EP0184181A2 - Pompe à chaleur - Google Patents

Pompe à chaleur Download PDF

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Publication number
EP0184181A2
EP0184181A2 EP85115297A EP85115297A EP0184181A2 EP 0184181 A2 EP0184181 A2 EP 0184181A2 EP 85115297 A EP85115297 A EP 85115297A EP 85115297 A EP85115297 A EP 85115297A EP 0184181 A2 EP0184181 A2 EP 0184181A2
Authority
EP
European Patent Office
Prior art keywords
heat
pressure
medium
temperature
heat pump
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
EP85115297A
Other languages
German (de)
English (en)
Other versions
EP0184181B1 (fr
EP0184181A3 (en
Inventor
Arpád Dr. Bakay
György Bergmann
Géza Hivessy
Istvan Dr. Szentgyörgyi
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 AT85115297T priority Critical patent/ATE57763T1/de
Publication of EP0184181A2 publication Critical patent/EP0184181A2/fr
Publication of EP0184181A3 publication Critical patent/EP0184181A3/de
Application granted granted Critical
Publication of EP0184181B1 publication Critical patent/EP0184181B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
    • F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • 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

Definitions

  • the invention relates to a heat pump, the working medium of which consists of a mixture of readily soluble media with different boiling points and in which the condensation and evaporation takes place at a changing temperature, with one or more compressors, evaporators, condensers and pressure-reducing elements and piping connecting these units.
  • Fig. 1 which shows these cycles in a TS (temperature entropy) diagram.
  • the heat source is the medium designated by reference number 2, which can be cooled from a temperature T 2 'to a temperature T 2 ".
  • the task of the heat pump is to change the medium labeled 1 from a temperature T 1 ' to a temperature Temperature T 1 "to warm up. These changes in state of the two media are shown by continuous lines.
  • the power factor of the heat pump i.e. the quotient of the useful heat and the mechanical work used, can be expressed as follows will:
  • the power factor can be increased if the necessary mechanical work, ie the area enclosed by the cycle, can be reduced. In the case of a single Carnot process, however, this is not possible because the heat obtainable from the medium 2 is conveyed from the lowest temperature T 2 "of the heat source to the highest temperature T 1 " of the heat-absorbing medium 1 even in the case of an infinitely large heat exchange surface got to. In the case of finite heat exchange surfaces, the temperature of the evaporation is lower than T 2 "and the temperature of the condensation is higher than T 1 ", so that an even higher temperature level must be bridged, that is, an even greater mechanical work is required. In the interest of better understanding these considerations, however, infinitely large heat exchange areas are assumed for the time being with ideal (i.e. isentropic) compression and expansion.
  • the working medium can only absorb a quantity of heat from the medium 2 if its temperature is lower than that of the latter, that is to say the curve path AE runs under the curve of the medium 2.
  • the heat capacity of the two media is the same and the heat exchange surface is infinitely large, the temperature difference z required for heat transfer
  • a circular process with a heat transfer that has a variable temperature sequence is most advantageously implemented by the previously known technical solutions by the so-called hybrid heat pump described in EP-B 0 021 205.
  • the circuit of the hybrid heat pump shown in Fig. 3 is reminiscent of the conventional heat pumps with compressors, differs from them in that a working medium is circulated from two components which can be easily separated from one another in the entire cycle.
  • the media pair does not evaporate completely. but a mixture emerges a vapor rich in the low boiling point medium and a liquid poor in the low boiling point medium, and this mixture enters the compressor 3.
  • the compressor transfers this two-phase working medium from two components in the form of a so-called "wet compression" to a higher pressure level. From here, the steam and the liquid phase reach a condenser (absorber) 4, where the steam rich in the medium with a lower boiling point condenses and gradually dissolves in the flowing liquid phase.
  • the working medium returns to the evaporator (degasser) 6 via an expansion valve 5. With the help of an internal heat exchanger 7, the power factor of the cycle can be improved.
  • FIG. 4 The actual sequence of the above cycle is shown in a T-S diagram by FIG. 4.
  • the letters designating the individual states correspond to the designations of FIG. 3.
  • the internal heat exchanger is not shown and isentropic expansion or compression is assumed.
  • Fig. 5 shows the theoretical cycle of such a hybrid heat pump in a TS diagram in the case of a working medium given concen tration, this cycle from heat absorption with variable temperature (evaporation and degassing at constant pressure p 2 on the route AB), isentropic compression (the route BC), a heat emission with variable temperature (condensation and dissolution at constant pressure P 1 on the route CD) and an isentropic expansion (the route DA).
