US3583156A - Gas turbine powerplants - Google Patents

Gas turbine powerplants Download PDF

Info

Publication number
US3583156A
US3583156A US816520A US3583156DA US3583156A US 3583156 A US3583156 A US 3583156A US 816520 A US816520 A US 816520A US 3583156D A US3583156D A US 3583156DA US 3583156 A US3583156 A US 3583156A
Authority
US
United States
Prior art keywords
compressors
turbine
heat
medium
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US816520A
Other languages
English (en)
Inventor
Hans-Peter Schabert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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
Priority claimed from DE19681751226 external-priority patent/DE1751226C/de
Application filed by Individual filed Critical Individual
Application granted granted Critical
Publication of US3583156A publication Critical patent/US3583156A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • G—PHYSICS
    • G21—NUCLEAR PHYSICS; NUCLEAR ENGINEERING
    • G21D—NUCLEAR POWER PLANT
    • G21D5/00—Arrangements of reactor and engine in which reactor-produced heat is converted into mechanical energy
    • G21D5/04—Reactor and engine not structurally combined
    • G21D5/08—Reactor and engine not structurally combined with engine working medium heated in a heat exchanger by the reactor coolant
    • 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
    • Y02E30/00—Energy generation of nuclear origin
    • 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
    • Y02T50/00—Aeronautics or air transport
    • Y02T50/60—Efficient propulsion technologies, e.g. for aircraft

