EP0152308A2 - Dampfkreislaufsystem - Google Patents

Dampfkreislaufsystem Download PDF

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Publication number
EP0152308A2
EP0152308A2 EP85301016A EP85301016A EP0152308A2 EP 0152308 A2 EP0152308 A2 EP 0152308A2 EP 85301016 A EP85301016 A EP 85301016A EP 85301016 A EP85301016 A EP 85301016A EP 0152308 A2 EP0152308 A2 EP 0152308A2
Authority
EP
European Patent Office
Prior art keywords
working fluid
receiver
jet pump
fluid
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.)
Withdrawn
Application number
EP85301016A
Other languages
English (en)
French (fr)
Other versions
EP0152308A3 (de
Inventor
George Ernest Carpenter (deceased), legally represented by Carpenter, Mary Isobel and Martin, Alice
Robert John Edwards
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.)
CARPENTER, GEORGE ERNEST (DECEASED), LEGALLY REPRE
Original Assignee
George Ernest Carpenter (deceased), legally represented by Carpenter, Mary Isobel and Martin, Alice
Robert John Edwards
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by George Ernest Carpenter (deceased), legally represented by Carpenter, Mary Isobel and Martin, Alice, Robert John Edwards filed Critical George Ernest Carpenter (deceased), legally represented by Carpenter, Mary Isobel and Martin, Alice
Publication of EP0152308A2 publication Critical patent/EP0152308A2/de
Publication of EP0152308A3 publication Critical patent/EP0152308A3/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/06—Compression machines, plants or systems with non-reversible cycle with compressor of jet type, e.g. using liquid under pressure
    • F25B1/08—Compression machines, plants or systems with non-reversible cycle with compressor of jet type, e.g. using liquid under pressure using vapour under pressure

