US3400555A - Refrigeration system employing heat actuated compressor - Google Patents

Refrigeration system employing heat actuated compressor Download PDF

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US3400555A
US3400555A US547038A US54703866A US3400555A US 3400555 A US3400555 A US 3400555A US 547038 A US547038 A US 547038A US 54703866 A US54703866 A US 54703866A US 3400555 A US3400555 A US 3400555A
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condenser
compressor
fluid
evaporator
motor
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US547038A
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Eric G U Granryd
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American Gas Association Inc
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American Gas Association Inc
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Priority to US547038A priority Critical patent/US3400555A/en
Priority to ES340005A priority patent/ES340005A1/en
Priority to SE06137/67A priority patent/SE336361B/xx
Priority to BE697875D priority patent/BE697875A/xx
Priority to AT409767A priority patent/AT295564B/en
Priority to NL6706157A priority patent/NL6706157A/xx
Priority to GB20329/67A priority patent/GB1196472A/en
Priority to FR104862A priority patent/FR1521290A/en
Priority to DE19671551304 priority patent/DE1551304A1/en
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    • 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
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • 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
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure

Definitions

  • a closed cooling system includes a conduit and a cooling medium-of carbon dioxide or sulfur dioxide.
  • An evaporator is connected to the conduit and perates at a relativelylow pressure.
  • a heat actuated compressor increases the pressure of the cooling medium passing from the evaporator at a relatively low pressure to a relatively high pressure.
  • a condenser is connected to receive the coOling medium passing from the compressor. The cooling medium passes from the condenser in a high pressure, condensed condition.
  • a fluid operated motor is connected to the conduit between the con-denser and the evaporator and the fluid motor is mechanically operated by the flow of the condensed fluid passing through the motor from the condenser to the evaporator.
  • the flow of the cooling medium through the fluid motor provides useful mechanical energy for the fluid motor and the cooling capacity of the system is increased.
  • This invention relates to a novel improvement in airconditioning and refrigeration systems and, in particular, to an improved air-conditioning system with a heat-actuated compressor.
  • Typical air-conditioning and refrigeration systems comprise four basic elements: A compressor for taking a gas at a first relatively low pressure and compressing it to a second relatively high pressure; a condenser, normally water or air-cooled, for cooling and liquefying the compressed gas to remove the latent heat of evaporization; a throttle valve through which the liquefied gas is expanded into a zone of relatively low pressure; and an evaporator in which the expanded gas absorbs its latent heat of vaporization from the surroundings to be cooled.
  • Air-conditioning and refrigeration cycles for systems using gases such as carbon dioxide as refrigerant have low thermodynamic efficiency because the state of the refrigerant in the condenser is supercritical. Expansion of refrigerant such as carbon dioxide through a throttle valve results in wasteful loss of cooling capacity of the system due to unfavorable temperature-entropy considerations, more fully discussed hereinafter.
  • the object of this invention is to provide a modified and improved cycle for an air-conditioning or refrigeration system with a heat-actuated compressor wherein the cooling capacity of the system is increased, While at the same time useful mechanical work is obtained from the system.
  • FIG. 1 is a diagrammatic view showing an air-conditioning 0r refrigeration system according to the invention.
  • FIG. 2 is a temperature-entropy diagram for carbon dioxide illustrating the advantages of my system.
  • My invention comprises using a fluid-actuated motor to control the flow of fluid carbon dioxide between the condenser of the cooling system and the evaporator rather than using a throttling valve as is conventional practice.
  • a fluid-actuated motor to control the flow of fluid carbon dioxide between the condenser of the cooling system and the evaporator rather than using a throttling valve as is conventional practice.
