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WO1996039577A1 - Dispositif de refroidissement et de refrigeration alimente par gaz et vapeur ou a turbine, et systemes de cogeneration - Google Patents

Dispositif de refroidissement et de refrigeration alimente par gaz et vapeur ou a turbine, et systemes de cogeneration Download PDF

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Publication number
WO1996039577A1
WO1996039577A1 PCT/US1996/005931 US9605931W WO9639577A1 WO 1996039577 A1 WO1996039577 A1 WO 1996039577A1 US 9605931 W US9605931 W US 9605931W WO 9639577 A1 WO9639577 A1 WO 9639577A1
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WO
WIPO (PCT)
Prior art keywords
steam
set forth
power system
hybrid power
cycle turbine
Prior art date
Application number
PCT/US1996/005931
Other languages
English (en)
Inventor
Milton Meckler
Original Assignee
Milton Meckler
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 US08/635,756 external-priority patent/US6050083A/en
Application filed by Milton Meckler filed Critical Milton Meckler
Priority to AU56323/96A priority Critical patent/AU5632396A/en
Publication of WO1996039577A1 publication Critical patent/WO1996039577A1/fr

Links

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
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/008—Sorption machines, plants or systems, operating continuously, e.g. absorption type with multi-stage operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/02—Compression-sorption machines, plants, or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2250/00—Special cycles or special engines
    • F02G2250/03—Brayton cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2254/00—Heat inputs
    • F02G2254/30—Heat inputs using solar radiation
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/62—Absorption based systems
    • Y02B30/625—Absorption based systems combined with heat or power generation [CHP], e.g. trigeneration
    • 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
    • Y02E20/14—Combined heat and power generation [CHP]
    • 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
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Definitions

