EP0021205A2 - Procédé de compression-absorption hybride pour pompes à chaleur ou machine frigorifique - Google Patents

Procédé de compression-absorption hybride pour pompes à chaleur ou machine frigorifique Download PDF

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Publication number
EP0021205A2
EP0021205A2 EP80103173A EP80103173A EP0021205A2 EP 0021205 A2 EP0021205 A2 EP 0021205A2 EP 80103173 A EP80103173 A EP 80103173A EP 80103173 A EP80103173 A EP 80103173A EP 0021205 A2 EP0021205 A2 EP 0021205A2
Authority
EP
European Patent Office
Prior art keywords
heat
working medium
compressor
circuit
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.)
Granted
Application number
EP80103173A
Other languages
German (de)
English (en)
Other versions
EP0021205B1 (fr
EP0021205A3 (en
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
Priority to AT80103173T priority Critical patent/ATE6387T1/de
Priority to AT83101481T priority patent/ATE22490T1/de
Priority to DE8383101481T priority patent/DE3071785D1/de
Publication of EP0021205A2 publication Critical patent/EP0021205A2/fr
Publication of EP0021205A3 publication Critical patent/EP0021205A3/de
Application granted granted Critical
Publication of EP0021205B1 publication Critical patent/EP0021205B1/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 hybrid refrigeration machine or heat pump, which is provided with a mechanical compressor and which in its thermodynamic system contains a working fluid pair, known or similar in the case of absorption refrigerators, of a refrigerant and a solvent for the refrigerant, so that a solution or sorption cycle is interconnected with a compressor.
  • 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 medium with variable temperature a cooling medium
  • the extracted energy should also be transferred to a medium with variable temperature (e.g. cooling water).
  • a medium with variable temperature e.g. cooling water
  • the conventional compression refrigeration machines have the major disadvantage that the evaporation and condensation temperatures of the refrigeration machine on the side of the heat exhaust are below the lowest temperature of the medium to be cooled, and on the side of the heat output the highest temperature of the heat-absorbing medium must, and that - which is closely related - the pressures of the heat exchanger vessels must be determined with an unnecessarily large deviation. So the value of the pressure ratio, which basically determines the operation of the compressor, becomes rather unfavorable. The same problem also occurs with heat pumps.
  • the essence of the invention and at the same time the object to be achieved is the creation of a hybrid system which combines the advantageous properties of the sorption chillers and the chillers provided with mechanical compressors (compression chillers), without the disadvantages of the starting types.
  • the heat exchanger vessels which enable a variable temperature sequence due to the sorption principle, are combined with the compressor of the compression refrigeration machines, and as a working medium not a pure refrigerant, but a pair of agents that is already known or similar in the absorption (or absorption) refrigeration machines circulated from a refrigerant and a sorption liquid in the thermodynamic circuit of the system according to the invention.
  • At least one of the heat exchanger vessels enabling heat exchange with the surroundings is a so-called “dry" construction, suitably consisting of pipes or plates which are guaranteed along the heat exchange surface with respect to both phases of the working medium between the initial and final state of continuously changing concentration ratios or clearly assigned continuously changing temperature conditions.
  • the system according to the invention has the vapor and liquid phase of the working medium in the working space of its compressor simultaneously and together.
  • a phase separator is installed behind the degasser of the system.
  • a rectifier is installed behind the phase separator in the vapor phase line of the working medium.
  • a phase separator is installed downstream of the compressor, and a condenser with an aftercooler on the vapor phase side, and an internal heat exchanger on the liquid phase side, the two separate working medium circuits thus created having at least one common section.
  • the cold is in the steam line behind the phase separator and in front of the condenser Rectifier increasing the medium concentration of the vapor phase is installed.
  • a drive circuit consisting of a boiler, an expansion machine, an absorber, an internal heat exchanger and a solution pump is connected to the base system, the expansion machine and the compressor of the base system being connected to one another by means of a power transmission element.
  • the heat pump according to the invention has, at the same pressure conditions, roughly the same, but at the same temperature conditions a 1.5 to 2 times higher performance coefficient e than the conventional systems.
  • This value can be increased further with goal-oriented research and by using working media with a higher specific solution heat.
  • the system in the thermodynamic system of which a solution is circulated as the working medium, has an absorber 1 and a degasser 4 as heat exchanger vessels.
  • An internal heat exchanger 2 temperature changer
  • a pressure-reducing expansion valve 3 expediently a throttle valve
  • Behind the degasser 4 is a phase separator 5, in which the two-phase working solution is separated.
  • the path of the liquid leads back into the absorber 1 with the aid of a liquid pump 6 via the internal heat exchanger 2, where it preferably flows in countercurrent to the solution emerging from the absorber 1.
  • the path of the vapor phase leads via a rectifier 7 to a mechanical compressor 8, the output of which is also connected to the absorber 1.
  • the solution emerging from the absorber 1 flows through one side of the inner heat exchanger 2 and through the expansion valve 3. After flowing through the pressure-reducing expansion valve 3, a solution of low pressure enters the degasser 4, which draws heat from the medium to be cooled. Due to the amount of heat q extracted from the medium to be cooled, a significant proportion of the refrigerant components of the solution are converted into the vapor phase, which means that this amount of heat drives the refrigerant out of the solution and provides the necessary heat of solution and evaporation.
  • the two-phase mixture emerging from the degasifier 4 enters the phase separator 5, where the liquid and the vapor phase are separated from one another. From here, the liquid flows back with the help of the liquid pump 6 over the other side of the internal heat exchanger 2 into the absorber 1, where it comes into contact with the vapor phase again.