Definitions

  • a gas turbine powerplant for operation with heat from nuclear or fossil fuel comprises a circulatory system which contains the gaseous working medium for a turbine and has a recuperative heat exchanger in series with the turbine and the heat supply.
  • the system has a plurality of compressors of which two form respective paths for parallel flows of medium and are connected to respectively different temperature stages of the recuperative heat exchanger at the high-pressure side thereof.
  • the compressors are connected through cooling means with the heat supply within the circulatory system.
  • the median specific heat of the gaseous medium at the high-pressure side of the recuperative heat exchanger is more than 5 percent higher than at the low-pressure side, and the suction pressure of at least one of the two compressors at full load is above the critical pressure.
  • the essential components of such a powerplant are a heat source, a gas turbine, recuperative heat exchanger, compressor and cooler.
  • Another object of the invention is to devise a powerplant that it particularly well suitable for operation with nuclear reactors cooled by sodium gas and which is also suitable for gas turbines connected to other types of heat sources.
  • the median specific heat of the gaseous working medium at the high-pressure side of the recuperative heat exchanger is more than percent higher than on the low-pressure side, at least two compressors being provided of which two, serving as partial flow compressors, are connected to different temperature stages respectively at the high-pressure side of the recuperative heat exchanger; and high-pressure gas coming form the compressors is supplied to the recuperative heat exchanger in the from of two partial flows.
  • the heat exchanger may be provided, for example, with a tap in its system of tube windings.
  • separate windings of heat exchanger tubes for the respective two component flows of compressed working medium are also applicable.
  • the supercritical state of induction of the gas preferably CO ahead of the compressor has the advantage that a power regulation through regulation of the throughput of medium by weight, can be secured in a simple manner by changing the temperature setting at the outlet of the cooler. As will be recognized from FIG. 2a, there is no danger that liquified gas may occur in the system since the process remains within the supercritical range of the gas.
  • FIGS. 1 and 2 are schematic circuit diagrams of two powerplants operating with heat from a sodium-cooled nuclear reactor
  • FIGS. 2a and 2b are explanatory temperature-pressure diagrams for explaining the operation of the gas turbine circulatory system of such plants;
  • FIG. 3 is a schematic circuit diagram of a plant directly heated from a nuclear reactor
  • FIG. 4 is another temperature-pressure diagram of the cycle operation in a system somewhat modified from that of FIG. 4;
  • FIG. 5 is the schematic circuit diagram ofa gas turbine plant heated with fossil fuel and operating according to the performance diagram of FIG. 4.
  • FIG. 1 illustrates an example of a circulatory system for a sodium-heated CO gas turbine plant with partialflow compression and precompression.
  • the original heat generator is a sodium-cooled nuclear reactor plant which is not illustrated.
  • the heat generated by the reactor is applied to a heat exchanger 10 which transfers the heat to the gas circulation system thus forming part of the heat source means of that system.
  • Mutually corresponding temperature and pressure relations are indicated at the respective circuit localities of the system.
  • the gas current, heated in the source exchanger 10 and having a temperature of 500 C. at a pressure of 300 ata. (atmospheres above ambient) passes through two valves 30 and 31 in two partial flows to respective turbines 18 and 14.
  • the turbine 14 is the main prime mover and serves for driving a precompressor 16, a main compressor 18 and an electric current generator 15.
  • the auxiliary turbine 13 drives an auxiliary compressor 17.
  • the gas arrives at a temperature of 320 C. at a recuperative heat exchanger 19 where it transfers its residual heat to the coolant which recycles back to the source heat exchanger 10.
  • the recuperative exchanger 19 (recuperator) the working gas reaches a cooler 22 at a temperature of C.
  • the working medium arrives at the precompressor l6 driven from the main turbine 14.
  • Approximately 30 percent of the working medium are branched off behind the main turbine 14 and pass as a first partial flow to the auxiliary compressor 17.
  • the other partial flow, amounting to 70 percent passes through another cooler 21 to the main compressor 18.
  • the working medium leaving the compressor 18 flows through a check valve (flap valve) 33 and thence through the tube windings of the recuperator 19 at an entering temperature of about 68 C.
  • the partial flow coming form the auxiliary compressor 17, not having passed through the second cooler 21, has a higher temperature, namely C., an is supplied through a check (flap) valve 32 to a tap point a of the highpressure tube windings 20.
  • the two partial currents are again combined to a single flow of working medium which returns to the source heat exchanger 10 at a temperature of 273 C., and a pressure of 305 ata.
  • the check valves 37 and 36 are closed, and the valves 30, 31, 32 and 33 are open. In the event a rapid stoppage of the turbine is required, a bypass valve 36 is opened.
  • the auxiliary turbine 13 can be shut down by closing the valve 30.
  • the valves 30 and 37 are open in a regulated manner; the valve 37 then acts as a bypass valve and the auxiliary cooler 23 prevents an excessive temperature increase during startup performance.
  • FIG. 2 shows a somewhat simplified circuit of a similar sodium-heated CO turbine plant in which the above-mentioned precompressor l6 and the cooler 22 are omitted.
  • the division into partial flows or currents of working gas is effected before the gas enters into the cooler 2].