  • This invention relates to the generation of power for air conditioning systems, processing and co- generation, and is characterized by a primary gas turbine that produces shaft power and an exhaust that produces a high temperature liquid state heat transfer media for selective uses including steam activated adsorption chilling, steam-jet refrigeration, and steam generating; and by a secondary steam turbine operated by said steam generation to produce shaft power coupled by clutch means through a gear means that reduces the two turbine shaft speeds to a common power shaft speed driving air conditioning systems including a vapor compression chiller system, a vapor compression refrigeration system, and a co-generation system for electrical power.
  • a constant speed gas turbine is combined with a constant speed steam turbine operating on steam generated from the exhaust heat of the gas turbine.
  • a constant speed gas turbine is combined with a constant speed steam turbine operating on steam generated from the exhaust heat of the gas turbine.
  • shaft speeds of these two turbines, gas and steam it being an object of this invention to cooperatively combine the torque outputs of each so as to unite in a common power output shaft to drive either the air conditioning system or the co-generation system.
  • the shaft speed of a typical gas turbine is
  • the potential fuel energy is introduced into this hybrid system at the primary gas turbine which is operated at an optimum shaft speed as required by the air conditioning system or co-generator, for example, by a mechanical chiller unit or electrical co-generator, and operated at a constant shaft speed conductive to operating either of said systems.
  • the shaft speeds of the two turbines are individually controlled by means of speed limiting governors, and it is significant that the primary gas turbine operating in the Brayton cycle is the energy producing prime mover, in that it produces shaft power and exhaust heat that contains energy in the Rankine Cycle range.
  • the Brayton cycle employs a compressor followed by a combustion chamber, and an air engine to produce power.
  • An axial flow gas turbine embodiment of the Brayton cycle is characterized by an axial flow compressor that compresses and heats induction air.
  • the compressed air enters a combustion chamber where the temperature is increased by means of burning fuel, a hydrocarbon and preferably gas, while the pressure remains constant.
  • the resulting high temperature mixture of combusted gases and air then enters a turbine at high velocity to perform the work of producing shaft power.
  • the exhaust of a gas turbine is high in the range of 1500°F. Accordingly, it is an object of this invention to capture the exhaust heat energy from the gas turbine and convert it into additional shaft power and a steam turbine. Both gas and steam turbines are reliable in their operation and are characteristically compact.
  • a feature of this invention is the initial operation of the primary gas turbine that is directly coupled to the air conditioning system or co-generator system, followed by operation of the secondary steam turbine that relies upon the exhaust heat energy recovery from said gas turbine.
  • a feature of this invention therefore is the clutch means that separates the shaft drives from the two turbines.
  • the clutch coupling the steam turbine to the power shaft is an over- riding clutch, for example, a Sprague-type clutch. Therefore, after initial start operation of a gas turbine to speed, the steam turbine responds to steam generated from the gas turbine exhaust and reaches the shaft speed to complement the power output by adding torque thereto.
  • the hybrid power system herein disclosed utilizes shaft power from a gas turbine to operate air conditioning, refrigeration processing and co-generation equipment, and also utilizes exhaust heat to operate air conditioning and refrigeration process equipment.
  • a feature of this invention is that the shaft power of the primary gas turbine is supplemented by shaft power from a secondary steam turbine also operating from said exhaust heat, thereby conserving the energy not used by said air conditioning and refrigeration processing and this conserved energy is then used in the co-generation of electrical power.
  • the shaft power of the two turbines can be employed separately for processing systems and co- generation, or jointly through a common power shaft to operate a processing system or co-generator, as is shown and later described, it being an object to consume energy by conserving the remainder thereof by means of a co- generator.
  • a first utilitarian processing system advantageously combined with the hybrid power system herein disclosed is the subject of my co-pending application Serial No. 08/427,832 filed April 24, 1995, wherein concentrated absorbent solution in a closed absorption chiller is concentrated by vapor compression from an evaporator followed by liquification by a condenser with heat transfer from the condenser into the evaporator, increasing solution concentration and chilling capacity with an increased coefficient of performance, resulting in an increase in chilling.
  • This chiller provides a refrigerant enhancement and absorbent concentrator unit that increases the efficiency of absorption chillers, in any one of the generally recognized types thereof, by increasing the volume of water refrigerant supplying the evaporator at the chilling coils and simultaneously concentrating the absorbent solution at the heat absorber that removes heat from the system for discharge at a cooling tower or the like. It is the chilling mode of operation with which this chiller is particularly concerned, providing a unit that is compatible with and acceptable to existent air conditioning systems of the type under consideration, in either a cooling mode or heating mode as the case may be, and particularly with double effect absorption chiller systems.
  • the basic principles of adsorption is the use of heat and thereby produces a strong absorbent solution of lithium-bromide and water, and distilling therefrom a water vapor refrigerant that is condensed in an evaporator to thereby chill system water that is usefully circulated.
  • the absorbent solution is weakened in the process and heat removed therefrom and eliminated by means of an absorber that transfers said heat to a cooling tower or the like.
  • An enhancer-concentrator unit is employed in circuit with said absorber to remove heat from the system and is adaptable to single or double effect systems.
  • a second utilitarian processing system advantageously combined with the hybrid power system disclosed herein is the subject of my United States Letters Patent No. 4,290,273 issued September 22, 1981, entitled PELTIER EFFECT ABSORPTION CHILLER-HEAT PUMP SYSTEM, wherein a chiller and heat pump system employs a steam-jet refrigeration unit associated with a condenser and with an evaporator absorption unit, and associated pump means and valve control means for multi-mode operation including; simultaneous heating and cooling, cooling, heating, and simultaneous high temperature heating and cooling.
  • This chiller provides a heat pump in combination with a Steam-Jet Refrigeration Unit, a Condenser, and an Evaporation-Absorber Unit.
  • DDGS As a by-product commodity, it is required that DDGS be produced and sold in a dry state or condition, for example, as bulk feed to be used in animal husbandry. Characteristically, and based, for example, upon corn, DDGS is 99% dry substance, 28-31% raw protein, 12-13% raw fat, 10% raw fibers, 5-6% ash, and 41-43% Nitrogen free extract. For example, in the manufacture of Ethanol, the following feed stock can be used: Wheat, Corn, Rice and Sugar. Accordingly, this Freeze Concentration Process is not to be limited to the material processed, whether it be the purification of a primary fluid such as sea and/or brackish water, or other inorganic and organic solutions refining concentrations such as DDGS.
  • a primary fluid such as sea and/or brackish water, or other inorganic and organic solutions refining concentrations such as DDGS.
  • the process involved herein is the vacuum freezing process in which the freezing is accomplished in a stirred tank crystallizer due to the vaporization of water vapor which, in turn, is absorbed in an adjacent chamber by a concentrated solution of sodium chloride (NaCl) diluted by the water vapor pumped to a compressor where it is concentrated to its original strength by vapor compression apparatus using a closed circuit.
  • NaCl sodium chloride
