EP0085994A2 - Fonctionnement d'une pompe à chaleur ou d'une machine frigorifique - Google Patents

Fonctionnement d'une pompe à chaleur ou d'une machine frigorifique Download PDF

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Publication number
EP0085994A2
EP0085994A2 EP83101481A EP83101481A EP0085994A2 EP 0085994 A2 EP0085994 A2 EP 0085994A2 EP 83101481 A EP83101481 A EP 83101481A EP 83101481 A EP83101481 A EP 83101481A EP 0085994 A2 EP0085994 A2 EP 0085994A2
Authority
EP
European Patent Office
Prior art keywords
phase
liquid
working medium
heat
compressor
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.)
Granted
Application number
EP83101481A
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German (de)
English (en)
Other versions
EP0085994A3 (en
EP0085994B1 (fr
Inventor
Géza Dipl.-Ing. Hivessy
Péter Dipl.-Ing. Pecz
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.)
Energiagazdalkodasi Intezet
Original Assignee
Energiagazdalkodasi Intezet
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Publication date
Application filed by Energiagazdalkodasi Intezet filed Critical Energiagazdalkodasi Intezet
Publication of EP0085994A2 publication Critical patent/EP0085994A2/fr
Publication of EP0085994A3 publication Critical patent/EP0085994A3/de
Application granted granted Critical
Publication of EP0085994B1 publication Critical patent/EP0085994B1/fr
Expired 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
    • 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
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type

