EP2244040B1 - Vidange de vapeur instantanée du réservoir d'un circuit refrigérant - Google Patents

Vidange de vapeur instantanée du réservoir d'un circuit refrigérant Download PDF

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Publication number
EP2244040B1
EP2244040B1 EP10167202.0A EP10167202A EP2244040B1 EP 2244040 B1 EP2244040 B1 EP 2244040B1 EP 10167202 A EP10167202 A EP 10167202A EP 2244040 B1 EP2244040 B1 EP 2244040B1
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EP
European Patent Office
Prior art keywords
line
refrigerant
compressor unit
receiver
pressure
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.)
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Application number
EP10167202.0A
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German (de)
English (en)
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EP2244040A3 (fr
EP2244040A2 (fr
Inventor
Heinbokel Bernd
Gernemann Andreas
Schierhorn Uwe
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Carrier Corp
Original Assignee
Carrier Corp
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Publication date
Priority claimed from DE102004038640A external-priority patent/DE102004038640A1/de
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP2244040A2 publication Critical patent/EP2244040A2/fr
Publication of EP2244040A3 publication Critical patent/EP2244040A3/fr
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Publication of EP2244040B1 publication Critical patent/EP2244040B1/fr
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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
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—Superheaters
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/22—Refrigeration systems for supermarkets
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel

Definitions

  • the invention relates to a refrigeration cycle in which a one- or multi-component refrigerant circulates, comprising in the flow direction a condenser, a collecting container, an expansion device upstream of an evaporator, an evaporator and a single-stage compressing compressor unit.
  • the invention relates to a method for operating a refrigeration cycle.
  • liquefier should be understood to mean both liquefier and gas cooler.
  • Composite refrigerators generally supply a large number of refrigeration consumers, such as refrigerators, refrigerators and freezers. For this purpose circulates in them a one- or multi-component refrigerant or refrigerant mixture.
  • a method for operating a compression refrigeration system with the working fluid carbon dioxide with a two-stage throttling and division of the circulating working fluid flow is known.
  • the working medium mass flow is passed after the first throttle stage in a subcritical working medium pressure separator, which in the lower part of the medium pressure separator collecting, larger liquid Hästoffmassestromanteil the evaporator, the separating in the upper part of the medium pressure separating, smaller vapor Häffenmassestromanteil is about a second throttle level to close relaxes the evaporation pressure.
  • the smaller vapor mass of the working medium mass used by evaporation and overheating serves to subcool the supercritical high-pressure gas. After evaporation and overheating, the smaller working medium mass fraction is mixed in a collecting tube integrated in the evaporator with the outlet of the evaporator strands.
  • a subcritical working refrigeration cycle known in the embodiment of the Fig. 1 is a compressor, a condenser, a high pressure float valve, a tank and evaporator with upstream expansion valves is present, in which a line connects the upper part of the liquid tank with the input of the compressor, and wherein in this line successively an electronically operated valve and an additional manual Adjustment organ are present.
  • a counting of the prior art refrigeration cycle or a refrigeration system in which such a refrigeration cycle is realized, is based on the in the FIG. 1 illustrated embodiment explained in more detail.
  • condenser or gas cooler A - hereinafter referred to only as a condenser, which is usually outside the supermarket, for example, on the roof, by heat exchange, preferably against outside air condensed.
  • the liquid refrigerant from the condenser A is fed via line B to a (refrigerant) collector C.
  • a (refrigerant) collector C Within a refrigeration cycle always so much refrigerant must be present that even with maximum cooling demand, the evaporator of all refrigeration consumers can be filled. However, with lower cooling requirements individual evaporators are only partially filled or even completely empty, the excess refrigerant must be collected during these times in the designated collector C.
  • the refrigerant passes through the liquid line D to the cold consumers of the so-called normal cooling circuit.
  • the in the FIG. 1 represented consumers F and F 'for any number of consumers of the normal refrigeration cycle.
  • Each of the aforementioned refrigeration consumers is preceded by an expansion valve E or E ', in which the refrigerant flowing into the refrigeration appliance or the evaporator or the evaporator of the refrigeration consumer is expanded.
  • the so-relaxed refrigerant is evaporated in the evaporators of the refrigerant consumers F and F 'and thus cools the corresponding refrigeration cabinets and rooms.
  • the refrigerant evaporated in the refrigeration consumers F and F 'of the normal refrigeration cycle is then fed via the suction line G to the compressor unit H and compressed therein to the desired pressure between 10 and 25 bar.