  • a feature is the complementary refrigeration of heat transfer fluid (NaCl) by the steam- jet refrigeration means and by the absorber section of the absorber-freezer means, pumped through parallel closed circuits and passed through a pre-cooler means that lowers the temperature of the dilute feed solution near to freezing. Accordingly, the dilute feed solution is in optimum condition for processing in the freezer section of said absorber-freezer means.
  • heat transfer fluid NaCl
  • a fourth utilitarian processing system advantageously combined with the hybrid power system disclosed herein is the Combined Cycle Gas Turbine Dual Chiller and Ice Thermal Storage System shown in Fig. 6 of the drawings. It is significant that this power system is adapted to be used with any one or all of the aforementioned processing systems as disclosed in Figs. 3, 4 and 5. Accordingly, it will be observed that hot liquid working fluid is available for either or both steam generation of jet processes as shown in Figs. 4 and 5, and also that super-heated steam is available for the chiller process as shown in Fig. 3. Each of these processes cooperate with the hybrid power system with remaining power used for co-generation of electrical power.
  • the hybrid power system disclosed herein is fueled with gas and features a primary gas turbine which is reliable, compact and cost effective, and the producer of shaft power and of a large volume high temperature exhaust.
  • This hybrid system also features a secondary steam turbine which is reliable, compact and cost effective, and the producer of shaft power.
  • the two turbines operate at constant speed (preferably) with torque balanced to the load, dependent upon the equipment or system being operated thereby.
  • the gas turbine and steam turbine are independent, their utility being selective.
  • the gas turbine and steam turbine are cooperatively combined by coupled and geared engagement to a common power output shaft, and in accordance with this invention said power output shaft drives a co- generator that responds to remaining system energy to generate electrical power.
  • These various power sources are made available from this hybrid power system to be implemented individually or simultaneously, and characterized by remaining energy converted into electrical power by co-generation.
  • Fig. 5 is a schematic diagram of a FREEZE CONCENTRATION PROCESS with connections as they are coupled to the system of Fig. 1;
  • FIG. 6 is a schematic diagram of a COMBINED BRAYTON AND RANKINE CYCLE TURBINE POWERED DUAL CHILLER AND ICE THERMAL STORAGE SYSTEM with connections as they are coupled to the system of Fig. 1.
  • this hybrid power system is shown in Fig. 1 to have separately operable turbines GT and ST.
  • Turbine GT operates on the Brayton cycle and turbine ST operates on the Rankine cycle.
  • a feature of this invention is that the heat energy of the high temperature exhaust gas turbine GT is recovered and employed to operate the steam turbine ST. It is essential that the shaft power produced by each turbine be used and employed, and to this end the Fig.
  • thermoelectric generator HWG for producing high temperature water for example 540°F and 12000 p.s.i.
  • steam generator STG for producing super heated steam for example 750°F and 650 p.s.i.
  • the closed circuit heat transfer media flow is in series through the steam generator STG and then through the hot water generator HWG, and return through the heat recovery heater HRH.
  • SHWS super hot water supply
  • a service valve 15 for connection into either one of the process systems as they are disclosed in Figs. 4 and 5.
  • a super heated steam line 16 with a service valve 17 for connection into the process system as disclosed in Fig. 3. It will be observed that the closed circuit 18 of the heat transfer media through pump 13 is confined to circulation from the heat recovery heater HRH through the two generators STG and HWG.
  • the gas turbine GT power shaft is coupled to a base load chiller Cl or the like, by a coupling 20, there being a chilled water supply line (CWSL) for example, at 42°F, and a chilled water return (CHWR) line 22 for example at 52°F.
  • the chiller Cl is connected to a cooling tower CT by a chilled water supply line CWS and by a chilled water return line CWR, and then to tower water circulated by a pump 19.
  • the cooling tower CT is shared by the steam condenser SC from the turbine ST next described.
  • the steam turbine ST power shaft is coupled to the co-generator CG or the like by a coupling 23, the steam discharge of said turbine is into a steam condenser SC supplied with cooling tower water through a coil 24.
  • the condensed water is held in a receiver 25 and is returned to the hot water generator HWG by means of a pump 26.
  • the steam turbine ST is operated by super heated steam for example at 750°F and 650 p.s.i. generated by the steam generator STG that received super heated heat transfer media from the heat recovery heater HRH, thereby flashing the hot water received thereby from the hot water generator HWG.
  • Super heated steam is delivered directly to the steam turbine ST, and to the service valve 17.
  • a dual gear means 30 for receiving the differential shaft velocities of the two turbines, for converting each to a common velocity at an output shaft 31.
  • the gas turbine GT is coupled to an input shaft 32 by means of a clutch 20, and the generator CG is brought up to operating speed as circumstances require.
  • the steam turbine ST is subservient to operation of the gas turbine GT, as it is reliant upon exhaust heat and its transfer into the system.
  • the steam turbine ST is coupled to its output input shaft 33 by means of an over-riding clutch 34, for example a Sprague-type clutch. Therefore, when the steam turbine ST comes up to speed, it then applies torque through the gear means 30 to assist in driving the co-generator CG, or other means, as may be required.
  • FIG. 3 is a double effect system wherein there are two stages of refrigerant reconcentration of the absorbent solution, a first stage high temperature high pressure concentrator HPC and a second stage low pressure low temperature concentrator LPC.
  • the chilling cycle is driven indirectly by the steam application from the service valve 17 of the hybrid power system and generates refrigerant water vapor at a relatively higher temperature and pressure, and the heat of condensation is used to drive the second stage LPC operating at a lower temperature and pressure.
  • the refrigerant mass is boiled out of solution in each of the two stages, thereby substantially increasing the net generation of refrigerant and cooling capability per unit of heat input *
  • the tower is indicated but not shown, nor is the system water distribution shown, both of which are state of the art.
  • the Peltier effect embodiment does not prove itself to be cost effective in providing the necessary hot water for steam-jet refrigeration, and is replaced herein by the direct application of super-heated water from line 14 through the power system service valve 15.
  • the super heated water at 540°F and 1000 p.s.i. is supplied directly to the flash means F of the steam-jet.
  • the high pressure water is passed through said flash chamber for conversion to steam and to reduce its temperature and pressure values to those required for the steam-jet refrigeration that follows.
  • the high temperature strong absorbent is passed through a heat exchanger so as to recover heat into the weak absorbent feed to the generator.
  • the steam-jet refrigeration unit discharges high temperature steam passed through the condenser means to change its condition to liquid and to transfer heat into a space heating circuit when desired.
  • the condenser heat discharge is passed through the cooling tower.
  • the chilled wager is passed through the evaporator section of the chiller-heater means for a further reduction in temperature and thence through a space cooling circuit when required.
  • the evaporator-absorber means has a recirculation circuit for the evaporator section thereof and a recirculation circuit for the absorber section thereto, and it has a chilled water circuit to and from the evaporator section and a heated water circuit to and from the absorber section.
  • Weak absorbent feed to the generator means is from the said absorber section or from the condenser means.
  • the hybrid system of Fig. 6 is the same as that shown and described in Fig. 1, but with the added feature of chiller C2 and the inclusion of ice bank storage. Accordingly, the chiller Cl is driven by the gas turbine GT through clutch 20, while the co-generator CG is driven by the steam turbine ST through clutch 23, all as hereinabove described. As shown, the ice chiller Cl is also driven by the steam turbine ST through a clutch 23'. Gear means is indicated for each drive application, as in Fig. 2 for example. Most efficient use of fuel and energy recovery is attained.