  • Thirty percent of the medium pass through the valve 35 and the compressor 17 through the check valve 32 at a temperature of 197 C. to enter at point a of the stack 20 of tube windings in the recuperator 19.
  • the major portion of the working medium traverses the cooler 21 and arrives at the compressor 18 at a temperature of 33 C. and a pressure of 90 ata. From compressor 18 the gas enters into the lower end of the winding stack 20 at 310 ata. and 68 C.
  • the normal operation just described with reference to FIG. 2 requires that the valves 35, 32 and 30 be open, the valve 30 being regulated if desired.
  • the valves 34, 36 and 38 are closed during such operation.
  • the compressor 17 and the turbine 13 can be shut down by closing the valve 30. If nothing else is done, the outlet temperature at the recuperator 19 increases at the high-pressure side. For preventing an excessive or undesired temperature increase of this kind, the valves 35 and 32 are to be additionally closed.
  • the valves 38, 35, 34 and 30 are opened in a regulated manner, and the cooler 21 then additionally assumes the function of the auxiliary cooler 23 in FIG. 1. After startup, the valve conditions are the same as for normal operation. As in the system of FIG. 1, rapid shutdown is effected by completely opening the bypass valve 36.
  • FIG. 3 illustrates a circuit in which a nuclear reactor 1] is used as a direct heat source in the gas turbine circulatory system. That is, the working medium of the gas turbine simultaneously constitutes a coolant for the nuclear reactor, a separate primary circuit in the reactor, for example a circulation of sodium in the reactor, being dispensed with.
  • the coolant heated in the nuclear reactor does not directly reach the turbine but first passes through the recuperative heat exchanger 19.
  • the pressure reduction of the working medium in the main turbine 14 occurs before the coolant reenters into the reactor 11. This, among other things, affords preventing the nuclear reactor from being impressed by the maximum pressure of the turbine system.
  • the system of FIG. 3 is similar to those of FIGS. 1 and 2. That is, the current or working medium, after leaving the recuperative heat exchanger 19, is subdivided. A partial flow of 25 percent passes through the auxiliary compressor l7, and another flow of 75 percent passes through the cooler 21 to the main compressor 16. Both partial currents are recombined in the stack of tube windings 20 in the recuperator 19, substantially as described with reference to FIGS. 1 and 2. After leaving the recuperator 19, the working medium reaches the turbines l3 and 14 at 300 ata. and 436 C. Upon leaving the turbines, the working medium, now having a pressure of 120 ata. and a temperature of 334 C., returns to the nuclear reactor 11 to serve as a coolant therein.
  • valves 30, 35 and 32 are open, and the partial valves 36 and 34 are closed.
  • the auxiliary compressor 17 is to be shut down.
  • the valve 35 is partially closed to provide for mixed cooling, and the valve 36 is opened.
  • the bypass valve 34 and the valve 30 are opened approximately in synchronism with each other.
  • the valve 34 is closed and the initial valve condition for normal operation is reestablished, so that the partial flow delivered through the auxiliary compressor 17 can enter into the recuperator exchanger 19.
  • FIG. 4 is a schematic temperature-pressure cycle diagram of such a direct circulatory system comprising two-stage pressure reduction, precompression and partial flow compression.
  • FIG. 5 shows a circuit diagram of the type represented by FIG. 4, but designed for a source heated with fossil fuel.
  • the firing or boiler plant (source) proper is denoted by 12.
  • the heat is transferred to the gas turbine circulation system by means of a heat exchange 121.
  • a heat exchanger 122 in the path of the heating or flue gases of the boiler serves to preheat the combustion air supplied to the firing system 12.
  • the same purpose is served by an air preheater 123 which is connected in series with the heat exchanger 122 with respect to the flow of the heating or flue gases.
  • the exchanger 123 is traversed by a portion of the working gas.
  • the circuitry of the system is otherwise as in the embodiments described above.
  • a partial current of about 15 percent having a pressure of 92 ata. and a temperature of C.
  • the embodiments described constitute relatively simple circuit systems. Intermediate superheating upon partial pressure reduction of the working medium is dispensed with. Such intermediate superheating is highly disagreeable with a sodiumcooled reactor, since the heat transfer onto the CO side within the intermediate superheater portion of the plant would be very poor. consequently, it would be necessary to employ soidum-CO side within the intermediate superheater portion of the plant would be very poor. Consequently, it would be necessary to employ sodium-CO heat exchangers of extremely large volume. Another disadvantage would be the complicated ducting required for passing the CO pipes twice into the reactor building and twice out of the building.
  • the compressors may consist of radial compressors which do not react as fast as axial compressors upon changes of their throughput.
  • the known processes involving condensation and great expansion require the use of axial compressors at least in the lower pressure stages.
  • the axial compressors may attain a gas flow below the pumping limit of this compressor type.
  • radial compressors have a slightly lower efficiency than axial compressors, but this difference is of little significance because of the relatively low compressing power and, besides, can be moderated to a great extent by using spiral-type housings with several straight-duct diffusors. It is preferable to provide the main compressor being called upon to deliver about 70 percent of the working medium, with an adjustable input guiding device in order to better adapt the performance in the partial load range to the varying CO data.