  • the vapor phase passes through the rectifier 7, which can be included in the degasser 4 according to FIG. 1, into the compressor 8, which compresses the vapor phase to the higher pressure level of the absorber 1 through the use of mechanical work q k .
  • the absorber 1 In the absorber 1, the vapor phase and the sorption liquid containing little refrigerant, the so-called poor solution, are mixed, the refrigerant is dissolved in the sorption liquid and the heat of evaporation and the heat of solution are extracted, i.e. the amount of heat q, with changing temperature parameters.
  • the heat exchange surface of the absorber can also be uniquely assigned a temperature field that changes along the same; the heat given off can therefore really be used with changing temperature parameters.
  • the use of the internal heat exchanger 2 improves the thermal efficiency of the system.
  • Fig. 2 shows another advantageous embodiment of the combined heat pump according to the invention.
  • This embodiment differs from that of Fig. 1 essentially in that the phases of the two-phase working medium emerging from the degasser 4 are not separated, but - after passing through the internal heat exchanger 2 - come together and simultaneously into the working space of the compressor 8, where in addition to compression, the physical processes determined by the thermodynamics of the solutions also take place.
  • 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.
  • the high pressure liquid-vapor mixture flows into the absorber 1, where the heat of vaporization of the vapor and the heat of solution of the refrigerant, i.e. the amount of heat q is withdrawn when the temperature changes or is used for heating purposes.
  • the liquid passes under high pressure into the pressure-reducing expansion valve 3 (e.g. into a throttle valve), in which the working medium expands.
  • the pressure-reducing expansion valve 3 e.g. into a throttle valve
  • a very great advantage of this embodiment is the so-called "wet compression".
  • the mixing of the vapor and the liquid phase and the dissolving of the vapor take place in parallel with the pressure increase, whereby the vapor phase and the liquid phase are endeavored to function as a function of time and the reaction rates - in accordance with the laws of the thermodynamics of the solutions To achieve balance.
  • the temperature values belonging to these equilibrium states are always significantly lower than the temperature values belonging to 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 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.
  • FIG. 3 Another possible embodiment of the heat pump according to the invention is shown in FIG. 3.
  • This embodiment is particularly expedient in such cases when the use of a heat exchanger vessel of constant or almost constant temperature is more advantageous when exchanging heat with the surroundings, be it on the low-pressure side or on the high-pressure side, or even at both pressures.
  • This latter case which is also shown in the figure, can actually be seen as a further development of the conventional chiller.
  • the machine presented here thus combines the advantages that the heat exchanger vessels have a constant temperature profile and the "wet compression", i.e. offer the thermodynamics of the solutions.
  • 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 emits 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 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 physically usable or still usable or in the operation of the refrigerator extractable heat content is exempted.
  • the liquid then flows through one side of an internal heat exchanger 12 and a pressure-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.
  • 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 embodiment according to FIG. 3 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.
  • the embodiment according to FIG. 4 has the advantage that it combines the good properties of the previously discussed embodiments and the absorption machines, since this embodiment works without external mechanical energy expenditure by introducing thermal energy.
  • the liquid working medium flows out of the absorber 1 in the already known manner via one side of the inner heat exchanger 2 and the pressure-reducing expansion valve 3 into the degasser 4, in which the working medium extracts thermal energy q, as a result of which part of the working medium evaporates .
  • the working medium is pressed by the compressor 8 into the absorber 19 of the drive circuit.
  • the working medium is dissolved in a poor solution coming from a boiler 18, during which the working medium releases its heat of evaporation and solution q02.
  • the rich solution flows out of the absorber 19 with the help of a solution pump 6 via one side of the inner heat exchanger 2 of the drive circuit into the boiler 18, in which the rich refrigerant vapor is expelled again from this rich solution with the help of an external amount of energy q ka high temperature levels becomes.
  • the poor solution flows back over the other side of the inner heat exchanger 2 and the pressure-reducing expansion valve 3 into the drive-side absorber 19.
  • the steam leaving the boiler 18 flows into a mechanical expansion machine 17, in which part of the enthalpy of the steam is converted into mechanical energy.
  • the compressor 8 is driven by this mechanical energy.
  • the working medium emerging from the compressor 8 could also be conducted into the absorber 1, the steam emerging from the expansion machine 17 having to be conducted into the drive-side absorber 19. This could thermodynamically separate the working side and the drive side.
  • This way of switching is less interesting because it means no further advantages in terms of function; it even results in a certain deterioration of the specific characteristic values, because in the former case higher temperatures can be achieved by appropriately selecting the concentration ratios on the drive side in the absorber 19, as a result of which a larger proportion of the energy expended can be obtained at a higher temperature level.
  • the heat pump according to the invention has a very wide field of application because, from the deep-freezing tasks up to the heating purposes, it guarantees more energy-efficient operation than the previous systems.
  • 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 characteristic can be optimized.
EP80103173A 1979-06-08 1980-06-09 Procédé de compression-absorption hybride pour pompes à chaleur ou machine frigorifique Expired EP0021205B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AT80103173T ATE6387T1 (de) 1979-06-08 1980-06-09 Hybrides kompressions-absorphionsverfahren fuer das betreiben von waermepumpen oder kaeltemaschinen.
AT83101481T ATE22490T1 (de) 1979-06-08 1980-06-09 Betreiben einer waermepumpe oder kaeltemaschine.
DE8383101481T DE3071785D1 (en) 1979-06-08 1980-06-09 Operation of a heat pump or refrigeration machine