  • Considerable improvement is the performance of a carbon dioxide air-conditioning or refrigeration system can be achieved by the arrangement of my invention which is Patented Sept. 10, 1968 shown diagrammatically in FIG. 1 wherein a fluid motor is placed between the high-pressure source (condenser) and the low-pressure source (evaporator) in an air-conditioning or refrigeration system and is driven by fluid passing from the condenser to the evaporator.
  • the fluid motor may be any type of motor well known in the art capable of being driven by a pressurized fluid flowing from a region of high-pressure source to a region of low-pressure.
  • 'a fluid motor as above described is particularly advantageous in a system employing carbon dioxide as refrigerant while systems using other refrigerants, such as S0 provide only a small mechanical output due to temperature-entropy considerations.
  • my system has distinct advantages over an air cycle-conditioning system in which a turbine is arranged similarly to the fluid motor of my system.
  • the system is an open system using air as the working fluid, the air being in gaseous state throughout the cycle, whereas in my system, the refrigerant is liquefied or rendered supercritical while circulating through the condenser of the system.
  • the mechanical output of the fluid motor per ton of refrigeration can be varied over Wide limits depending on temperatures and pressures in the system. For example, as one limit, if no heat exchange takes place in the condenser, the system is converted to a power generation system.
  • FIG. 2 is a temperature-entropy diagram for carbon dioxide.
  • line 2 of FIG. 2 illustrates the entropy change of a system using a throttling valve when the fluid carbon dioxide at 1450 p.s.i.a. in the condenser is throttled down to 600 p.s.i.a. in the evaporator.
  • the slope of line 2 shows the relatively large increase in entropy associated with the irreversible throttling process.
  • line 1 shows the entropy change associated with use of the fluid motor arrangement of my invention. Note that the entropy change is small as compared to the throttling process.
  • the total area A plus B in FIG. 2 represents the cooling capacity of the system using the fluid motor arrangement of my invention.
  • Area B represents the equivalent of the mechanical output of the fluid motor and also the improvement in cooling capacity using the motor compared to the capacity of a system using a throttling valve instead of the fluid motor.
  • the system of my invention provides not only for increased cooling capacity but in addition for available mechanical work for use in auxiliary parts of the overall cooling system, such as for running fans or operating the compressor as above noted.
  • the system of my invention it is possible to vary the temperature to which the highly compressed CO is cooled in the condenser, and in this way vary the ratio of mechanical work 'and cooling effect which can be gotten from the compressed fluid by use of the fluid motor and the evaporator.
  • the system is operated as 'a power-generator system.
  • the compressed fluid can he cooled to varying degrees in the condenser and the system correspondingly operates as a combined cooling system and power generation system.
  • a closed cooling system comprising conduit means, a cooling medium selected from the group consisting of carbon dioxide and sulfur dioxide and passing through said conduit means, an evaporator connected to said conduit means, and being operated at a relatively low pressure, a heat actuated compressor connected in said conduit means for increasing the pressure of the cooling medium passing from said evaporator at a relatively low pressure to a relatively high pressure, a condenser connected to said conduit means and being operated at a relatively high pressure, said cooling medium passing from said compressor to said condenser and passing from said condenser in a relatively high pressure and condensed condition, and a fluid operated :motor connected to said conduit means between said condenser and said evaporator, said fluid motor being mechanically operated by the flow of said relatively high pressure condensed cooling medium passing therethrough from said condenser to said evaporator, the flow of said cooling medium through said fluid motor providing useful mechanical energy for said fluid motor and the cooling capacity of said system is increased.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