  • the temperature change of the working medium is ⁇ T 2 in the evaporator (section AB) and ⁇ T 1 in the condenser (section CD). These two values are almost the same. This results from the peculiarity of the working media consisting of two components (from a 1 solution) that in the TS diagram of a given concentration the curves for constant pressures are approximately parallel.
  • the hybrid heat pump can only work with a really favorable performance factor if the temperature change of the heat-emitting and heat-absorbing medium is almost the same, and the temperature change of the working medium in the evaporator and in the condenser is adapted to these temperature changes.
  • the heat source is waste heat with a low temperature level, e.g. a waste water of 30 ° C or a heated cooling water that can be cooled to a maximum of + 5 ° C without risk of freezing, i.e. the temperature change is 25 ° C.
  • the task consists in the production of domestic hot water with a temperature of 85 ° C from the available tap water of 15 ° C for the purposes of the food industry.
  • the change in temperature is 70 ° C, i.e. a multiple of the other value.
  • In 1 lg. 6 is the temperature flow of the media 1 or? denoted by continuous lines.
  • the figure shows ideal circular processes (isentropic compression and expansion. Infinitely large heat exchange areas). They are the Carnot press with a dashed line and the theory Retic circular process of the hybrid heat pump shown with a dash-dotted line, the latter being adapted to the medium 2. It can be clearly seen from the figure that the area enclosed by the cyclic process of variable temperature and thus the necessary mechanical work are considerably less than in the Carnot process, but much larger than the theoretically necessary minimum work. This deficiency cannot be remedied either by adapting the cycle to the medium 1 or by using an intermediate variant.
  • the object of the invention is such a further development of the hybrid heat pump, which makes it possible, independently of one another, to adapt the temperature flow of the evaporator and the condenser between very wide limits to the temperature flow of the heat-emitting or heat-absorbing medium, so that the theoretically largest possible power factor is approximated to the maximum can be.
  • the compressor is designed as a fin having more than one suction and / or pressure nozzle.
  • the spigot form several pressure levels for simultaneous suction at more than one suction pressure level and / or for delivery to more than one pressure level, the number of pressure levels of the ver steamer is equal to the number of suction pressure levels and the number of pressure stages of the condensers is equal to the number of pressure-side pressure levels.
  • pressure-reducing elements e.g. Expansion valves are installed in such a way that a pressure-reducing element is arranged between two adjacent pressure stages in accordance with the pressure levels of the compressor which are arranged successively according to the flea of the pressure levels.
  • an expansion turbine the plurality of inlet and / or outlet connections of which are designed in such a way that the turbine, in accordance with the number of pressure stages of the compressor, for receiving or discharging the working medium at several pressure levels simultaneously is capable.
  • the heat pump works with a working medium consisting of two components, which evaporates and condenses at variable temperature, at least the condenser and / or the evaporator working at more than one pressure level p 3 , p 4 , p 5 , as a result of which the temperature change of the working medium can be influenced as required.
  • a working medium consisting of two components, which evaporates and condenses at variable temperature, at least the condenser and / or the evaporator working at more than one pressure level p 3 , p 4 , p 5 , as a result of which the temperature change of the working medium can be influenced as required.
  • An example of this is shown in FIG. 8.
  • the working medium emerges from the compressor 3 at three different pressure levels and a separate condenser is assigned to each outlet pressure level, so that the heat-absorbing medium 1 is heated in the three condensers 4a, 4b, 4c at three different pressures.
  • the working medium from the condensers enters an expansion turbine 8 at three correspondingly different pressure levels and is fed therefrom at two different pressure levels to the two evaporators 6a and 6b, which are heated by the heat-emitting medium 2 and from which the working medium at two accordingly different inlet pressure levels is passed back into the compressor 3.
  • FIGS. 8 and 9 shows this cyclic process in a TS diagram in the case of isentroplic compression and expansion.
  • the temperature changes of the Media and 2 - for infinitely large heat exchange surfaces - are shown separately on the right side of the figure.
  • the condenser and the evaporator in FIGS. 8 and 9 only have three or two pressure stages, for example, since the number of pressure stages can be determined as required.