Definitions

  • the invention relates to a method for operating a heat pump or refrigeration machine with a working medium from two different boiling point working materials, which are subjected together as a vapor mixture to a compression process, according to which the working medium is separated into a vapor phase and a liquid phase in a phase separation process Sub-flows are subjected to heat exchange processes, the partial flow withdrawn as a vapor phase from the phase separation process being condensed by heat removal and, after it has been released, subjected to an evaporation process by supplying heat, after which it is recombined with the other partial flow withdrawn from the phase separation process as a liquid phase and relaxed with the latter Compression process is supplied.
  • the invention further relates to a heat pump or refrigerator for carrying out the method.
  • the possible uses of heat pumps and the increase in their effectiveness are being investigated with increased intensity all over the world due to the energy crisis.
  • the heat pump is actually a reversed chiller that transfers the energy from the environment into a functionally closed space.
  • a method of the type mentioned at the outset (DE-B-1 241 468) is designed as a compression method, in which a mixture of two refrigerants with different boiling points is used, the higher-boiling component being liquefied from the compressed refrigerant / vapor mixture by partial condensation the lower-boiling vaporous component is separated and expanded and evaporated to liquefy the lower-boiling component, whereas the liquefied lower-boiling component is expanded and evaporated and mixed with the relaxed higher-boiling component again before evaporation, after which the vaporous higher-boiling component and the vaporous lower-boiling component mixed with it are evaporated Components are compressed again together.
  • the remaining portion of refrigerant is separated from the solution enriched with refrigerant after exiting the absorber and brought into heat exchange with the rich solution in a degasser and thereby partially condensed, so that the refrigerant is expelled from the solution by the evaporation heat released.
  • the expelled refrigerant and the liquid solvent are sucked out of the degasser into a compressor, in which that part of the refrigerant that was used in the degasser to expel the refrigerant fraction absorbed in the solvent is sucked in after complete condensation and subsequent evaporation.
  • the compressor compressing the refrigerant vapor is additionally used to suck the working medium through the degasser and to pump the liquid solvent to the high-pressure side of the absorber, so that an additional solvent pump can be dispensed with. Since an 01 is also used as the solvent, it is also used for lubrication by passing it through the compressor, which is a screw compressor, for example. However, since excess refrigerant is used in this process, the compression work is high.
  • ammonia and water are used as the working medium.
  • the vaporous refrigerant expelled from the liquid solvent in a degassing process by supplying heat is separated from the solvent, the vapor phase consisting of the separated refrigerant is led after its compression into an absorber, while the liquid phase consisting of the separated, low-refrigerant solution is pumped about egg NEN internal heat exchanger, in which the liquid phase in countercurrent to the solution, which is rich in absorbed refrigerant and is drawn off from the degasser, which can also be understood as an evaporator, is heated before being released from it, is also conducted into the absorber and there with the compressed refrigerant vapor is brought back together.
  • the refrigerant vapor condenses in the absorber and is dissolved in the solvent.
  • the invention achieves the object of designing the method of the type mentioned at the outset as a combined compression-absorption method and of creating a refrigeration machine or heat pump for carrying out the method in such a way that an energetically high degree of efficiency can be achieved.
  • this is achieved in the method in that a working medium pair consisting of a solvent and a refrigerant soluble therein is used as the working medium, the vapor mixture of which is compressed in the compression process with the simultaneous presence of its solution and is fed from the compression process to the phase separation process, and that the partial stream withdrawn as a vapor phase from the phase separation process after its condensation is after-cooled by the other partial stream withdrawn as a liquid phase from the phase separation process after its expansion.
  • phase separator which on the steam side is connected to a condenser, which is connected to the input of the compressor via a first expansion valve and an evaporator, and which on the liquid side via a second one Expansion valve is connected to the input of the compressor
  • the phase separator is connected on the liquid side to the input of the compressor via an internal heat exchanger, between the two heat exchange sides of which the second expansion valve and a downstream aftercooler of the condenser are switched on.
  • the vapor phase and the liquid phase of the working medium are present simultaneously and together during the compression, the mixing of the vapor phase and the liquid phase and the dissolving of the vaporous refrigerant in the liquid solvent run in parallel with the pressure increase during the compression. This results in a recooling process during compression and during the dissolving of the refrigerant vapor, the mass fraction of the vapor phase decreases, so that less steam has to be compressed. At the same time, the final temperature of the compression also decreases, so that the compression ratio can be increased.
  • the cooling potential of the liquid phase drawn off from the phase separation process after its relaxation is used to after-cool the condensate precipitated from the vapor phase by means of heat removal before it is relaxed and fed to the evaporation process.
  • the illustrated embodiment is particularly expedient in such cases if, when exchanging heat with the surroundings, the use of a heat exchanger of constant or almost constant temperature is more advantageous than a heat exchanger in which there are continuously changing temperatures along the heat exchange surface, be it at the low-pressure or on the high pressure side or even at both pressures.
  • This latter case which is also shown in the figure, can actually be regarded as a further development of the conventional refrigerator.
  • the two-phase, high-pressure working medium emerging from the compressor 8 passes into a phase separator 16, where the path of the liquid and the vapor are separated from one another.
  • the steam is fed from here into a condenser 9 known per se, where it gives off its heat of vaporization q ko , and then passes via an aftercooler 10 and a pressure-reducing expansion valve 14 into an evaporator 15, in which heat q is obtained from the environment at an almost constant temperature is withdrawn, so that the working medium evaporates in connection therewith.
  • the liquid flows out of the phase separator 16 into a liquid cooler 13, in which it is freed from its heat content which can still be used or which can still be physically extracted in the operation of the refrigerator.
  • the liquid then flows through one side of an internal heat exchanger 12 and a through-reducing expansion valve 11 into the other side of the aftercooler 10, in which the liquid refrigerant cools further. From here, the liquid reaches the suction side of the compressor 8 via the other side of the internal heat exchanger 12, where it mixes with the steam coming from the evaporator 15.
  • this mixture is passed on to the phase separator 16 by the compressor leg, which compresses the vapor phase to the higher pressure level of the condenser 9 through the use of mechanical work q k .
  • a rectifier (not shown) can optionally be installed upstream of the condenser 9, by means of which the refrigerant concentration of the vapor phase is increased.
  • the liquid can even be present in two different forms.
  • the liquid phase can occur in its specifically liquid form.
  • it can also be present in the form of aerosol in the steam.
  • a suitable pump and also an atomizer are of course also required for the latter embodiment.
  • a very great advantage of this "wet" compression is that during the compression the mixing of the vapor phase and the liquid phase of the working medium and the dissolving of the steam take place in parallel with the pressure increase, the vapor phase and the liquid phase being sought, as a function of time and the reaction rates - in accordance with the laws of the thermodynamics of the solutions - to achieve an equilibrium.
  • the temperature values associated with these equilibrium states are always significantly lower than those associated with a given pressure Temperature values in the case of adiabatic compression.
  • the final temperature of the compression also decreases, which is of crucial importance with regard to the structural features of the compressor and the materials that can be used.
  • the pressure ratio of the single-stage compression can be increased significantly, whereby the set goal can be achieved with simpler and cheaper means.
  • the embodiment shown thus combines the advantages that the heat exchangers have a constant temperature profile and the "wet" compression, i.e. offer the thermodynamics of the solutions. It can primarily be used advantageously for such cooling tasks where a large pressure difference is necessary (e.g. freezing, heating with a heat pump); but it can also be used in an energetically effective manner in conventional cooling conditions.
  • Another advantage of the system according to the invention is that it can be adapted very flexibly to the task to be solved, depending on the concentration ratios of the solution used, and its operating parameters can be optimized in this way.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
EP83101481A 1979-06-08 1980-06-09 Fonctionnement d'une pompe à chaleur ou d'une machine frigorifique Expired EP0085994B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
HUPE001086 1979-06-08
HU79PE1086A HU186726B (en) 1979-06-08 1979-06-08 Hybrid heat pump