Sept. 10, 1968 REFRIGERATION E. G. U. GRANRYD SYSTEM EMPLOYING HEAT ACTUATED COMPRESSOR Filed May 2. 1966 C ONOENSER FL U/D MOTOR TEMPERATURE, T'
H. A. l?- C. COMPRESSOR FOR CARBON DIOXIDE TYPICAL TEMPERATURE-ENTROPY D/A GRAM FOR COOL/N6 CYCLE E VA POAA TOR 1450 PS/A ERIC 6. U. GRANRYD BY M, 7LW
ATTORNEYS United States Patent 3,400,555 REFRIGERATION SYSTEM EMPLOYING HEAT ACTUATED COMPRESSOR Eric G. U. Granryd, Chicago, Ill., assignor, by mesne assignments, to American Gas Association, Inc., New
York, N.Y., a not-for-profit corporation of New York Filed May 2, 1966, Ser. No. 547,038 3 Claims. (Cl. 62-498) ABSTRACT OF THE DISCLOSURE A closed cooling system. The system includes a conduit and a cooling medium-of carbon dioxide or sulfur dioxide. An evaporator is connected to the conduit and perates at a relativelylow pressure. A heat actuated compressor increases the pressure of the cooling medium passing from the evaporator at a relatively low pressure to a relatively high pressure. A condenser is connected to receive the coOling medium passing from the compressor. The cooling medium passes from the condenser in a high pressure, condensed condition. A fluid operated motor is connected to the conduit between the con-denser and the evaporator and the fluid motor is mechanically operated by the flow of the condensed fluid passing through the motor from the condenser to the evaporator. The flow of the cooling medium through the fluid motor provides useful mechanical energy for the fluid motor and the cooling capacity of the system is increased.
This invention relates to a novel improvement in airconditioning and refrigeration systems and, in particular, to an improved air-conditioning system with a heat-actuated compressor.
Typical air-conditioning and refrigeration systems comprise four basic elements: A compressor for taking a gas at a first relatively low pressure and compressing it to a second relatively high pressure; a condenser, normally water or air-cooled, for cooling and liquefying the compressed gas to remove the latent heat of evaporization; a throttle valve through which the liquefied gas is expanded into a zone of relatively low pressure; and an evaporator in which the expanded gas absorbs its latent heat of vaporization from the surroundings to be cooled.
Air-conditioning and refrigeration cycles for systems using gases such as carbon dioxide as refrigerant have low thermodynamic efficiency because the state of the refrigerant in the condenser is supercritical. Expansion of refrigerant such as carbon dioxide through a throttle valve results in wasteful loss of cooling capacity of the system due to unfavorable temperature-entropy considerations, more fully discussed hereinafter.
The object of this invention is to provide a modified and improved cycle for an air-conditioning or refrigeration system with a heat-actuated compressor wherein the cooling capacity of the system is increased, While at the same time useful mechanical work is obtained from the system.
In the drawings:
FIG. 1 is a diagrammatic view showing an air-conditioning 0r refrigeration system according to the invention; and
FIG. 2 is a temperature-entropy diagram for carbon dioxide illustrating the advantages of my system.
My invention comprises using a fluid-actuated motor to control the flow of fluid carbon dioxide between the condenser of the cooling system and the evaporator rather than using a throttling valve as is conventional practice. Considerable improvement is the performance of a carbon dioxide air-conditioning or refrigeration system can be achieved by the arrangement of my invention which is Patented Sept. 10, 1968 shown diagrammatically in FIG. 1 wherein a fluid motor is placed between the high-pressure source (condenser) and the low-pressure source (evaporator) in an air-conditioning or refrigeration system and is driven by fluid passing from the condenser to the evaporator.
The fluid motor may be any type of motor well known in the art capable of being driven by a pressurized fluid flowing from a region of high-pressure source to a region of low-pressure.
The use of 'a fluid motor as above described is particularly advantageous in a system employing carbon dioxide as refrigerant while systems using other refrigerants, such as S0 provide only a small mechanical output due to temperature-entropy considerations. In addition, my system has distinct advantages over an air cycle-conditioning system in which a turbine is arranged similarly to the fluid motor of my system. In the air cycle scheme, the system is an open system using air as the working fluid, the air being in gaseous state throughout the cycle, whereas in my system, the refrigerant is liquefied or rendered supercritical while circulating through the condenser of the system.
Use of CO as refrigerant in conjunction with a heatactuated regenerative compressor, as described in my copending application Ser. No. 547,040 filed May 2, 1966, results in a mechanical output from the fluid motor of about 1 HR in a 3-ton air-conditioning system, assuming motor efficiency to be 70%. In addition, the co-efficient of performance of the cooling cycle simultaneously is improved about 7%. My system using carbon dioxide as refrigerant can be made completely self-sufficient, i.e. the work done by the fluid motor is sufficient to satisfy the mechanical energy requirements of the heat-actuated regenerative compressor as well as the necessary fans in the system.