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

Abstract

Cette invention concerne un système de réfrigération et de traitement à carburant, lequel système comprend une première turbine à gaz à cycle Brayton (GT) produisant une force sur un arbre ainsi qu'un produit d'évacuation dont la chaleur est récupérée dans un milieu de transfert (18) fournissant de l'eau à haute température (15) et de la vapeur surchauffée (14). Une seconde turbine à gaz à cycle Rankine (ST) est entraînée par ladite vapeur et produit une force sur un arbre qui est envoyée à un générateur (CG). Chacune de ces turbines entraînent des compresseurs de réfrigération (C1, C2), fournissant ainsi et de manière sélective de l'eau chaude (15), de la vapeur (14), de l'eau glacée (21), de la glace et de l'électricité (CG), en fonction des besoins.
PCT/US1996/005931 1995-06-06 1996-04-29 Dispositif de refroidissement et de refrigeration alimente par gaz et vapeur ou a turbine, et systemes de cogeneration WO1996039577A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU56323/96A AU5632396A (en) 1995-06-06 1996-04-29 Gas and steam powered or jet refrigeration chiller and co-ge neration systems

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US46640195A 1995-06-06 1995-06-06
US08/466,401 1995-06-06
US08/635,756 US6050083A (en) 1995-04-24 1996-04-22 Gas turbine and steam turbine powered chiller system
US08/635,756 1996-04-22