  • the actual switching of the heat pump according to the invention is more complicated, namely it preferably also contains internal heat exchangers 7 e.g. 10.
  • the expansion turbine 8 is only economical in very large systems, so that pressure-reducing elements (e.g. throttle valves) are generally used instead of these turbines.
  • pressure-reducing elements e.g. throttle valves
  • FIG. 10 Hi'er, like in the previous example, the condenser unit has three pressure stages, while the evaporator unit has two pressure stages. If necessary, a different number of pressure levels can also be selected.
  • the working medium passes from the compressor 3 with three different pressure levels p 3 , p 4 , p 5 into the three condensers 4a, 4b, 4c, where the heat-absorbing medium 1 is heated by the working medium.
  • Internal heat exchangers 7a, 7b, 7c are connected downstream of the condensers, where the working medium cools down further at high pressure and transfers heat to the working medium at low pressure.
  • the outputs of the inner heat exchangers 7a, 7b, 7c are brought together by interposing one of two expansion valves 5c, 5d, which are followed by two further expansion valves 5a, 5b.
  • the pressure of the working medium is gradually reduced in the four expansion valves 5a, 5b, 5c, 5d to the required level, after which the working medium with two different pressure levels enters each of two evaporators 6a, 6b.
  • the evaporators 6a, 6b are heated by the heat-emitting medium 2.
  • the here heated and partially evaporated working medium heats up in the internal heat exchangers 7a, 7b. 7c further, two of which are connected in series to the one evaporator 6a and one to the other evaporator 6b, then it enters the compressor 3 again at corresponding pressure levels p 1 and p 2 .
  • FIG. 11a If the construction of the compressor 3 is not suitable for having suction or pressure ports at different pressure levels, several compressors can also be provided according to FIG. 11a.
  • five compressors 3a, 3b, 3c, 3d, 3e are expediently installed on a common axis, the common axis not being an indispensable condition.
  • the working medium enters the two first compressors 3a and 3b with two different pressures and exits the three last compressors 3c, 3d and 3e with three different pressures.
  • the suction pressure p 2 is slightly higher than the pressure p 3 .
  • the circuit of the internal heat exchangers 7a, 7b, 7c in Fig. 10 is such that the working medium emerging from the evaporator with a pressure p 2 from a liquid with a pressure p 5 , and the medium with a pressure p 1 from the liquids with the pressures p 3 and p 4 is heated.
  • the circuit shown in the figure is optimal for certain values of the media flows and the pressures. However, there may also be cases in which a circuit deviating from the figure is associated with a greater thermodynamic advantage, for example if the mass flows and the pressure levels are distributed differently among the individual condensers and evaporators, as a result of which the temperature sequences are also different.
  • the medium with the pressure p 4 is branched onto the internal heat exchangers 7b and 7c which emit heat from it, these are therefore connected in parallel, but such a case is also possible, for which it is more favorable is to connect the internal heat exchangers 7b and 7c in series along the flow path of the medium with the pressure p 3 .
  • FIG. 12 A special case of realizing the inventive concept is shown in Fig. 12, wherein only the condenser operates at three pressure stages 4a, 4b, 4c and only one evaporator 6 has occurred, i.e. the compressor only draws in at a single pressure level and supplies working media with three different pressure levels. This is necessary if the temperature change of the heat-absorbing medium is significantly greater than that of the heat-emitting medium.
  • FIG. 12 An opposite case can be seen from FIG. 12, according to which only one condenser stage 4 and three evaporator stages 6a, 6b, 6c are provided.
  • 10 shows the general solution to the problem according to the invention, according to which the number of stages of the condensers and evaporators differs from one another. In a special case, this number of steps can also be the same, e.g. two suction-side pressure stages on the compressor 3 Calso two evaporator stages) and two pressure-side pressure stages (i.e. two condenser stages).
  • the solution of the invention can be two to the series circuit of independent cycles of the hybrid Heat pump can be returned.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Central Heating Systems (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Control Of The Air-Fuel Ratio Of Carburetors (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP85115297A 1984-12-03 1985-12-03 Pompe à chaleur Expired - Lifetime EP0184181B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85115297T ATE57763T1 (de) 1984-12-03 1985-12-03 Waermepumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
HU844461A HU198328B (en) 1984-12-03 1984-12-03 Method for multiple-stage operating hibrid (compression-absorption) heat pumps or coolers
HU446184 1984-12-03