  • the auxiliary compressor 17 may also be driven through the main shaft from the main turbine.
  • the partial current may be passed through its own winding or coil of tubes in the recuperative heat exchanger 19, thus avoiding the necessity of providing a tap at the tube winding stack 20.
  • the flow delivered by the auxiliary compressor may be passed separately through the CO heater, thus providing a completely independent auxiliary compressor turbine system which may also run on a lower high-pressure level than the main flow of working medium.
  • the branched-off auxiliary flow in such a case is preferably provided with a type ofoverflow with the aid of a check valve which connects this flow with the main flow on the high-pressure side.
  • Such a separate auxiliary flow system can be started up without the use of a bypass.
  • the induction temperature of the auxiliary compressor need not correspond exactly to the CO temperature at the transition from the recuperator to the cooler. This induction temperature may also be reduced, for example, by applying the mixing circuit extending through the valves and 36 as will be apparent from FIG. 2. In the latter case the necessary speed of the auxiliary compressor decreases and the total efficiency is slightly reduced.
  • nuclear reactors when using nuclear reactors as a source of heat, these may operate with coolants other than sodium.
  • Such systems often require an indirect circulation involving the use of a primary-secondary heat exhanger. If, with a Co -cooled reactor, the primary as well as the secondary circuits are operated with the same medium, namely CO gas, considerable leakage between primary and secondary circulation is permissible, such as in the order of l ton CO per day, without the danger of contaminating the turbine circulation system since the latter is under a higher pressure than the primary circulation.
  • the indirect type of system has the disadvantage ofconsuming additional power for the blower needed to circulate the medium in the primary circuit.
  • the liberty of selecting the secondary pressures for optimum performance compensates for this disadvantage to a large extend in spite of the lower turbine inlet temperature, for example 464 C., occurring in a Co -cooled fast breeder reactor.
  • Illustrative in this respect is the diagram in FIG. 2b.
  • the recuperator outlet temperature (point 9 in the diagram) is so low that its distance from the end temperature (point 7) of the auxiliary flow compression is only moderate or small. This applies particularly because the pressure ratio in the turbine according to FIG. 2a has been somewhat increased, which causes the temperature at point 9 to be lower and at point 7 to be higher.
  • CO turbines in conjunction with gas-cooled nuclear reactors can also be employed for driving the pump or blower which circulates the coolant in the primary circuit.
  • recuperative heat exchanger 19 As well as of the coolers, reference may be had to my above-mentioned application Ser. NO. 772,640, according to which these apparatus may have a prestressed concrete containerin common.
  • a gas turbine powerplant for operation with heat from nuclear or fossil fuel comprising a circulatory system contain ing gaseous working medium and having heat source means for heating said medium and at least one turbine connected to said source means, a recuperative heat exchanger interposed in said system serially with said turbine and said source means, a plurality of compressors, two of said compressors forming paths for respective partial flows of the total flow of medium and being connected to respectively different temperature stages of said recuperative heat exchanger at the high-pressure side thereof, cooling means connected in said system behind said turbine and ahead of said source means, the median specific heat of said medium at the high-pressure side of said recuperative heat exchanger being more than 5 percent than at the lower-pressure side, and the suction pressure of at least one of said two compressors at full load being above the critical pressure magnitude.
  • each of said two compressors having its own drive turbine connected to said source means for operation by said gaseous medium heated by said source means.
  • one of said two compressors having in said system a gas induction point ahead of one of said cooling means, and said other compressor having its induction point arrear of said other cooling means.
  • a powerplant according to claim 1, wherein said gaseous working medium is carbon dioxide.
  • said heat source means comprising a heat exchanger secondarily connected in said system, and a nuclear reactor with which said latter exchanger is primarily connected to receive heat generated in said reactor.
  • said heat source means comprising a nuclear reactor, said gaseous working medium constituting a coolant for directly cooling said reactor.
  • a powerplant according to claim 8 comprising at least two turbines for useful mechanical power generation, said two turbines being connected in said system ahead and arrear respectively of said reactor.
  • said heat source means comprising a fossil fuel boiler plant having combustion air preheater means connected to said system for preheating the air at least partially by residual heat of said circulatory system for the gaseous working medium.
  • one of said two compressors being the main compressor and the other an auxiliary compressor of the system, said main compressor having a larger throughput of gaseous medium than said auxiliary compressor, and regulating means for partial load operation of the plant, said regulating means being in connection with said auxiliary compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Plasma & Fusion (AREA)
  • High Energy & Nuclear Physics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
US816520A 1968-04-24 1969-04-16 Gas turbine powerplants Expired - Lifetime US3583156A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19681751226 DE1751226C (de) 1968-04-24 Durch Kernkraft oder fossile Brennstoffe beheizte Gasturbinenanlage