  • the compressor unit H is designed to be single-stage and has several compressors connected in parallel.
  • the compressed in the compressor unit H refrigerant is then fed via the pressure line I in turn to the aforementioned condenser A.
  • a second liquid line D ' is the condenser C refrigerant supplied to the condenser K and evaporated in this heat exchange with the refrigerant of the still to be explained Tiefkühlniklaufes before it is fed via the line G' of the compressor unit H.
  • the liquefied in the condenser K refrigerant of the freezing circuit is supplied via line L to the collector M of the freezing circuit.
  • the refrigerant to the consumer P - this is for any number of consumers -, which is preceded by a relaxation device O, supplied and evaporated in this.
  • the suction line Q the vaporized refrigerant is fed to the single-stage or multi-stage compressor unit R, in this pressure compressed between 25 and 40 bar and then fed via the pressure line S to the aforementioned capacitor K.
  • R 404A As a refrigerant of the normal refrigeration cycle, for example, R 404A is used, while for the freezing cycle carbon dioxide is used.
  • compressor units H and R, the collector C and M and the capacitor K are usually arranged in a separate machine room.
  • about 80 to 90% of the entire pipeline network is located in the sales rooms, the storage areas or other areas of a supermarket accessible to employees and customers.
  • this line network operates at pressures of no more than 35 to 40 bar, this is acceptable to the supermarket operators both from a psychological point of view and for cost reasons.
  • Object of the present invention is to provide a generic refrigeration cycle and a method for operating a refrigeration cycle, which avoids the disadvantages mentioned.
  • an intermediate expansion device is arranged between the condenser and the collecting container.
  • a relaxation of the refrigerant to an (intermediate) pressure of 5 to 40 bar is carried out in the arranged between the condenser and the collecting intermediate relaxation device, a relaxation of the refrigerant to an (intermediate) pressure of 5 to 40 bar.
  • inventive refrigeration cycle the inventive method for operating a refrigeration cycle and other embodiments thereof are described below with reference to in the FIGS. 2 to 5 shown embodiments explained in more detail.
  • FIG. 2 a composite refrigeration system in which a possible embodiment of the refrigeration cycle according to the invention is realized.
  • a procedure is described in which as a refrigerant HFC (s), HFC (s) or CO 2 can be used.
  • the compressed in the compressor unit 6 to a pressure between 10 and 120 bar refrigerant is supplied via the pressure line 7 to the condenser or gas cooler 1 and condensed in this against outside air or deprived.
  • the refrigerant is supplied to the refrigerant collector 3, but now it is relaxed according to the invention in the intermediate expansion device a to an intermediate pressure of 5 to 40.
  • This intermediate relaxation offers the advantage that the downstream line network and the collector 3 only to a lower Pressure must be designed.
  • the pressure to which the refrigerant is expanded in the mentioned intermediate relaxation device a is hereby preferably selected so that it is still below the lowest expected condensing pressure.
  • the pressure line 7 with the collecting container 3, preferably with the gas space, connected or connectable can take place, for example, via a connecting line 17, in which an expansion valve h is arranged.
  • the pressure line 7 is connected or connectable to the line or line sections 2 or 2 ', 2 "connecting the condenser 1 and the collection container 3.
  • the gas space of the collecting container is connected to the input of the compressor unit 6 or connectable.
  • the selected intermediate pressure can now be kept constant for all operating conditions.
  • a scheme such that a constant difference value to the suction pressure exists. This ensures that the throttle steam fraction at the evaporators is comparatively small, with the result that the liquid and suction lines can be dimensioned correspondingly smaller.
  • This also applies to the condensate line, since now no gaseous components have to flow through them back into the condenser 1.
  • a portion of the withdrawn from the collector 3 via line 4 refrigerant is fed via line 8 one or more frozen consumers - represented by the heat exchanger E4 - which is also preceded by a relaxation valve d supplied.
  • this partial refrigerant flow is fed via the suction line 9 to the compressor unit 10 and compressed therein to the inlet pressure of the compressor unit 6.
  • the thus compressed refrigerant partial stream is then fed via line 11 to the input side of the compressor unit 6.
  • the invention further, it is proposed that - as in the FIG. 2 represented - the collecting container 3, a heat exchanger E1 can be connected upstream.
  • the heat exchanger E1 is preferably connected on the input side to the output of the condenser 1 or connectable.
