EP0085994B1 - Betreiben einer Wärmepumpe oder Kältemaschine - Google Patents

Betreiben einer Wärmepumpe oder Kältemaschine Download PDF

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Publication number
EP0085994B1
EP0085994B1 EP83101481A EP83101481A EP0085994B1 EP 0085994 B1 EP0085994 B1 EP 0085994B1 EP 83101481 A EP83101481 A EP 83101481A EP 83101481 A EP83101481 A EP 83101481A EP 0085994 B1 EP0085994 B1 EP 0085994B1
Authority
EP
European Patent Office
Prior art keywords
phase
heat
liquid
compressor
vapour
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP83101481A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0085994A3 (en
EP0085994A2 (de
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
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 Energiagazdalkodasi Intezet filed Critical Energiagazdalkodasi Intezet
Publication of EP0085994A2 publication Critical patent/EP0085994A2/de
Publication of EP0085994A3 publication Critical patent/EP0085994A3/de
Application granted granted Critical
Publication of EP0085994B1 publication Critical patent/EP0085994B1/de
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-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 by partial condensation from the compressed refrigerant / vapor mixture 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 before evaporation, after which the vaporous higher-boiling component and the vaporous lower-boiling component mixed with it are evaporated be compacted together again.
  • a refrigerant such as a halogenated hydrocarbon, which can be condensed in the operating range of the method and a solvent compatible with it, such as an 01, is used as the working medium, and the method is performed such that only part of the refrigerant, for example half or less is dissolved in the solvent during the absorption process.
  • the remaining refrigerant portion is separated from the refrigerant-enriched solution 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 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 81 is also used as the solvent, this is also passed through the compressor, e.g. a screw compressor is used in addition to its lubrication. However, since an excess of refrigerant is used in this process, the compression work is high.
  • the invention achieves the object of designing the method of the type mentioned at the outset as a compression-absorption method in such a way as to provide 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 is connected on the liquid side to the input of the compressor via a second expansion valve
  • the phase separator is connected to the input of the compressor on the liquid side 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 withdrawn 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 expanded and fed to the evaporation process.
  • the illustrated embodiment is particularly expedient in such cases when, 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 e 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 passes through the other side of the internal heat exchanger 12 to the suction side of the compressor 8, where it mixes with the steam coming from the evaporator 15.
  • This mixture is then passed on through the compressor 8, in which the vapor phase is compressed to the higher pressure level of the condenser 9 by the use of mechanical work q k , into the phase separator 16.
  • 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 damping phase and the liquid phase of the working medium come together and at the same time into the working space of the compressor 8, where, in addition to the compression, those determined by the thermodynamics of the solutions play physical processes.
  • 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 an atomizer are of course also required for the latter embodiment.
  • a very big 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 to achieve an equilibrium in accordance with the laws of thermodynamics of the solutions, but the temperature values associated with these equilibrium states are always significantly lower than the temperature values associated with a given pressure in the case of adiabatic compression.
  • the final temperature of the compression also decreases, which is of crucial importance with regard to the design 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 goal can be achieved with simpler and cheaper means.
  • the embodiment shown thus combines the advantages that the heat exchanger has 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 in this way its operating characteristics can be optimized.

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 Betreiben einer Wärmepumpe oder Kältemaschine Expired EP0085994B1 (de)

Applications Claiming Priority (2)

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

Related Parent Applications (1)

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

Publications (3)

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

Family

ID=11000504

Family Applications (2)

Application Number Title Priority Date Filing Date
EP83101481A Expired EP0085994B1 (de) 1979-06-08 1980-06-09 Betreiben einer Wärmepumpe oder Kältemaschine
EP80103173A Expired EP0021205B1 (de) 1979-06-08 1980-06-09 Hybrides Kompressions-Absorphionsverfahren für das Betreiben von Wärmepumpen oder Kältemaschinen

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP80103173A Expired EP0021205B1 (de) 1979-06-08 1980-06-09 Hybrides Kompressions-Absorphionsverfahren für das Betreiben von Wärmepumpen oder Kältemaschinen