The mechanical output of the fluid motor per ton of refrigeration can be varied over Wide limits depending on temperatures and pressures in the system. For example, as one limit, if no heat exchange takes place in the condenser, the system is converted to a power generation system.
The reason for the advantages of the system of my invention can best be seen by referring to FIG. 2 which is a temperature-entropy diagram for carbon dioxide. Assuming a cooling system in which the condenser operates at 1450 p.s.-i.a. and the evaporator at 600 p.s.i.a., line 2 of FIG. 2 illustrates the entropy change of a system using a throttling valve when the fluid carbon dioxide at 1450 p.s.i.a. in the condenser is throttled down to 600 p.s.i.a. in the evaporator. The slope of line 2 shows the relatively large increase in entropy associated with the irreversible throttling process.
On the other hand, line 1 shows the entropy change associated with use of the fluid motor arrangement of my invention. Note that the entropy change is small as compared to the throttling process.
The total area A plus B in FIG. 2 represents the cooling capacity of the system using the fluid motor arrangement of my invention. Area B represents the equivalent of the mechanical output of the fluid motor and also the improvement in cooling capacity using the motor compared to the capacity of a system using a throttling valve instead of the fluid motor. As can be seen from FIG. 2, the system of my invention provides not only for increased cooling capacity but in addition for available mechanical work for use in auxiliary parts of the overall cooling system, such as for running fans or operating the compressor as above noted.
By using the system of my invention, it is possible to vary the temperature to which the highly compressed CO is cooled in the condenser, and in this way vary the ratio of mechanical work 'and cooling effect which can be gotten from the compressed fluid by use of the fluid motor and the evaporator. For example, as noted above, if no heat exchange takes place in the condenser, the system is operated as 'a power-generator system. Alternatively, the compressed fluid can he cooled to varying degrees in the condenser and the system correspondingly operates as a combined cooling system and power generation system.
Those skilled in the art will recognize that various modifications can be made to the principle of my invention within the scope thereof which I intend to be limited solely by the following claims.
I claim:
1. A closed cooling system comprising conduit means, a cooling medium selected from the group consisting of carbon dioxide and sulfur dioxide and passing through said conduit means, an evaporator connected to said conduit means, and being operated at a relatively low pressure, a heat actuated compressor connected in said conduit means for increasing the pressure of the cooling medium passing from said evaporator at a relatively low pressure to a relatively high pressure, a condenser connected to said conduit means and being operated at a relatively high pressure, said cooling medium passing from said compressor to said condenser and passing from said condenser in a relatively high pressure and condensed condition, and a fluid operated :motor connected to said conduit means between said condenser and said evaporator, said fluid motor being mechanically operated by the flow of said relatively high pressure condensed cooling medium passing therethrough from said condenser to said evaporator, the flow of said cooling medium through said fluid motor providing useful mechanical energy for said fluid motor and the cooling capacity of said system is increased.
2. The system of claim 1 wherein said compressor is a heat actuated regenerative compressor and said fluid motor is operatively connected to said heat actuated regenerative compressor to provide mechanical energy for the operation thereof.
3. The system of claim 2 wherein said cooling medium is carbon dioxide.
' References Cited UNITED STATES PATENTS 1,440,000 12/1922 Bonine 62-402 2,157,229 5/1939 Bush 626 2,494,120 1/1950 Ferro 62493 3,115,014 12/1963 Hogan 626 MEYER PERLIN, Primary Examiner.
US547038A 1966-05-02 1966-05-02 Refrigeration system employing heat actuated compressor Expired - Lifetime US3400555A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
US547038A US3400555A (en) 1966-05-02 1966-05-02 Refrigeration system employing heat actuated compressor
ES340005A ES340005A1 (en) 1966-05-02 1967-04-29 Refrigeration system employing heat actuated compressor
BE697875D BE697875A (en) 1966-05-02 1967-05-02
AT409767A AT295564B (en) 1966-05-02 1967-05-02 Cooling method and apparatus for carrying out the same
SE06137/67A SE336361B (en) 1966-05-02 1967-05-02
NL6706157A NL6706157A (en) 1966-05-02 1967-05-02
GB20329/67A GB1196472A (en) 1966-05-02 1967-05-02 Cooling System
FR104862A FR1521290A (en) 1966-05-02 1967-05-02 Air conditioning device
DE19671551304 DE1551304A1 (en) 1966-05-02 1967-05-02 Air conditioning with heat-operated compressor