  • a partial flow of the liquefied or desiccant refrigerant can now be withdrawn from the condenser or gas cooler 1 or line 2 via line 13, in which an expansion valve f is provided, and in the heat exchanger E1 against the heat exchanger E1 to be heated via line 2 'supplied refrigerant to be evaporated.
  • the vaporized refrigerant partial stream is then fed via line 14 to a compressor 6 ', which is associated with the above-described compressor unit 6 and which preferably sucks at a higher pressure level, and in this compressed to the desired final pressure of the compressor unit 6.
  • the refrigerant stream to be expanded in the intermediate expansion device a is preferably cooled to such an extent that the throttled vapor portion of the expanded refrigerant is minimized.
  • the resulting in the collector 3 throttle steam fractions can be sucked off via the line 12 and the dashed line 15 by means of the compressor 6 'at a higher pressure level.
  • FIG. 3 1 shows an embodiment of the refrigeration cycle according to the invention or of the method according to the invention for operating a refrigeration cycle, in which the refrigerant drawn off from the collecting container 3 via the line 4 is subjected to supercooling in the heat exchanger E5.
  • the supercooling - according to an advantageous embodiment of the invention - in heat exchange with the withdrawn from the reservoir 3 via line 12 flash gas.
  • Liquid lines such as those in the Figures 2 and 3 shown line 4, with a temperature level below the ambient temperature are exposed to heat radiation. This has the consequence that the refrigerant flowing inside the liquid line partially evaporates, thus resulting in the formation of undesirable vapor contents. To prevent this, refrigerant so far either by an expansion of a partial flow of the refrigerant and subsequent evaporation or by an internal heat transfer against a suction gas stream, which is thereby overheated, subcooled.
  • the temperature interval between the suction and liquid line or the circulating refrigerant therein may be too low to realize an internal heat transfer for the required supercooling of the refrigerant flowing in the liquid line.
  • the invention further developing is therefore - as already mentioned - proposed to cool the withdrawn from the sump 3 via line 4 refrigerant in the heat exchanger and subcooler E5 against the relaxed from the sump 3 via line 12 and in the valve e flash gas.
  • the expanded refrigerant which has been overheated in the heat exchanger E5 is fed via the line sections 12 'and 11 to the inlet of the compressor unit 6.
  • the procedure described thus has the additional advantage that the reliability of the compressor or compressor unit 6 is increased due to a safe overheating of the flash gas stream.
  • FIG. 4 shows a further embodiment of the refrigeration cycle according to the invention or the method according to the invention for operating a refrigeration cycle. For the sake of clarity is in the FIG. 4 only a part of the in the FIG. 2 and 3 illustrated refrigeration circuit according to the invention shown.
  • FIG. 4 shows a possible embodiment of the method according to the invention, in which at least temporarily a partial flow of the withdrawn from the reservoir 3 via line 12 flash gas via line 16 to a heat exchanger E6 and superheated in this against the compressed in the compressor unit 6 refrigerant.
  • the flash gas stream After passing through the heat exchanger / superheater E6, the flash gas stream is fed via line 16 'to the inlet of the compressor 6' of the compressor unit 6.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Transmitters (AREA)
  • Details Of Measuring And Other Instruments (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)

Claims (14)

  1. Circuit réfrigérant dans lequel un réfrigérant à un ou plusieurs composants, en particulier du CO2, circule,
    dans lequel le circuit réfrigérant permet un fonctionnement supercritique,
    présentant dans le sens d'écoulement un condenseur/refroidisseur à gaz (1), un dispositif de détente intermédiaire (a) pour la détente du réfrigérant à une pression intermédiaire de 5 à 40 bars, un récipient collecteur (3), un évaporateur (E2, E3) avec un dispositif de détente respectivement prémonté (b, c) et une unité de compresseur (6) raccordée aux évaporateurs (E2, E3) par une conduite d'aspiration (5),
    dans lequel l'espace de gaz du récipient collecteur (3) est ou peut être raccordé à l'entrée de l'unité de compresseur (6), dans lequel dans la conduite de raccordement (11, 12) entre l'espace de gaz du récipient collecteur (3) et l'entrée de l'unité de compresseur (6) une soupape de détente (e) est prévue ;
    dans lequel la conduite de liaison (11, 12) débouche dans la conduite d'aspiration (5) avant l'unité de compresseur (6) ; dans lequel le réfrigérant retiré du récipient collecteur (3) est amené par le biais d'une conduite (8) à un ou plusieurs consommateurs à refroidissement profond (E4) en amont desquels est montée une soupape de détente (d) ;
    dans lequel une unité de compresseur (10) est prévue, laquelle est alimentée par le biais d'une conduite d'aspiration (9) en réfrigérant évaporé dans le consommateur à refroidissement profond (E4) ; et
    dans lequel le réfrigérant compressé dans l'unité de compresseur (10) est amené par le biais d'une conduite d'aspiration (11) à l'unité de compresseur (6).