Country Status (5)

Country Link
US (1) US4481783A (enrdf_load_html_response)
EP (2) EP0085994B1 (enrdf_load_html_response)
JP (1) JPS5637471A (enrdf_load_html_response)
DE (1) DE3066679D1 (enrdf_load_html_response)
HU (1) HU186726B (enrdf_load_html_response)

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
US4674297A (en) * 1983-09-29 1987-06-23 Vobach Arnold R Chemically assisted mechanical refrigeration process
CA1233655A (en) * 1983-09-29 1988-03-08 Arnold R. Vobach 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
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
FR2913762A1 (fr) * 2007-03-16 2008-09-19 Usifroid "boucles frigorifiques a troncon commun"
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

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE84084C (enrdf_load_html_response) *
DE142330C (enrdf_load_html_response) *
DE386863C (de) * 1920-06-17 1923-12-17 Siemens Schuckertwerke G M B H Anlage zum Heben von Waerme auf hoehere Temperaturen mittels zweier zusammengeschalteter Kaeltemaschinen
FR537438A (fr) * 1920-11-03 1922-05-23 Procédé et dispositifs de production de frigories à cycle fermé
DE491065C (de) * 1926-06-12 1930-02-05 Frans Georg Liljenroth Kaelteerzeugungsmaschine nach dem Absorptionsprinzip
US2041725A (en) * 1934-07-14 1936-05-26 Walter J Podbielniak Art of refrigeration
US2307380A (en) * 1939-12-26 1943-01-05 Carroll W Baker Refrigeration
FR983950A (fr) * 1943-09-08 1951-06-29 Machine à froid
US2581558A (en) * 1947-10-20 1952-01-08 Petrocarbon Ltd Plural stage cooling machine
DE953378C (de) * 1950-08-29 1956-11-29 Margarete Altenkirch Geb Schae Verfahren und Vorrichtung zum Betrieb einer Waermepumpe
US2952139A (en) * 1957-08-16 1960-09-13 Patrick B Kennedy Refrigeration system especially for very low temperature
US3067590A (en) * 1960-07-06 1962-12-11 Jr Charles P Wood Pumping apparatus for refrigerator systems
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
DE1241468B (de) * 1962-12-01 1967-06-01 Andrija Fuderer Dr Ing Kompressionsverfahren zur Kaelterzeugung
US3283524A (en) * 1964-03-17 1966-11-08 Byron John Thomson Refrigeration system
DE1426956A1 (de) * 1964-07-17 1969-05-08 Fuderer Michael Verfahren zur Tiefkuehlung
US3872682A (en) * 1974-03-18 1975-03-25 Northfield Freezing Systems In Closed system refrigeration or heat exchange
US3952533A (en) * 1974-09-03 1976-04-27 Kysor Industrial Corporation Multiple valve refrigeration system
US3922873A (en) * 1974-11-14 1975-12-02 Carrier Corp High temperature heat recovery in refrigeration
US3990264A (en) * 1974-11-14 1976-11-09 Carrier Corporation Refrigeration heat recovery system
AU501390B2 (en) * 1974-11-14 1979-06-21 Carrier Corporation Refrigeration heat reclaiming system
SE419479B (sv) * 1975-04-28 1981-08-03 Sten Olof Zeilon Kylalstringsforfarande och apparatur for utovning av forfarandet
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
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JPS5434159A (en) * 1977-08-08 1979-03-13 Hitachi Ltd Refrigerating device with screw compressor

Also Published As

Publication number Publication date
EP0021205A3 (en) 1981-03-18
JPH0423185B2 (enrdf_load_html_response) 1992-04-21
EP0021205B1 (de) 1984-02-22
DE3066679D1 (en) 1984-03-29
HU186726B (en) 1985-09-30
EP0085994A3 (en) 1984-10-03
EP0021205A2 (de) 1981-01-07
EP0085994A2 (de) 1983-08-17
JPS5637471A (en) 1981-04-11
US4481783A (en) 1984-11-13

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