Publications (1)

Publication Number Publication Date
US3583156A true US3583156A (en) 1971-06-08

Family

ID=5692194

Family Applications (1)

Application Number Title Priority Date Filing Date
US816520A Expired - Lifetime US3583156A (en) 1968-04-24 1969-04-16 Gas turbine powerplants

Country Status (5)

Country Link
US (1) US3583156A (de)
JP (1) JPS4820322B1 (de)
CH (1) CH488103A (de)
FR (1) FR2016741A1 (de)
GB (1) GB1263124A (de)

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3878683A (en) * 1969-07-01 1975-04-22 Kenji Imai Method of cooling substance or generating power by use of liquefied gas
US4003786A (en) * 1975-09-16 1977-01-18 Exxon Research And Engineering Company Thermal energy storage and utilization system
US4021299A (en) * 1973-11-29 1977-05-03 Georges Alfred Rigollot Method of working a combined nuclear-fossil fuel cycle and device for using same
US4863675A (en) * 1984-10-04 1989-09-05 General Atomics Nuclear power system
US5267288A (en) * 1991-09-05 1993-11-30 Asea Brown Boveri Ltd. Power station installation
US5309492A (en) * 1993-04-15 1994-05-03 Adams Atomic Engines, Inc. Control for a closed cycle gas turbine system
US6674830B2 (en) * 2001-03-09 2004-01-06 President Of Tokyo Institute Of Technology Nuclear reactor plant
US20040003622A1 (en) * 2002-04-15 2004-01-08 Masami Negishi Refrigerating cycle system using carbon dioxide as refrigerant
US20040131138A1 (en) * 2001-05-25 2004-07-08 Michael Correia Brayton cycle nuclear power plant and a method of starting the brayton cycle
US20070137203A1 (en) * 2004-02-23 2007-06-21 Mitsubishi Heavy Industries, Ltd. Gas turbine plant
US20070183554A1 (en) * 2004-02-23 2007-08-09 Mitsubishi Heavy Industries, Ltd. Gas turbine plant
US20070248472A1 (en) * 2004-10-21 2007-10-25 Baumer Klaus Device for Generating Highly Compressed Gas
US20130145759A1 (en) * 2011-12-13 2013-06-13 Chandrashekhar Sonwane Low cost and higher efficiency power plant
WO2013109616A1 (en) 2012-01-17 2013-07-25 Stapp David S System and method for generating power using a supercritical fluid
US20150200022A1 (en) * 2012-08-01 2015-07-16 Areva Gmbh Containment protection system for a nuclear facility and associated operating method
US20160053638A1 (en) * 2014-08-22 2016-02-25 Peregrine Turbine Technologies, Llc Power generation system including multiple cores
CN110836144A (zh) * 2019-12-05 2020-02-25 上海电气燃气轮机有限公司 一种防止燃气轮机发生热悬挂的方法和调节系统
CN110848032A (zh) * 2019-12-05 2020-02-28 上海电气燃气轮机有限公司 一种消除燃气轮机热悬挂前兆的方法和调节系统
US11407283B2 (en) * 2018-04-30 2022-08-09 Tiger Tool International Incorporated Cab heating systems and methods for vehicles
US11492964B2 (en) 2020-11-25 2022-11-08 Michael F. Keller Integrated supercritical CO2/multiple thermal cycles
EP2619418B1 (de) * 2010-09-21 2023-02-15 8 Rivers Capital, LLC Hocheffizientes energieerzeugungsverfahren und -system
US11879691B2 (en) * 2017-06-12 2024-01-23 General Electric Company Counter-flow heat exchanger
US11993130B2 (en) 2018-11-05 2024-05-28 Tiger Tool International Incorporated Cooling systems and methods for vehicle cabs
US12030368B2 (en) 2020-07-02 2024-07-09 Tiger Tool International Incorporated Compressor systems and methods for use by vehicle heating, ventilating, and air conditioning systems
US12209533B2 (en) 2022-11-29 2025-01-28 General Electric Company Heat driven thermal management systems and methods for operating the same
US12473874B2 (en) 2022-11-17 2025-11-18 General Electric Company Dual compression-expansion pumps and related methods