  2. Circuit réfrigérant selon la revendication 1, dans lequel un transmetteur thermique (E1) est monté en amont du récipient collecteur (3) et/ou dans lequel le transmetteur thermique (E1) est ou peut être relié côté entrée à la sortie du condenseur/refroidisseur à gaz (1) (2, 13).
  3. Circuit réfrigérant selon la revendication 2, dans lequel la conduite (2) se sépare du condenseur/refroidisseur à gaz (1) en une première section de conduite (2') et en une seconde section de conduite (13), dans lequel une soupape de détente (f) est agencée dans la seconde section de conduite (13), et dans lequel le réfrigérant est évaporé dans la seconde section de conduite (13) dans le transmetteur de chaleur (E1) contre le réfrigérant dans la première section de conduite (2'), et/ou dans lequel la seconde section de conduite (13, 14) est ou peut être reliée après le transmetteur de chaleur (E1) à l'entrée du compresseur (6') de l'unité de compresseur (6).
  4. Circuit réfrigérant selon l'une quelconque des revendications précédentes, dans lequel une conduite de pression (7) est prévue pour l'amenée de réfrigérant compressé de l'unité de compresseur (6) au condenseur/refroidisseur à gaz (1), et dans lequel la conduite de pression (7) est ou peut être raccordée à la conduite (2, 2', 2") raccordant le condenseur/refroidisseur à gaz (1) et le récipient collecteur (3).
  5. Circuit réfrigérant selon la revendication 4, dans lequel une conduite de pression (7) est prévue pour l'amenée de réfrigérant compressé de l'unité de compresseur (6) au condenseur/refroidisseur à gaz (1), et dans lequel une conduite (18) raccorde avec une soupape (j) prévue dedans la section de conduite (2', 2") entre le transmetteur de chaleur (E1) et le dispositif de détente intermédiaire (a) à la conduite de pression (7) après l'unité de compresseur (6), et/ou dans lequel une conduite (17) raccorde avec une soupape (h) prévue dedans la section de conduite entre le dispositif de détente intermédiaire (a) et le récipient collecteur (3) à la conduite de pression (7) après l'unité de compresseur (6).
  6. Circuit réfrigérant selon la revendication 5, dans lequel la pression intermédiaire choisie peut être régulée par le biais de la soupape de détente (e) dans la conduite (12) et par le biais de la soupape de détente (h) dans la conduite (17) et/ou par le biais de la soupape de détente (j) dans la conduite (18) de sorte qu'elle présente une valeur constante ou une différence constante par rapport à la pression d'aspiration.
  7. Circuit réfrigérant selon l'une quelconque des revendications précédentes, dans lequel l'espace de gaz du récipient collecteur (3) est ou peut être raccordé à l'entrée d'un compresseur (6') de l'unité de compresseur (6).
  8. Circuit réfrigérant selon l'une quelconque des revendications précédentes, dans lequel une conduite de pression (7) est prévue pour l'amenée de réfrigérant compressé de l'unité de compresseur (6) au condenseur/refroidisseur à gaz (1), et dans lequel un échangeur de chaleur (E6) est prévu dans lequel de la vapeur instantanée retirée du récipient collecteur (3) est surchauffée contre du réfrigérant compressé dans la conduite de pression (7).
  9. Circuit réfrigérant selon la revendication 8, dans lequel la vapeur instantanée est amenée après le passage par l'échangeur de chaleur/surchauffeur (E6) par le biais d'une conduite (16') à l'entrée du compresseur (6') de l'unité de compresseur (6).
  10. Procédé de fonctionnement supercritique d'un circuit réfrigérant selon l'une quelconque des revendications précédentes,
    dans lequel un réfrigérant à un ou plusieurs composants, en particulier du CO2, circule,
    dans lequel dans le dispositif de détente intermédiaire (a) agencé entre le condenseur/refroidisseur à gaz (1) et le récipient collecteur (3) une détente du réfrigérant est effectuée à une pression intermédiaire de 5 à 40 bars,
    caractérisé en ce que
    par une soupape de détente (e) dans la conduite de liaison (11 12), qui raccorde l'espace de gaz du récipient collecteur (3) à l'entrée de l'unité compresseur (6) et débouche dans la conduite d'aspiration (5) avant l'unité de compresseur (6), la pression intermédiaire est maintenue constante.