Publications (1)

Publication Number Publication Date
WO1996039577A1 true WO1996039577A1 (fr) 1996-12-12

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WO (1) WO1996039577A1 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1016775A3 (fr) * 1998-12-31 2001-10-17 Ormat Industries, Ltd. Récupération de chaleur dans un convertisseur d'énergie organique utilisant un cycle de liquide intermédiare
US6880344B2 (en) 2002-11-13 2005-04-19 Utc Power, Llc Combined rankine and vapor compression cycles
US6892522B2 (en) 2002-11-13 2005-05-17 Carrier Corporation Combined rankine and vapor compression cycles
US6962056B2 (en) 2002-11-13 2005-11-08 Carrier Corporation Combined rankine and vapor compression cycles
WO2005071231A3 (fr) * 2004-01-23 2006-01-19 York Int Corp Commande de capacite adaptative integree pour une unite de refroidissement commandee par turbine a vapeur
US7146813B2 (en) 2002-11-13 2006-12-12 Utc Power, Llc Power generation with a centrifugal compressor
US7174716B2 (en) 2002-11-13 2007-02-13 Utc Power Llc Organic rankine cycle waste heat applications
US7254949B2 (en) 2002-11-13 2007-08-14 Utc Power Corporation Turbine with vaned nozzles
US7281379B2 (en) 2002-11-13 2007-10-16 Utc Power Corporation Dual-use radial turbomachine
DE102009037570B4 (de) * 2009-08-14 2013-04-04 Deutsches Zentrum für Luft- und Raumfahrt e.V. Verfahren und Vorrichtung zur solarthermischen Gefrierentsalzung von Meer- oder Brackwasser
WO2020019922A1 (fr) * 2018-07-23 2020-01-30 南京航空航天大学 Système et procédé de cogénération de concentration de solution de pompe à chaleur
WO2021150580A1 (fr) * 2020-01-23 2021-07-29 Rocky Research Système de refroidissement flexible à accumulation d'énergie thermique
US11543216B2 (en) 2017-03-06 2023-01-03 Rocky Research Burst mode cooling for directed energy systems

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* Cited by examiner, † Cited by third party
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US1993585A (en) * 1933-07-06 1935-03-05 Gen Electric Mercury vapor generating plant
US3421978A (en) * 1966-04-29 1969-01-14 Commissariat Energie Atomique Thermal power plant and method of operation
US3500636A (en) * 1966-02-18 1970-03-17 Ass Elect Ind Gas turbine plants
US4290273A (en) * 1980-02-13 1981-09-22 Milton Meckler Peltier effect absorption chiller-heat pump system
US4328677A (en) * 1980-09-23 1982-05-11 Milton Meckler Peltier freeze concentration process
US4907405A (en) * 1989-01-24 1990-03-13 Union Carbide Corporation Process to cool gas

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1993585A (en) * 1933-07-06 1935-03-05 Gen Electric Mercury vapor generating plant
US3500636A (en) * 1966-02-18 1970-03-17 Ass Elect Ind Gas turbine plants
US3421978A (en) * 1966-04-29 1969-01-14 Commissariat Energie Atomique Thermal power plant and method of operation
US4290273A (en) * 1980-02-13 1981-09-22 Milton Meckler Peltier effect absorption chiller-heat pump system
US4328677A (en) * 1980-09-23 1982-05-11 Milton Meckler Peltier freeze concentration process
US4907405A (en) * 1989-01-24 1990-03-13 Union Carbide Corporation Process to cool gas

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1016775A3 (fr) * 1998-12-31 2001-10-17 Ormat Industries, Ltd. Récupération de chaleur dans un convertisseur d'énergie organique utilisant un cycle de liquide intermédiare
US7735324B2 (en) 2002-11-13 2010-06-15 Carrier Corporation Power generation with a centrifugal compressor
US6892522B2 (en) 2002-11-13 2005-05-17 Carrier Corporation Combined rankine and vapor compression cycles
US6962056B2 (en) 2002-11-13 2005-11-08 Carrier Corporation Combined rankine and vapor compression cycles
US6880344B2 (en) 2002-11-13 2005-04-19 Utc Power, Llc Combined rankine and vapor compression cycles
US7146813B2 (en) 2002-11-13 2006-12-12 Utc Power, Llc Power generation with a centrifugal compressor
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