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 Child Applications (1)

Application Number Title Priority Date Filing Date
EP83101481.6 Division-Into 1980-06-09

Publications (3)

Publication Number Publication Date
EP0021205A2 true EP0021205A2 (fr) 1981-01-07
EP0021205A3 EP0021205A3 (en) 1981-03-18
EP0021205B1 EP0021205B1 (fr) 1984-02-22

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 After (1)

Application Number Title Priority Date Filing Date
EP83101481A Expired EP0085994B1 (fr) 1979-06-08 1980-06-09 Fonctionnement d'une pompe à chaleur ou d'une 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 (7)

* 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
EP0093051A2 (fr) * 1982-04-28 1983-11-02 Henri Rodié-Talbère Procédé à cycle de resorption pour les pompes à chaleur
EP0138041A2 (fr) * 1983-09-29 1985-04-24 VOBACH, Arnold R. Méthode de réfrigération mécanique aidée chimiquement
EP0184181A2 (fr) * 1984-12-03 1986-06-11 Energiagazdalkodasi Intezet Pompe à chaleur
US4674297A (en) * 1983-09-29 1987-06-23 Vobach Arnold R Chemically assisted mechanical refrigeration process
EP0248296A2 (fr) * 1986-05-23 1987-12-09 Energiagazdálkodási Részvénytársaság Procédé pour augmenter le coefficient de performance de machines frigorifiques ou de pompes à chaleur hybrides
EP0276251A1 (fr) * 1986-07-02 1988-08-03 RADERMACHER, Reinhard Cycle avance de pompes thermiques a compression de vapeur utilisant un melange de fluides non-azeotropes de travail