  11. Procédé selon la revendication 10, dans lequel le réfrigérant (2) est refroidi avant sa détente intermédiaire (a), dans lequel le refroidissement (E1) du réfrigérant (2) est effectué en particulier contre un courant partiel du réfrigérant (13).
  12. Procédé selon la revendication 11, dans lequel le réfrigérant (4) retiré du récipient collecteur (3) est sous-refroidi.
  13. Procédé selon l'une quelconque des revendications 10 à 12, dans lequel au moins un courant partiel de la vapeur instantanée retirée (12) du récipient collecteur (3) est surchauffé au moins temporairement contre le réfrigérant compressé (7).
  14. Procédé selon l'une quelconque des revendications 10 à 13, dans lequel la pression intermédiaire est réglée au moyen d'au moins une soupape (e, h, j) à une valeur constante et/ou à une différence constante par rapport à la pression d'aspiration, dans lequel cette régulation est effectuée en particulier par le biais de la soupape de détente (e) dans la conduite (12) et par le biais de la soupape de détente (h) dans la conduite (17) et/ou par le biais de la soupape de détente (j) dans la conduite (18).
EP10167202.0A 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant Active EP2244040B1 (fr)

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DE102004038640A DE102004038640A1 (de) 2004-08-09 2004-08-09 Kältekreislauf und Verfahen zum Betreiben eines Kältekreislaufes
PCT/EP2005/008255 WO2006015741A1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique
EP05775838A EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique

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EP05715407.2A Active EP1782001B1 (fr) 2004-08-09 2005-02-18 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP05723393A Not-in-force EP1794510B1 (fr) 2004-08-09 2005-02-18 Circuit de réfrigération à co2 avec sous-refroidissement de l'agent réfrigérant liquide contre la vapeur instantanée de la bouteille accumulatrice et méthode pour exploiter celui-ci
EP07020311.2A Active EP1895246B3 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique
EP10181303.8A Active EP2264385B1 (fr) 2004-08-09 2005-07-29 Cycle frigorifique et procédé d'operation d'un cycle frigorifique
EP05775838A Active EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique
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EP05715407.2A Active EP1782001B1 (fr) 2004-08-09 2005-02-18 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP05723393A Not-in-force EP1794510B1 (fr) 2004-08-09 2005-02-18 Circuit de réfrigération à co2 avec sous-refroidissement de l'agent réfrigérant liquide contre la vapeur instantanée de la bouteille accumulatrice et méthode pour exploiter celui-ci
EP07020311.2A Active EP1895246B3 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique
EP10181303.8A Active EP2264385B1 (fr) 2004-08-09 2005-07-29 Cycle frigorifique et procédé d'operation d'un cycle frigorifique
EP05775838A Active EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique

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US (2) US7644593B2 (fr)
EP (6) EP1782001B1 (fr)
KR (2) KR20070050046A (fr)
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AU (2) AU2005278162A1 (fr)
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Families Citing this family (56)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080196420A1 (en) * 2004-08-09 2008-08-21 Andreas Gernemann Flashgas Removal From a Receiver in a Refrigeration Circuit
WO2007111595A1 (fr) 2006-03-27 2007-10-04 Carrier Corporation Système réfrigérant avec circuits économiseurs étagés en parallèle à sortie transférée en pression interétage d'un compresseur principal
EP2008036B1 (fr) * 2006-03-27 2015-12-02 Carrier Corporation Système réfrigérant avec circuits économiseurs étagés parallèles employant une compression multi-étage
DK2005079T3 (en) * 2006-03-27 2017-02-06 Carrier Corp COOLING SYSTEM WITH PARALLEL STEP ECONOMIZER CIRCUIT AND ONE OR 2-STEP HEAD COMPRESSOR
CN101460790A (zh) * 2006-06-01 2009-06-17 开利公司 调节受控膨胀阀的系统与方法
EP2021703A4 (fr) * 2006-06-01 2012-02-15 Carrier Corp Unité de compresseur à étages multiples pour système de réfrigération
WO2008019689A2 (fr) * 2006-08-18 2008-02-21 Knudsen Køling A/S Système de réfrigération transcritique doté d'un surpresseur
DE102006050232B9 (de) * 2006-10-17 2008-09-18 Bitzer Kühlmaschinenbau Gmbh Kälteanlage
EP1921399A3 (fr) * 2006-11-13 2010-03-10 Hussmann Corporation Système de réfrigération transcritique à deux étapes
CN101413738A (zh) * 2007-10-17 2009-04-22 开利公司 一种中低温集成式冷藏/冷冻系统
JP2009139037A (ja) * 2007-12-07 2009-06-25 Mitsubishi Heavy Ind Ltd 冷媒回路
WO2010003590A2 (fr) * 2008-07-07 2010-01-14 Carrier Corporation Circuit de réfrigération
US20110113822A1 (en) * 2008-07-07 2011-05-19 Carrier Corporation Refrigerating Circuit
US8631666B2 (en) * 2008-08-07 2014-01-21 Hill Phoenix, Inc. Modular CO2 refrigeration system
CA2820930C (fr) 2008-10-23 2016-04-26 Serge Dube Systeme frigorifique par co2
ITTV20080140A1 (it) * 2008-11-04 2010-05-05 Enex Srl Sistema frigorifero con compressore alternativo ed economizzatore.