Publications (3)

Publication Number Publication Date
EP0184181A2 true EP0184181A2 (fr) 1986-06-11
EP0184181A3 EP0184181A3 (en) 1988-01-13
EP0184181B1 EP0184181B1 (fr) 1990-10-24

Family

ID=10968033

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85115297A Expired - Lifetime EP0184181B1 (fr) 1984-12-03 1985-12-03 Pompe à chaleur

Country Status (9)

Country Link
US (1) US4688397A (fr)
EP (1) EP0184181B1 (fr)
JP (1) JPS61180861A (fr)
AT (1) ATE57763T1 (fr)
CA (1) CA1262057A (fr)
DE (1) DE3580249D1 (fr)
DK (1) DK161482C (fr)
HU (1) HU198328B (fr)
NO (1) NO164738C (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014213542A1 (de) * 2014-07-11 2016-01-14 Siemens Aktiengesellschaft Verfahren zum Betrieb einer Wärmepumpe mit wenigstens zwei Verdampfern
DE102014213543A1 (de) * 2014-07-11 2016-01-14 Siemens Aktiengesellschaft Verfahren zum Betrieb einer Wärmepumpe mit wenigstens zwei Verflüssigern

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
HU210994B (en) * 1990-02-27 1995-09-28 Energiagazdalkodasi Intezet Heat-exchanging device particularly for hybrid heat pump operated by working medium of non-azeotropic mixtures
US11078896B2 (en) * 2018-02-28 2021-08-03 Treau, Inc. Roll diaphragm compressor and low-pressure vapor compression cycles

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH97319A (de) * 1921-05-20 1923-01-02 Escher Wyss Maschf Ag Kälteanlage mit Kreiselverdichter und mindestens zwei Verdampfern, die mit verschiedenen Drücken arbeiten.
DE712629C (de) * 1937-09-14 1941-10-22 Karl Glaessel Mehrfach wirkender Kompressor fuer Kaelteanlagen
DE830801C (de) * 1950-07-25 1952-02-07 E H Edmund Altenkirch Dr Ing Kompressions-Kaelteanlage
DE867122C (de) * 1950-08-29 1953-02-16 Edmund Dr-Ing E H Altenkirch Verfahren und Vorrichtung zum Heben der einem Waermetraeger entzogenen Waermemenge niedrigerer Temperatur auf eine hoehere Temperatur
DE1035669B (de) * 1954-08-09 1958-08-07 Frantisek Wergner Verfahren zum Betrieb einer Kompressor-Kuehlanlage mit mindestens zweistufiger Kompression eines in der Anlage umlaufenden Kaeltemittels sowie Kompressor-Kuehlanlage zur Durchfuehrung des Verfahrens
US2952139A (en) * 1957-08-16 1960-09-13 Patrick B Kennedy Refrigeration system especially for very low temperature
US3092976A (en) * 1960-08-03 1963-06-11 Conch Int Methane Ltd Refrigeration of one fluid by heat exchange with another
FR1568871A (fr) * 1968-01-18 1969-05-30
DE1900814A1 (de) * 1968-01-10 1969-07-31 Babcock Atlantique Sa Kuehlverfahren und Einrichtung zur Durchfuehrung des Verfahrens
US3577742A (en) * 1969-06-13 1971-05-04 Vilter Manufacturing Corp Refrigeration system having a screw compressor with an auxiliary high pressure suction inlet
EP0021205A2 (fr) * 1979-06-08 1981-01-07 Energiagazdalkodasi Intezet Procédé de compression-absorption hybride pour pompes à chaleur ou machine frigorifique
EP0179225A1 (fr) * 1984-09-19 1986-04-30 Kabushiki Kaisha Toshiba Système de pompe de chaleur