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2125171C1 (ru) * 1997-12-19 1999-01-20 Закрытое акционерное общество "Агентство регионального развития" Способ эксплуатации энергетической установки и установка для его осуществления
RU2334113C1 (ru) * 2007-01-22 2008-09-20 Дмитрий Александрович Новосельцев Микротурбина
WO2012176254A1 (ja) * 2011-06-20 2012-12-27 熱技術開発株式会社 閉サイクルガスタービン
JP5550787B2 (ja) * 2011-06-20 2014-07-16 熱技術開発株式会社 閉サイクルガスタービン
CA2860823A1 (en) * 2011-12-20 2013-06-27 Nihon Nature Cell Co., Ltd. Compact nuclear power generation system
RU2508460C1 (ru) * 2012-07-10 2014-02-27 Федеральное государственное унитарное предприятие "Государственный космический научно-производственный центр имени М.В. Хруничева" Космическая энергетическая установка с машинным преобразованием энергии
RU2583191C1 (ru) * 2014-12-22 2016-05-10 Федеральное государственное унитарное предприятие "Государственный космический научно-производственный центр имени М.В. Хруничева" Космическая энергетическая установка с машинным преобразованием энергии
KR102669709B1 (ko) * 2017-08-28 2024-05-27 8 리버스 캐피탈, 엘엘씨 회수식 초임계 co2 동력 사이클들의 저등급의 열 최적화
US10570783B2 (en) * 2017-11-28 2020-02-25 Hanwha Power Systems Co., Ltd Power generation system using supercritical carbon dioxide
RU2716766C1 (ru) * 2019-03-11 2020-03-16 Акционерное общество "Государственный космический научно-производственный центр имени М.В. Хруничева" Энергетическая установка с машинным преобразованием энергии
RU2757148C1 (ru) * 2020-11-10 2021-10-11 Акционерное общество "КБхиммаш им. А.М. Исаева" Космическая энергетическая установка с машинным преобразованием энергии

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2203731A (en) * 1937-01-25 1940-06-11 Ag Fuer Technische Studien Means for regulating and starting thermal power plants
US3324652A (en) * 1964-07-08 1967-06-13 Commissariat Energie Atomique Process and apparatus for power production
US3444038A (en) * 1966-07-09 1969-05-13 Siemens Ag Nuclear power station with carbon dioxide cooling system

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2203731A (en) * 1937-01-25 1940-06-11 Ag Fuer Technische Studien Means for regulating and starting thermal power plants
US3324652A (en) * 1964-07-08 1967-06-13 Commissariat Energie Atomique Process and apparatus for power production
US3444038A (en) * 1966-07-09 1969-05-13 Siemens Ag Nuclear power station with carbon dioxide cooling system