US20100281914A1 (en) * 2009-05-07 2010-11-11 Dew Point Control, Llc Chilled water skid for natural gas processing
JP2013510286A (ja) * 2009-11-03 2013-03-21 イー・アイ・デュポン・ドウ・ヌムール・アンド・カンパニー フルオロオレフィン冷媒を用いるカスケード冷凍システム
JP5595025B2 (ja) * 2009-12-10 2014-09-24 三菱重工業株式会社 空気調和機および空気調和機の冷媒量検出方法
CA2724255C (fr) * 2010-09-28 2011-09-13 Serge Dube Systeme de refrigeration au co2 pour surfaces de sports sur glace
CN102589217B (zh) * 2011-01-10 2016-02-03 珠海格力电器股份有限公司 冷媒量控制装置和方法及具有该控制装置的空调机组
DK2663817T3 (en) * 2011-01-14 2019-01-28 Carrier Corp COOLING SYSTEM AND PROCEDURE FOR OPERATING A COOLING SYSTEM.
DK177329B1 (en) 2011-06-16 2013-01-14 Advansor As Refrigeration system
US8863494B2 (en) 2011-10-06 2014-10-21 Hamilton Sundstrand Space Systems International, Inc. Turbine outlet frozen gas capture apparatus and method
US9109816B2 (en) * 2012-02-23 2015-08-18 Systemes Lmp Inc. Mechanical subcooling of transcritical R-744 refrigeration systems with heat pump heat reclaim and floating head pressure
CN104334984A (zh) * 2012-04-27 2015-02-04 开利公司 冷却系统
WO2013174379A1 (fr) 2012-05-22 2013-11-28 Danfoss A/S Procédé pour actionner une machine frigorifique à compression dans un climat chaud
JP6292480B2 (ja) * 2012-10-31 2018-03-14 パナソニックＩｐマネジメント株式会社 冷凍装置
CA2815783C (fr) 2013-04-05 2014-11-18 Marc-Andre Lesmerises Systeme de refroidissement au co2 et procede de fonctionnement de celui-ci
NZ714420A (en) 2013-05-03 2018-11-30 Hill Phoenix Inc Systems and methods for pressure control in a co2 refrigeration system
JP6091399B2 (ja) * 2013-10-17 2017-03-08 三菱電機株式会社 空気調和装置
EP2889558B1 (fr) 2013-12-30 2019-05-08 Rolls-Royce Corporation Système de refroidissement avec machine à expansion et éjecteur
US9739200B2 (en) 2013-12-30 2017-08-22 Rolls-Royce Corporation Cooling systems for high mach applications
US9696074B2 (en) * 2014-01-03 2017-07-04 Woodward, Inc. Controlling refrigeration compression systems
US9726411B2 (en) * 2015-03-04 2017-08-08 Heatcraft Refrigeration Products L.L.C. Modulated oversized compressors configuration for flash gas bypass in a carbon dioxide refrigeration system
US11656005B2 (en) 2015-04-29 2023-05-23 Gestion Marc-André Lesmerises Inc. CO2 cooling system and method for operating same
EP3187796A1 (fr) 2015-12-28 2017-07-05 Thermo King Corporation Système de transfert thermique en cascade
US11125483B2 (en) 2016-06-21 2021-09-21 Hill Phoenix, Inc. Refrigeration system with condenser temperature differential setpoint control
DE102016116028B4 (de) 2016-07-18 2019-12-12 imbut GmbH Verfahren zum Fixieren von elektronischen Bauelementen auf einem flexiblen, insbesondere textilen Flächengebilde
US10352604B2 (en) * 2016-12-06 2019-07-16 Heatcraft Refrigeration Products Llc System for controlling a refrigeration system with a parallel compressor
CN106766297B (zh) * 2016-12-22 2019-08-16 广州协义自动化科技有限公司 一种能快速恢复平衡压力的超低温水汽捕集泵系统
KR101891993B1 (ko) * 2017-01-19 2018-08-28 주식회사 신진에너텍 급냉실 냉동실 냉장실의 3단계 냉각 시스템