Definitions

  • the present invention relates to an improved vapour cycle system in particular, but not exclusively, for use in air conditioning and refrigeration plants.
  • the vapour cycle system may be used to heat or to cool its surroundings, depending on the way it is connected.
  • the vapour cycle system of refrigeration has been in use for more than a century and its method of operation is based on the Carnot thermodynamic cycle.
  • a working fluid in its liquid state is stored in a receiver or reservoir.
  • the liquid working fluid is fed into an evaporator over or through which a medium to be cooled is passed.
  • the pressure in the evaporator is maintained below the desired saturation vapour pressure of the working fluid.
  • the working fluid therefore extracts the latent heat needed to vaporise it from the medium to be cooled, thus vaporising the working fluid and cooling the medium.
  • the vapourised working fluid is drawn out of the evaporator and is compressed.
  • the hot pressurised gas thus formed which is a superheated vapour, is fed to a condenser, where the hot gas is cooled, for instance by passing a medium to be heated over or through the condenser, thereby causing the vaporised working fluid to condense to a liquid at a desired temperature and pressure.
  • the condensed liquid working fluid is then fed to the receiver for recycling.
  • the vapour cycle system can be used for cooling or refrigeration, by use of the medium to be cooled, or for heating, by using the heat extracted during condensation of the superheated vapour.
  • the low pressure in the evaporator ⁇ and the compression of the vaporised working fluid is normally achieved by use of a mechanical compressor which may, for instance, be driven electrically or by an internal combustion engine.
  • Using a mechanical compressor is disadvantageous oecause it involves the use of moving parts, therefore requiring maintenance or replacement. Also the use of a mechanical compressor requires a large amount of energy, which can make the operation of the vapour cycle system expensive.
  • an improved vapour cycle system comprising:
  • the material exiting from the jet pump will comprise vaporised working fluid which may also contain some condensed working fluid. It is therefore preferred that the system includes a condenser for receiving hot pressurised gas exiting from said jet pump to condense said working fluid, and for feeding said working fluid to said receiver.
  • the evaporator may be of any conventional type and receives heat from a medium to be cooled, such as water or air, which may be passed over or through it.
  • the medium to be cooled may be used to cool or refrigerate the surroundings of the system.
  • Jet pumps which are also known as suction pumps or ejectors, are well known.
  • a jet pump comprises a nozzle, a mixing chamber and a diffuser.
  • the nozzle is connected to a source of high pressure gas which is injected into the mixing chamber at high velocity. This creates a pressure drop in the mixing chamber.
  • the high velocity flow of gas from the heat exchanger through the nozzle causes a reduction in the pressure in the evaporator, thereby allowing the evaporation of the working fluid and the cooling of the medium.
  • the evaporated working fluid is then also entrained in the high velocity flow of gas which then passes to the diffuser where the velocity energy of the gas is converted into pressure energy. Therefore, the gas exiting from the jet pump is at high pressure and is heated by the latent heat of evaporation of the working fluid extracted from the medium to be cooled.
  • Any of the know forms of jet pump may be used in the improved system of the present invention.
  • the condenser may, for example, be located in a cooling medium, such as air or water, or may have the cooling medium passing over or through it.
  • the cooling medium after receiving heat from the condenser may be used for instance for space heating.
  • the working fluid is different from the entraining fluid, it will be necessary to separate the two fluids before they are recycled. However, it is preferred that the entraining fluid is the same as the working fluid and that the condenser is connected directly to the receiver.
  • the jet pump is located in a heat balance chamber to ensure that the gas exiting therefrom is at optimum temperature and pressure.
  • the heat exchanger may receive all the heat needed to operate the system directly from an external heat source.
  • the hot gas exiting from the jet pump is also passed through the heat exchanger which therefore supplies heat to both the entraining gas and the exiting hot gas.
  • the working fluid and the entraining fluid will be one or a mixture of the fluorocarbon or chlorofluorocarbon gases commonly used in refrigeration systems. Such gases are available under the trade name "Freon”.
  • the improved vapour cycle system of the present invention may, if desired, include further heat exchangers and/or condensers and/or heat balance chambers to optimise the thermal performance of the system or to utilize more effectively waste heat from external sources or the heated and cooled fluids produced by the system.
  • further heat exchangers and/or condensers and/or heat balance chambers to optimise the thermal performance of the system or to utilize more effectively waste heat from external sources or the heated and cooled fluids produced by the system.
  • valves such as one-way valves, control valves and bleed valves, for controlling the operation of the system.
  • control valves such as one-way valves, control valves and bleed valves
  • the improved vapour cycle system of the present invention can be operated by providing only an external source of heat. This may be derived from exhaust heat from internal combustion engines or steam generating plant, waste heat from industrial processes or electricity generating stations, or from solar power.
  • the system does not require any compressors or pumps, and is therefore energy efficient. Moreover, it has no moving parts and is therefore less prone to break down and does not require frequent maintenance.
  • the improved vapour cycle system of the present invention will be useful in cooling aircraft while they are on the ground and heating or cooling aircraft while in flight, for providing air conditioning and/or refrigeration on board ships and for providing air conditioning in factories, offices or homes. It is to be understood that air conditioning includes heating or cooling the ambient atmosphere.
  • a receiver 1 for storing a working fluid comprising a "Freon" fluorocarbon gas.
  • the working fluid is fed to an evaporator 3 and also to a heat exchanger 5.
  • the evaporator 3 is connected to the mixing chamber of a jet pump 7 located in a heat balance chamber 9.
  • the nozzle of the jet pump 7 is connected to the heat exchanger 5.
  • the system also includes an equalizing line 13 between the condenser 12 and the heat exchanger 5, having in it an automatic pressure valve 15.
  • the valve 15 responds to varying pressure in the condenser 12 to prevent the system from reaching equilibrium and therefore stopping the cycle.
  • the system also includes other regulating valves in various of the lines to regulate the flows of liquid and vaporised working fluid in the system.
  • the operation of these valves will be evident to a person skilled in the art and are therefore not referred to further herein.
  • the system may also include a second heat exchanger, for instance located in the line between the jet pump 7 and the first heat exchanger 5. Fluid heated in the second heat exchanger may be passed to a second circuit in the first heat exchanger to further heat the working fluid.
  • a second heat exchanger for instance located in the line between the jet pump 7 and the first heat exchanger 5. Fluid heated in the second heat exchanger may be passed to a second circuit in the first heat exchanger to further heat the working fluid.
  • working fluid is passed to the heat exchanger 5 and heated therein to produce vaporised fluid at high pressure and temperature (in a manner described below).
  • Working fluid is also passed to the evaporator 3, over which a medium to be cooled is flowing.
  • the hot pressurised vapour is fed to the nozzle of the jet pump 7 and is injected as a high velocity stream into the mixing chamber. This causes a reduction in the pressure in the evaporator 3, and as the gas pressure falls, the temperature thereof falls, causing an initial cooling of the medium flowing over the evaporator. As the pressure is reduced and gas is drawn out of the evaporator 3, working fluid in the evaporator 3' vaporises, thus causing a second stage of cooling of the medium.
  • the vaporised working fluid in the evaporator 3 is entrained in the high velocity flow of working fluid in the mixing chamber.
  • the mixed flows of working fluid pass to the diffuser of the jet pump 7 wherein the velocity energy is converted to pressure energy.
  • the mixed flow is then fed to the secondary circuit of heat exchanger 5 which receives heat from an external heat source, such as the exhaust gases from an internal combustion engine (not shown), wherein it is heated to above the saturation temperature required at condenser 12.
  • an external heat source such as the exhaust gases from an internal combustion engine (not shown)
  • This mixed flow is then fed to the condenser 12, over which an external cooling medium is flowing, wherein it is cooled sufficiently to cause the working fluid to condense.
  • the cooling medium is heated up by the condenser 12.
  • the condensed working fluid is recycled to the receiver 1.
  • the medium to be cooled, after passing over the evaporator 3 is used to effect the cooling or refrigeration.
  • the external cooling medium after passing over the condenser 12 is used to effect the heating.
  • the improved vapour cycle system of the present invention can be used without the need for mechanical pumps or compressors, has no moving parts, and can use waste heat or heat from readily available sources as the only energy input.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Sorption Type Refrigeration Machines (AREA)
EP85301016A 1984-02-16 1985-02-15 Dampfkreislaufsystem Withdrawn EP0152308A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB848404112A GB8404112D0 (en) 1984-02-16 1984-02-16 Vapour cycle system
GB8404112 1984-02-16