Cited By (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3878683A (en) * 1969-07-01 1975-04-22 Kenji Imai Method of cooling substance or generating power by use of liquefied gas
US4021299A (en) * 1973-11-29 1977-05-03 Georges Alfred Rigollot Method of working a combined nuclear-fossil fuel cycle and device for using same
US4003786A (en) * 1975-09-16 1977-01-18 Exxon Research And Engineering Company Thermal energy storage and utilization system
US4863675A (en) * 1984-10-04 1989-09-05 General Atomics Nuclear power system
US5267288A (en) * 1991-09-05 1993-11-30 Asea Brown Boveri Ltd. Power station installation
US5309492A (en) * 1993-04-15 1994-05-03 Adams Atomic Engines, Inc. Control for a closed cycle gas turbine system
US6674830B2 (en) * 2001-03-09 2004-01-06 President Of Tokyo Institute Of Technology Nuclear reactor plant
US20040131138A1 (en) * 2001-05-25 2004-07-08 Michael Correia Brayton cycle nuclear power plant and a method of starting the brayton cycle
US20040003622A1 (en) * 2002-04-15 2004-01-08 Masami Negishi Refrigerating cycle system using carbon dioxide as refrigerant
US20100086096A1 (en) * 2004-02-23 2010-04-08 Mitsubishi Heavy Industries, Ltd. Gas Turbine Plant
US20070183554A1 (en) * 2004-02-23 2007-08-09 Mitsubishi Heavy Industries, Ltd. Gas turbine plant
US7596947B2 (en) * 2004-02-23 2009-10-06 Mitsubishi Heavy Industries, Ltd. Gas turbine plant
US20070137203A1 (en) * 2004-02-23 2007-06-21 Mitsubishi Heavy Industries, Ltd. Gas turbine plant
US20070248472A1 (en) * 2004-10-21 2007-10-25 Baumer Klaus Device for Generating Highly Compressed Gas
US12264596B2 (en) 2010-09-21 2025-04-01 8 Rivers Capital, Llc High efficiency power production methods, assemblies, and systems
EP4183979A1 (de) * 2010-09-21 2023-05-24 8 Rivers Capital, LLC Hocheffiziente stromerzeugungsverfahren, anordnungen und systeme
EP2619418B1 (de) * 2010-09-21 2023-02-15 8 Rivers Capital, LLC Hocheffizientes energieerzeugungsverfahren und -system
US11859496B2 (en) 2010-09-21 2024-01-02 8 Rivers Capital, Llc High efficiency power production methods, assemblies, and systems
US20130145759A1 (en) * 2011-12-13 2013-06-13 Chandrashekhar Sonwane Low cost and higher efficiency power plant
US8887503B2 (en) * 2011-12-13 2014-11-18 Aerojet Rocketdyne of DE, Inc Recuperative supercritical carbon dioxide cycle
WO2013109616A1 (en) 2012-01-17 2013-07-25 Stapp David S System and method for generating power using a supercritical fluid
US10072574B2 (en) 2012-01-17 2018-09-11 Peregrine Turbine Technologies, Llc System and method for generating power using a supercritical fluid
US9540999B2 (en) 2012-01-17 2017-01-10 Peregrine Turbine Technologies, Llc System and method for generating power using a supercritical fluid
EP2807348A4 (de) * 2012-01-17 2016-03-02 Peregrine Turbine Technologies Llc System und verfahren zur erzeugung von energie unter verwendung einer überkritischen flüssigkeit
US20150200022A1 (en) * 2012-08-01 2015-07-16 Areva Gmbh Containment protection system for a nuclear facility and associated operating method
US20160053638A1 (en) * 2014-08-22 2016-02-25 Peregrine Turbine Technologies, Llc Power generation system including multiple cores
US11073339B2 (en) 2014-08-22 2021-07-27 Peregrine Turbine Technologies, Llc Heat exchanger for a power generation system
US10254048B2 (en) 2014-08-22 2019-04-09 Peregrine Turbine Technologies, Llc Heat exchanger for a power generation system
US10101092B2 (en) * 2014-08-22 2018-10-16 Peregrine Turbine Technologies, Llc Power generation system including multiple cores
US11879691B2 (en) * 2017-06-12 2024-01-23 General Electric Company Counter-flow heat exchanger
US11407283B2 (en) * 2018-04-30 2022-08-09 Tiger Tool International Incorporated Cab heating systems and methods for vehicles
US11993130B2 (en) 2018-11-05 2024-05-28 Tiger Tool International Incorporated Cooling systems and methods for vehicle cabs
CN110848032A (zh) * 2019-12-05 2020-02-28 上海电气燃气轮机有限公司 一种消除燃气轮机热悬挂前兆的方法和调节系统
CN110836144A (zh) * 2019-12-05 2020-02-25 上海电气燃气轮机有限公司 一种防止燃气轮机发生热悬挂的方法和调节系统
US12030368B2 (en) 2020-07-02 2024-07-09 Tiger Tool International Incorporated Compressor systems and methods for use by vehicle heating, ventilating, and air conditioning systems
US11492964B2 (en) 2020-11-25 2022-11-08 Michael F. Keller Integrated supercritical CO2/multiple thermal cycles
US12473874B2 (en) 2022-11-17 2025-11-18 General Electric Company Dual compression-expansion pumps and related methods
US12209533B2 (en) 2022-11-29 2025-01-28 General Electric Company Heat driven thermal management systems and methods for operating the same

