20010042367A1 (en)

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US10/852,656 US7089743B2 (en) 1998-02-25 2004-05-25 Method for operating a power plant by means of a CO2 process

Applications Claiming Priority (2)

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EP98810154A EP0939199B1 (de) 1998-02-25 1998-02-25 Kraftwerksanlage und Verfahren zum Betrieb einer Kraftwerksanlage mit einem CO2-Prozess
EP98810154.9 1998-02-25

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EP (1) EP0939199B1 (de)
JP (1) JP2000064854A (de)
DE (1) DE59811106D1 (de)
NO (1) NO316807B1 (de)

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WO2005019605A1 (de) * 2003-08-13 2005-03-03 Siemens Aktiengesellschaft Verfahren zum betrieb einer turbinenanlage, turbinenanlage sowie verwendung einer gasturbine
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US20120260654A1 (en) * 2009-10-06 2012-10-18 Thomas Proepper Driving device
EP2247367B1 (de) 2008-02-25 2013-01-23 Siemens Aktiengesellschaft Verfahren zur verdichtung von kohlendioxid
CN103459815A (zh) * 2011-03-22 2013-12-18 埃克森美孚上游研究公司 改变低排放涡轮气体再循环回路的方法和与此相关的系统和设备
WO2014036258A1 (en) * 2012-08-30 2014-03-06 Enhanced Energy Group LLC Cycle turbine engine power system
WO2014036256A1 (en) * 2012-08-30 2014-03-06 Enhanced Energy Group LLC Cycle piston engine power system
AU2015234309A1 (en) * 2014-09-30 2016-04-14 Toshiba Energy Systems & Solutions Corporation Gas turbine facility
US11931685B2 (en) 2020-09-10 2024-03-19 Enhanced Energy Group LLC Carbon capture systems

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DE50115748D1 (de) 2000-10-13 2011-02-03 Alstom Technology Ltd Verfahren zum Betrieb einer Kraftwerksanlage
WO2003029618A1 (de) * 2001-10-01 2003-04-10 Alstom Technology Ltd. Verfahren und vorrichtung zum anfahren von emissionsfreien gasturbinenkraftwerken
NO20023050L (no) * 2002-06-21 2003-12-22 Fleischer & Co Fremgangsmåte samt anlegg for utf degree relse av fremgangsmåten
DE10231879B4 (de) * 2002-07-12 2017-02-09 General Electric Technology Gmbh Verfahren zur Beeinflussung und Kontrolle der Oxidschicht auf thermisch belasteten metallischen Bauteilen von CO2/H2O-Gasturbinenanlagen
DE10325111A1 (de) * 2003-06-02 2005-01-05 Alstom Technology Ltd Verfahren zur Erzeugung von Energie in einer eine Gasturbine umfassende Energieerzeugungsanlage sowie Energieerzeugungsanlage zur Durchführung des Verfahrens
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