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1241468B (de) * 1962-12-01 1967-06-01 Andrija Fuderer Dr Ing Kompressionsverfahren zur Kaelterzeugung
FR2337855A1 (fr) * 1976-01-07 1977-08-05 Inst Francais Du Petrole Procede de production de chaleur utilisant une pompe de chaleur fonctionnant avec un melange de fluides
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
JPS6176855A (ja) * 1984-09-19 1986-04-19 株式会社東芝 カスケ−ド結合ヒ−トポンプ装置

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH97319A (de) * 1921-05-20 1923-01-02 Escher Wyss Maschf Ag Kälteanlage mit Kreiselverdichter und mindestens zwei Verdampfern, die mit verschiedenen Drücken arbeiten.
DE712629C (de) * 1937-09-14 1941-10-22 Karl Glaessel Mehrfach wirkender Kompressor fuer Kaelteanlagen
DE830801C (de) * 1950-07-25 1952-02-07 E H Edmund Altenkirch Dr Ing Kompressions-Kaelteanlage
DE867122C (de) * 1950-08-29 1953-02-16 Edmund Dr-Ing E H Altenkirch Verfahren und Vorrichtung zum Heben der einem Waermetraeger entzogenen Waermemenge niedrigerer Temperatur auf eine hoehere Temperatur
DE1035669B (de) * 1954-08-09 1958-08-07 Frantisek Wergner Verfahren zum Betrieb einer Kompressor-Kuehlanlage mit mindestens zweistufiger Kompression eines in der Anlage umlaufenden Kaeltemittels sowie Kompressor-Kuehlanlage zur Durchfuehrung des Verfahrens
US2952139A (en) * 1957-08-16 1960-09-13 Patrick B Kennedy Refrigeration system especially for very low temperature
US3092976A (en) * 1960-08-03 1963-06-11 Conch Int Methane Ltd Refrigeration of one fluid by heat exchange with another
DE1900814A1 (de) * 1968-01-10 1969-07-31 Babcock Atlantique Sa Kuehlverfahren und Einrichtung zur Durchfuehrung des Verfahrens
FR1568871A (fr) * 1968-01-18 1969-05-30
US3577742A (en) * 1969-06-13 1971-05-04 Vilter Manufacturing Corp Refrigeration system having a screw compressor with an auxiliary high pressure suction inlet
EP0021205A2 (fr) * 1979-06-08 1981-01-07 Energiagazdalkodasi Intezet Procédé de compression-absorption hybride pour pompes à chaleur ou machine frigorifique
EP0179225A1 (fr) * 1984-09-19 1986-04-30 Kabushiki Kaisha Toshiba Système de pompe de chaleur

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014213542A1 (de) * 2014-07-11 2016-01-14 Siemens Aktiengesellschaft Verfahren zum Betrieb einer Wärmepumpe mit wenigstens zwei Verdampfern
DE102014213543A1 (de) * 2014-07-11 2016-01-14 Siemens Aktiengesellschaft Verfahren zum Betrieb einer Wärmepumpe mit wenigstens zwei Verflüssigern

Also Published As

Publication number Publication date
DK553885A (da) 1986-06-04
DK161482B (da) 1991-07-08
HUT41526A (en) 1987-04-28
DK161482C (da) 1991-12-16
NO164738C (no) 1990-11-14
US4688397A (en) 1987-08-25
NO164738B (no) 1990-07-30
DK553885D0 (da) 1985-11-29
DE3580249D1 (de) 1990-11-29
CA1262057A (fr) 1989-10-03
ATE57763T1 (de) 1990-11-15
JPS61180861A (ja) 1986-08-13
NO854845L (no) 1986-06-04
EP0184181B1 (fr) 1990-10-24
HU198328B (en) 1989-09-28
EP0184181A3 (en) 1988-01-13

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