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DE (1) DE1551304A1 (en)
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GB (1) GB1196472A (en)
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SE (1) SE336361B (en)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3580003A (en) * 1968-08-14 1971-05-25 Inst Of Gas Technology The Cooling apparatus and process for heat-actuated compressors
US4205532A (en) * 1977-05-02 1980-06-03 Commercial Refrigeration (Wiltshire) Limited Apparatus for and method of transferring heat
US4235079A (en) * 1978-12-29 1980-11-25 Masser Paul S Vapor compression refrigeration and heat pump apparatus
EP0048139A1 (en) * 1980-09-16 1982-03-24 The Calor Group Limited Pumping arrangements
WO1990007683A1 (en) * 1989-01-09 1990-07-12 Sinvent As Trans-critical vapour compression cycle device
WO1991002885A1 (en) * 1989-08-18 1991-03-07 Glen John S Heat engine, refrigeration and heat pump cycles approximating the carnot cycle and apparatus therefor
US5027602A (en) * 1989-08-18 1991-07-02 Atomic Energy Of Canada, Ltd. Heat engine, refrigeration and heat pump cycles approximating the Carnot cycle and apparatus therefor
WO1993006423A1 (en) * 1991-09-16 1993-04-01 Sinvent A/S Method of high-side pressure regulation in transcritical vapor compression cycle device
US5245836A (en) * 1989-01-09 1993-09-21 Sinvent As Method and device for high side pressure regulation in transcritical vapor compression cycle
WO2003102478A1 (en) * 2002-05-29 2003-12-11 Carrier Corporation Expander driven motor for auxiliary machinery
US20040003622A1 (en) * 2002-04-15 2004-01-08 Masami Negishi Refrigerating cycle system using carbon dioxide as refrigerant
EP1389720A1 (en) * 2002-08-12 2004-02-18 Praxair Technology, Inc. Supercritical Refrigeration System
WO2004072567A2 (en) * 2003-02-12 2004-08-26 Carrier Corporation Supercritical pressure regulation of vapor compression system
US20050044865A1 (en) * 2003-09-02 2005-03-03 Manole Dan M. Multi-stage vapor compression system with intermediate pressure vessel
US20050044864A1 (en) * 2003-09-02 2005-03-03 Manole Dan M. Apparatus for the storage and controlled delivery of fluids
US20050132729A1 (en) * 2003-12-23 2005-06-23 Manole Dan M. Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
US20140150443A1 (en) * 2012-12-04 2014-06-05 General Electric Company Gas Turbine Engine with Integrated Bottoming Cycle System