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JPS5864470A (ja) * 1981-10-13 1983-04-16 工業技術院長 圧縮式冷凍装置
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
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

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FR537438A (fr) * 1920-11-03 1922-05-23 Procédé et dispositifs de production de frigories à cycle fermé
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
DE491065C (de) * 1926-06-12 1930-02-05 Frans Georg Liljenroth Kaelteerzeugungsmaschine nach dem Absorptionsprinzip
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
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
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
DE2624714A1 (de) * 1975-06-09 1976-12-23 Inst Francais Du Petrol Verfahren und vorrichtung zur erzeugung von kaelte

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DE142330C (fr) *
DE84084C (fr) *
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
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
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
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
DE2624714A1 (de) * 1975-06-09 1976-12-23 Inst Francais Du Petrol Verfahren und vorrichtung zur erzeugung von kaelte

Cited By (15)

* 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
EP0057120A2 (fr) * 1981-01-15 1982-08-04 Institut Français du Pétrole Procédé de chauffage d'un local au moyen d'une pompe à chaleur à compression fonctionnant avec un fluide mixte de travail
EP0057120A3 (en) * 1981-01-15 1983-05-04 Institut Francais Du Petrole Method of heating and thermal conditioning by means of a compression heat pump using a mixed working medium and a device for carrying out the method
EP0093051A2 (fr) * 1982-04-28 1983-11-02 Henri Rodié-Talbère Procédé à cycle de resorption pour les pompes à chaleur
FR2526136A1 (fr) * 1982-04-28 1983-11-04 Rodie Talbere Henri Procede a cycle de resorption pour les pompes a chaleur
EP0093051A3 (en) * 1982-04-28 1984-09-19 Henri Rodie-Talbere Resorption method for heat pumps
EP0138041A2 (fr) * 1983-09-29 1985-04-24 VOBACH, Arnold R. Méthode de réfrigération mécanique aidée chimiquement
EP0138041A3 (en) * 1983-09-29 1986-03-26 Arnold R. Vobach Chemically assisted mechanical refrigeration process
US4674297A (en) * 1983-09-29 1987-06-23 Vobach Arnold R Chemically assisted mechanical refrigeration process
EP0184181A2 (fr) * 1984-12-03 1986-06-11 Energiagazdalkodasi Intezet Pompe à chaleur
EP0184181A3 (en) * 1984-12-03 1988-01-13 Energiagazdalkodasi Intezet Heat pump
EP0248296A2 (fr) * 1986-05-23 1987-12-09 Energiagazdálkodási Részvénytársaság Procédé pour augmenter le coefficient de performance de machines frigorifiques ou de pompes à chaleur hybrides
EP0248296A3 (en) * 1986-05-23 1988-05-25 Energiagazdalkodasi Intezet Method and device for increasing the coefficient of performance of hybrid refrigeration machines or heat pumps
EP0276251A1 (fr) * 1986-07-02 1988-08-03 RADERMACHER, Reinhard Cycle avance de pompes thermiques a compression de vapeur utilisant un melange de fluides non-azeotropes de travail
EP0276251A4 (fr) * 1986-07-02 1988-11-22 Reinhard Radermacher Cycle avance de pompes thermiques a compression de vapeur utilisant un melange de fluides non-azeotropes de travail.

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EP0085994B1 (fr) 1986-09-24
EP0085994A2 (fr) 1983-08-17
EP0021205B1 (fr) 1984-02-22
JPH0423185B2 (fr) 1992-04-21
DE3066679D1 (en) 1984-03-29
US4481783A (en) 1984-11-13
HU186726B (en) 1985-09-30
JPS5637471A (en) 1981-04-11
EP0021205A3 (en) 1981-03-18
EP0085994A3 (en) 1984-10-03

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