US10830499B2 (en) * 2017-03-21 2020-11-10 Heatcraft Refrigeration Products Llc Transcritical system with enhanced subcooling for high ambient temperature
US10648701B2 (en) 2018-02-06 2020-05-12 Thermo Fisher Scientific (Asheville) Llc Refrigeration systems and methods using water-cooled condenser and additional water cooling
US11022382B2 (en) 2018-03-08 2021-06-01 Johnson Controls Technology Company System and method for heat exchanger of an HVAC and R system
US11796227B2 (en) 2018-05-24 2023-10-24 Hill Phoenix, Inc. Refrigeration system with oil control system
US10907869B2 (en) 2018-05-24 2021-02-02 Honeywell International Inc. Integrated vapor cycle and pumped two-phase cooling system with latent thermal storage of refrigerants for transient thermal management
US11397032B2 (en) 2018-06-05 2022-07-26 Hill Phoenix, Inc. CO2 refrigeration system with magnetic refrigeration system cooling
US11187445B2 (en) 2018-07-02 2021-11-30 Heatcraft Refrigeration Products Llc Cooling system
US10663201B2 (en) 2018-10-23 2020-05-26 Hill Phoenix, Inc. CO2 refrigeration system with supercritical subcooling control
CN110332635B (zh) * 2019-07-09 2024-03-19 珠海格力节能环保制冷技术研究中心有限公司 一种双级压缩多补气制冷热泵系统、控制方法和空调器
CN110319613B (zh) * 2019-07-22 2023-05-26 北京市京科伦冷冻设备有限公司 单级二氧化碳制冷系统
CN114375382B (zh) * 2019-09-18 2023-10-24 株式会社日立产机系统 热回收装置
US11686513B2 (en) 2021-02-23 2023-06-27 Johnson Controls Tyco IP Holdings LLP Flash gas bypass systems and methods for an HVAC system
CN114459179B (zh) * 2021-12-27 2023-05-12 华北理工大学 人工冰场二氧化碳直接蒸发式制冰系统及其使用方法
CN115077114A (zh) * 2022-06-08 2022-09-20 松下冷机系统（大连）有限公司 Co2跨临界船用碳捕集制冷机组

Family Cites Families (50)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US933682A (en) * 1908-07-03 1909-09-07 Gardner Tufts Voorhees Multiple-effect receiver.
US1860447A (en) * 1928-07-21 1932-05-31 York Ice Machinery Corp Refrigeration
US2585908A (en) * 1944-12-19 1952-02-19 Electrolux Ab Multiple temperature refrigeration system
US2680956A (en) * 1951-12-19 1954-06-15 Haskris Co Plural stage refrigeration system
US3150498A (en) * 1962-03-08 1964-09-29 Ray Winther Company Method and apparatus for defrosting refrigeration systems
US4151724A (en) * 1977-06-13 1979-05-01 Frick Company Pressurized refrigerant feed with recirculation for compound compression refrigeration systems
JPS5523859A (en) 1978-08-08 1980-02-20 Tokyo Shibaura Electric Co Pluralltemperature refrigeration cycle
FR2513747A1 (fr) * 1981-09-25 1983-04-01 Satam Brandt Froid Installation frigorifique a multimotocompresseurs
US4430866A (en) * 1982-09-07 1984-02-14 Emhart Industries, Inc. Pressure control means for refrigeration systems of the energy conservation type
JPS60262A (ja) * 1983-06-17 1985-01-05 株式会社日立製作所 冷凍サイクル
US4947655A (en) * 1984-01-11 1990-08-14 Copeland Corporation Refrigeration system
US4599873A (en) * 1984-01-31 1986-07-15 Hyde Robert E Apparatus for maximizing refrigeration capacity
JPS6164526A (ja) 1984-09-06 1986-04-02 Nippon Denso Co Ltd 車両用冷房冷凍装置
DE3440253A1 (de) 1984-11-03 1986-05-15 Bitzer Kühlmaschinenbau GmbH & Co KG, 7032 Sindelfingen Kuehlvorrichtung