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3338039C2 (en) * 1983-10-20 1985-11-07 Helmut 2420 Eutin Krueger-Beuster Compression refrigeration machine or heat pump

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1440000A (en) * 1920-05-03 1922-12-26 Charles E Bonine Refrigeration
US2157229A (en) * 1935-07-17 1939-05-09 Research Corp Apparatus for compressing gases
US2494120A (en) * 1947-09-23 1950-01-10 Phillips Petroleum Co Expansion refrigeration system and method
US3115014A (en) * 1962-07-30 1963-12-24 Little Inc A Method and apparatus for employing fluids in a closed cycle

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1440000A (en) * 1920-05-03 1922-12-26 Charles E Bonine Refrigeration
US2157229A (en) * 1935-07-17 1939-05-09 Research Corp Apparatus for compressing gases
US2494120A (en) * 1947-09-23 1950-01-10 Phillips Petroleum Co Expansion refrigeration system and method
US3115014A (en) * 1962-07-30 1963-12-24 Little Inc A Method and apparatus for employing fluids in a closed cycle

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3580003A (en) * 1968-08-14 1971-05-25 Inst Of Gas Technology The Cooling apparatus and process for heat-actuated compressors
US4205532A (en) * 1977-05-02 1980-06-03 Commercial Refrigeration (Wiltshire) Limited Apparatus for and method of transferring heat
US4235079A (en) * 1978-12-29 1980-11-25 Masser Paul S Vapor compression refrigeration and heat pump apparatus
EP0048139A1 (en) * 1980-09-16 1982-03-24 The Calor Group Limited Pumping arrangements
WO1990007683A1 (en) * 1989-01-09 1990-07-12 Sinvent As Trans-critical vapour compression cycle device
US5245836A (en) * 1989-01-09 1993-09-21 Sinvent As Method and device for high side pressure regulation in transcritical vapor compression cycle
WO1991002885A1 (en) * 1989-08-18 1991-03-07 Glen John S Heat engine, refrigeration and heat pump cycles approximating the carnot cycle and apparatus therefor
US5027602A (en) * 1989-08-18 1991-07-02 Atomic Energy Of Canada, Ltd. Heat engine, refrigeration and heat pump cycles approximating the Carnot cycle and apparatus therefor
WO1993006423A1 (en) * 1991-09-16 1993-04-01 Sinvent A/S Method of high-side pressure regulation in transcritical vapor compression cycle device
US20040003622A1 (en) * 2002-04-15 2004-01-08 Masami Negishi Refrigerating cycle system using carbon dioxide as refrigerant
WO2003102478A1 (en) * 2002-05-29 2003-12-11 Carrier Corporation Expander driven motor for auxiliary machinery
EP1389720A1 (en) * 2002-08-12 2004-02-18 Praxair Technology, Inc. Supercritical Refrigeration System
EP1592931A2 (en) * 2003-02-12 2005-11-09 Carrier Corporation Supercritical pressure regulation of vapor compression system
WO2004072567A3 (en) * 2003-02-12 2004-12-02 Carrier Corp Supercritical pressure regulation of vapor compression system
WO2004072567A2 (en) * 2003-02-12 2004-08-26 Carrier Corporation Supercritical pressure regulation of vapor compression system
US20050044865A1 (en) * 2003-09-02 2005-03-03 Manole Dan M. Multi-stage vapor compression system with intermediate pressure vessel
US20050044864A1 (en) * 2003-09-02 2005-03-03 Manole Dan M. Apparatus for the storage and controlled delivery of fluids
US6923011B2 (en) 2003-09-02 2005-08-02 Tecumseh Products Company Multi-stage vapor compression system with intermediate pressure vessel
US6959557B2 (en) 2003-09-02 2005-11-01 Tecumseh Products Company Apparatus for the storage and controlled delivery of fluids
US20050132729A1 (en) * 2003-12-23 2005-06-23 Manole Dan M. Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
US7096679B2 (en) 2003-12-23 2006-08-29 Tecumseh Products Company Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
US20140150443A1 (en) * 2012-12-04 2014-06-05 General Electric Company Gas Turbine Engine with Integrated Bottoming Cycle System
US9410451B2 (en) * 2012-12-04 2016-08-09 General Electric Company Gas turbine engine with integrated bottoming cycle system

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NL6706157A (en) 1967-11-03
GB1196472A (en) 1970-06-24
ES340005A1 (en) 1968-12-01
SE336361B (en) 1971-07-05
DE1551304A1 (en) 1970-03-05
AT295564B (en) 1972-01-10
BE697875A (en) 1967-10-16

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