Publications (2)

Publication Number Publication Date
EP0152308A2 true EP0152308A2 (de) 1985-08-21
EP0152308A3 EP0152308A3 (de) 1986-02-26

Family

ID=10556705

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85301016A Withdrawn EP0152308A3 (de) 1984-02-16 1985-02-15 Dampfkreislaufsystem

Country Status (2)

Country Link
EP (1) EP0152308A3 (de)
GB (1) GB8404112D0 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0294917A1 (de) * 1987-06-11 1988-12-14 Calmac Manufacturing Corporation Unvermischbare Treib- und Kältemittelpaare für Ejektor-Kühlsysteme
CN105423399A (zh) * 2014-11-01 2016-03-23 熵零股份有限公司 一种供热方法及其装置

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR930352A (fr) * 1946-07-08 1948-01-23 Installation frigorifique fonctionnant en circuit fermé
GB619112A (en) * 1942-02-24 1949-03-03 Lothar Meyer An improved refrigerating system
US2637174A (en) * 1950-07-11 1953-05-05 R T Patterson Nonreciprocating refrigeration unit
FR1077020A (fr) * 1953-03-14 1954-11-03 Machine frigorifique sans compresseur, utilisant un éjecteur et fonctionnant avec un fluide frigorigène quelconque
US2931190A (en) * 1957-05-29 1960-04-05 Coleman Co Jet refrigeration system
US3242679A (en) * 1964-04-07 1966-03-29 Edward G Fisher Solar refrigeration unit
FR1580420A (de) * 1968-07-05 1969-09-05
FR2018245A1 (de) * 1968-09-17 1970-05-29 Thielmann Gebruder
DE2629345A1 (de) * 1976-06-30 1978-01-12 Krupp Gmbh Waermepumpe
US4213305A (en) * 1976-09-13 1980-07-22 Genus Arie M De Solar powered cooling apparatus
DE3004070A1 (de) * 1980-02-05 1981-08-13 Peter Ing.(grad.) 4902 Bad Salzuflen Weißhaar Dampfstrahl-zweistoff-waermepumpe
US4301662A (en) * 1980-01-07 1981-11-24 Environ Electronic Laboratories, Inc. Vapor-jet heat pump
US4321801A (en) * 1981-01-26 1982-03-30 Collard Jr Thomas H Jet operated heat pump
DE3035207A1 (de) * 1980-09-18 1982-04-29 Fried. Krupp Gmbh, 4300 Essen Waermepumpe

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB619112A (en) * 1942-02-24 1949-03-03 Lothar Meyer An improved refrigerating system
FR930352A (fr) * 1946-07-08 1948-01-23 Installation frigorifique fonctionnant en circuit fermé
US2637174A (en) * 1950-07-11 1953-05-05 R T Patterson Nonreciprocating refrigeration unit
FR1077020A (fr) * 1953-03-14 1954-11-03 Machine frigorifique sans compresseur, utilisant un éjecteur et fonctionnant avec un fluide frigorigène quelconque
US2931190A (en) * 1957-05-29 1960-04-05 Coleman Co Jet refrigeration system
US3242679A (en) * 1964-04-07 1966-03-29 Edward G Fisher Solar refrigeration unit
FR1580420A (de) * 1968-07-05 1969-09-05
FR2018245A1 (de) * 1968-09-17 1970-05-29 Thielmann Gebruder
DE2629345A1 (de) * 1976-06-30 1978-01-12 Krupp Gmbh Waermepumpe
US4213305A (en) * 1976-09-13 1980-07-22 Genus Arie M De Solar powered cooling apparatus
US4301662A (en) * 1980-01-07 1981-11-24 Environ Electronic Laboratories, Inc. Vapor-jet heat pump
DE3004070A1 (de) * 1980-02-05 1981-08-13 Peter Ing.(grad.) 4902 Bad Salzuflen Weißhaar Dampfstrahl-zweistoff-waermepumpe
DE3035207A1 (de) * 1980-09-18 1982-04-29 Fried. Krupp Gmbh, 4300 Essen Waermepumpe
US4321801A (en) * 1981-01-26 1982-03-30 Collard Jr Thomas H Jet operated heat pump

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0294917A1 (de) * 1987-06-11 1988-12-14 Calmac Manufacturing Corporation Unvermischbare Treib- und Kältemittelpaare für Ejektor-Kühlsysteme
CN105423399A (zh) * 2014-11-01 2016-03-23 熵零股份有限公司 一种供热方法及其装置

Also Published As

Publication number Publication date
EP0152308A3 (de) 1986-02-26
GB8404112D0 (en) 1984-03-21

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Effective date: 19861028