Also Published As

Publication number Publication date
DE1751226B2 (de) 1973-02-15
DE1751226A1 (de) 1971-05-19
GB1263124A (en) 1972-02-09
CH488103A (de) 1970-03-31
FR2016741A1 (de) 1970-05-15
JPS4820322B1 (de) 1973-06-20

Similar Documents

Publication Publication Date Title
US3831373A (en) Pumped air storage peaking power system using a single shaft gas turbine-generator unit
US3150487A (en) Steam turbine-gas turbine power plant
US4998410A (en) Hybrid staged combustion-expander topping cycle engine
US5535584A (en) Performance enhanced gas turbine powerplants
US5609029A (en) Thermal power engine and its operating method
US5678408A (en) Performance enhanced gas turbine powerplants
US5255505A (en) System for capturing heat transferred from compressed cooling air in a gas turbine
US4214450A (en) Apparatus for recovering heat from exhaust gases of marine prime movers
US3974642A (en) Hybrid cycle power plant with heat accumulator for storing heat exchange fluid transferring heat between cycles
US3232052A (en) Power producing installation comprising a steam turbine and at least one gas turbine
US3047479A (en) Steam reactor system
US3006146A (en) Closed-cycle power plant
US20130044851A1 (en) Backup nuclear reactor auxiliary power using decay heat
JP2005527808A (ja) 少なくとも１つの高温原子炉のコアで生成される熱から電気を生成する方法及び装置
US3886749A (en) Steam power stations
US4193266A (en) Gas turbine power plant
US3043763A (en) Heat transfer system for nuclear power plant
US4466249A (en) Gas turbine system for generating high-temperature process heat
US3069342A (en) Heat exchange arrangement for nuclear power plant
US5267288A (en) Power station installation
US3436912A (en) Apparatus for combined steam-ammonia cycle
US3232050A (en) Cryogenic closed cycle power system
US2478851A (en) Gas turbine plant
US3503207A (en) Closed cycle co2 gas turbine power plant with partial condensation of the working substance prior to expansion thereof
US3974029A (en) Nuclear reactors with auxiliary boiler circuit