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP80103173.3 Division 1980-06-09

Publications (3)

Publication Number Publication Date
EP0085994A2 true EP0085994A2 (fr) 1983-08-17
EP0085994A3 EP0085994A3 (en) 1984-10-03
EP0085994B1 EP0085994B1 (fr) 1986-09-24

Family

ID=11000504

Family Applications (2)

Application Number Title Priority Date Filing Date
EP80103173A Expired EP0021205B1 (fr) 1979-06-08 1980-06-09 Procédé de compression-absorption hybride pour pompes à chaleur ou machine frigorifique
EP83101481A Expired EP0085994B1 (fr) 1979-06-08 1980-06-09 Fonctionnement d'une pompe à chaleur ou d'une machine frigorifique

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP80103173A Expired EP0021205B1 (fr) 1979-06-08 1980-06-09 Procédé de compression-absorption hybride pour pompes à chaleur ou machine frigorifique

Country Status (5)

Country Link
US (1) US4481783A (fr)
EP (2) EP0021205B1 (fr)
JP (1) JPS5637471A (fr)
DE (1) DE3066679D1 (fr)
HU (1) HU186726B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2913762A1 (fr) * 2007-03-16 2008-09-19 Usifroid "boucles frigorifiques a troncon commun"

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2497931A1 (fr) * 1981-01-15 1982-07-16 Inst Francais Du Petrole Procede de chauffage et de conditionnement thermique au moyen d'une pompe a chaleur a compression fonctionnant avec un fluide mixte de travail et appareil pour la mise en oeuvre dudit procede
JPS5864470A (ja) * 1981-10-13 1983-04-16 工業技術院長 圧縮式冷凍装置
FR2526136B1 (fr) * 1982-04-28 1986-05-30 Rodie Talbere Henri Procede a cycle de resorption pour les pompes a chaleur
CA1233655A (fr) * 1983-09-29 1988-03-08 Arnold R. Vobach Procede de refrigeration mecanique assiste par voie chimique
US4674297A (en) * 1983-09-29 1987-06-23 Vobach Arnold R Chemically assisted mechanical refrigeration process
HU198328B (en) * 1984-12-03 1989-09-28 Energiagazdalkodasi Intezet Method for multiple-stage operating hibrid (compression-absorption) heat pumps or coolers
HU198329B (en) * 1986-05-23 1989-09-28 Energiagazdalkodasi Intezet Method and apparatus for increasing the power factor of compression hybrid refrigerators or heat pumps operating by solution circuit
US4724679A (en) * 1986-07-02 1988-02-16 Reinhard Radermacher Advanced vapor compression heat pump cycle utilizing non-azeotropic working fluid mixtures
US5600967A (en) * 1995-04-24 1997-02-11 Meckler; Milton Refrigerant enhancer-absorbent concentrator and turbo-charged absorption chiller
US5791157A (en) * 1996-01-16 1998-08-11 Ebara Corporation Heat pump device and desiccant assisted air conditioning system
US6483580B1 (en) 1998-03-06 2002-11-19 Kla-Tencor Technologies Corporation Spectroscopic scatterometer system
KR100385432B1 (ko) * 2000-09-19 2003-05-27 주식회사 케이씨텍 표면 세정용 에어로졸 생성 시스템
TWI263384B (en) 2002-12-19 2006-10-01 Fuji Electric Co Ltd Terminal device for electrical equipment
US7878236B1 (en) 2009-02-09 2011-02-01 Breen Joseph G Conserving energy in an HVAC system
ITUA20161730A1 (it) 2016-03-16 2017-09-16 Stefano Briola Impianto e metodo per la fornitura all’utenza di potenza elettrica e/o potenza meccanica, potenza termica e/o potenza frigorifera
US9453665B1 (en) * 2016-05-13 2016-09-27 Cormac, LLC Heat powered refrigeration system

Citations (10)

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Publication number Priority date Publication date Assignee Title
SU178831A1 (ru) * В. Ф. Чайковский, А. П. Кузнецов , В. Б. Данкрчгс кийп Биагентная холодильная установка
DE84084C (fr) *
US2041725A (en) * 1934-07-14 1936-05-26 Walter J Podbielniak Art of refrigeration
US2581558A (en) * 1947-10-20 1952-01-08 Petrocarbon Ltd Plural stage cooling machine
US2952139A (en) * 1957-08-16 1960-09-13 Patrick B Kennedy Refrigeration system especially for very low temperature
DE1241468B (de) * 1962-12-01 1967-06-01 Andrija Fuderer Dr Ing Kompressionsverfahren zur Kaelterzeugung
DE1426956A1 (de) * 1964-07-17 1969-05-08 Fuderer Michael Verfahren zur Tiefkuehlung
DE2538730A1 (de) * 1974-11-14 1976-06-24 Carrier Corp Kuehlwaerme-rueckgewinnungsanlage
DE2617351A1 (de) * 1975-04-28 1976-11-04 Sten Olof Zeilon Verfahren und apparatur zur kaelteerzeugung
DE2628007A1 (de) * 1976-06-23 1978-01-05 Heinrich Krieger Verfahren und anlage zur erzeugung von kaelte mit wenigstens einem inkorporierten kaskadenkreislauf

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DE1125956B (de) * 1961-05-25 1962-03-22 Giovanni Novaro Verfahren und Vorrichtung zur Kaelteerzeugung mit einer Absorptionskaeltemaschine und einem Verdichter fuer das Kaeltemittel zwischen Verdampfer und Absorber
US3283524A (en) * 1964-03-17 1966-11-08 Byron John Thomson Refrigeration system
US3872682A (en) * 1974-03-18 1975-03-25 Northfield Freezing Systems In Closed system refrigeration or heat exchange
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FR2314456A1 (fr) * 1975-06-09 1977-01-07 Inst Francais Du Petrole Procede de production de froid
JPS5848820B2 (ja) * 1976-04-23 1983-10-31 ステン オロフ ザイロン 冷凍方法及び装置
JPS5434159A (en) * 1977-08-08 1979-03-13 Hitachi Ltd Refrigerating device with screw compressor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU178831A1 (ru) * В. Ф. Чайковский, А. П. Кузнецов , В. Б. Данкрчгс кийп Биагентная холодильная установка
DE84084C (fr) *
US2041725A (en) * 1934-07-14 1936-05-26 Walter J Podbielniak Art of refrigeration
US2581558A (en) * 1947-10-20 1952-01-08 Petrocarbon Ltd Plural stage cooling machine
US2952139A (en) * 1957-08-16 1960-09-13 Patrick B Kennedy Refrigeration system especially for very low temperature
DE1241468B (de) * 1962-12-01 1967-06-01 Andrija Fuderer Dr Ing Kompressionsverfahren zur Kaelterzeugung
DE1426956A1 (de) * 1964-07-17 1969-05-08 Fuderer Michael Verfahren zur Tiefkuehlung
DE2538730A1 (de) * 1974-11-14 1976-06-24 Carrier Corp Kuehlwaerme-rueckgewinnungsanlage
DE2617351A1 (de) * 1975-04-28 1976-11-04 Sten Olof Zeilon Verfahren und apparatur zur kaelteerzeugung
DE2628007A1 (de) * 1976-06-23 1978-01-05 Heinrich Krieger Verfahren und anlage zur erzeugung von kaelte mit wenigstens einem inkorporierten kaskadenkreislauf

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2913762A1 (fr) * 2007-03-16 2008-09-19 Usifroid "boucles frigorifiques a troncon commun"

Also Published As

Publication number Publication date
DE3066679D1 (en) 1984-03-29
JPH0423185B2 (fr) 1992-04-21
EP0021205A2 (fr) 1981-01-07
JPS5637471A (en) 1981-04-11
EP0021205B1 (fr) 1984-02-22
HU186726B (en) 1985-09-30
US4481783A (en) 1984-11-13
EP0085994A3 (en) 1984-10-03
EP0085994B1 (fr) 1986-09-24
EP0021205A3 (en) 1981-03-18

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