US4621505A (en) * 1985-08-01 1986-11-11 Hussmann Corporation Flow-through surge receiver
US4742694A (en) * 1987-04-17 1988-05-10 Nippondenso Co., Ltd. Refrigerant apparatus
FR2620205A1 (fr) * 1987-09-04 1989-03-10 Zimmern Bernard Compresseur hermetique pour refrigeration avec moteur refroidi par gaz d'economiseur
US4779427A (en) * 1988-01-22 1988-10-25 E. Squared Incorporated Heat actuated heat pump
US4831835A (en) * 1988-04-21 1989-05-23 Tyler Refrigeration Corporation Refrigeration system
JPH01318860A (ja) 1988-06-20 1989-12-25 Toshiba Corp 冷凍サイクル装置
US5042268A (en) 1989-11-22 1991-08-27 Labrecque James C Refrigeration
US5042262A (en) * 1990-05-08 1991-08-27 Liquid Carbonic Corporation Food freezer
US5103650A (en) * 1991-03-29 1992-04-14 General Electric Company Refrigeration systems with multiple evaporators
GB2258298B (en) * 1991-07-31 1995-05-17 Star Refrigeration Cooling method and apparatus
JPH0545007A (ja) * 1991-08-09 1993-02-23 Nippondenso Co Ltd 冷凍サイクル
US5174123A (en) 1991-08-23 1992-12-29 Thermo King Corporation Methods and apparatus for operating a refrigeration system
US5191776A (en) * 1991-11-04 1993-03-09 General Electric Company Household refrigerator with improved circuit
JPH06159826A (ja) * 1992-11-24 1994-06-07 Hitachi Ltd 多段圧縮冷凍装置
DE4309137A1 (de) * 1993-02-02 1994-08-04 Otfried Dipl Ing Knappe Verfahren für einen Kälteprozeß und Vorrichtung zur Durchführung desselben
DE69414077T2 (de) * 1993-12-14 1999-06-10 Carrier Corp., Syracuse, N.Y. Betrieb eines Economisers für Anlagen mit zweistufigem Verdichter
JPH07225059A (ja) * 1994-02-14 1995-08-22 Teruo Kinoshita 多機能冷凍サイクルシステム
JPH085163A (ja) 1994-06-16 1996-01-12 Mitsubishi Heavy Ind Ltd 冷凍サイクル装置
US5522233A (en) * 1994-12-21 1996-06-04 Carrier Corporation Makeup oil system for first stage oil separation in booster system
DE19522884A1 (de) * 1995-06-23 1997-01-02 Inst Luft Kaeltetech Gem Gmbh Verfahren zum Betrieb einer Kompressionskälteanlage
FR2738331B1 (fr) * 1995-09-01 1997-11-21 Profroid Ind Sa Dispositif d'optimisation energetique d'un ensemble de refrigeration a compression et a detente directe
NO970066D0 (no) * 1997-01-08 1997-01-08 Norild As Kuldeanlegg med lukket sirkulasjonskrets
JPH1163694A (ja) * 1997-08-21 1999-03-05 Zexel Corp 冷却サイクル
JP2000154941A (ja) * 1998-11-19 2000-06-06 Matsushita Electric Ind Co Ltd 冷凍装置
PT1162414E (pt) 1999-02-17 2006-09-29 Yanmar Co Ltd Circuito para super-refrigeracao de um refrigerante
EP1046869B1 (fr) * 1999-04-20 2005-02-02 Sanden Corporation Système de réfrigération et d'air conditionné
DE19920726A1 (de) * 1999-05-05 2000-11-09 Linde Ag Kälteanlage
US6276148B1 (en) * 2000-02-16 2001-08-21 David N. Shaw Boosted air source heat pump
CN100416191C (zh) * 2000-09-15 2008-09-03 迈尔高装备公司 安静的制冰设备
JP2002156161A (ja) * 2000-11-16 2002-05-31 Mitsubishi Heavy Ind Ltd 空気調和装置
US6470693B1 (en) * 2001-07-11 2002-10-29 Ingersoll-Rand Company Compressed air refrigeration system
JP3603848B2 (ja) * 2001-10-23 2004-12-22 ダイキン工業株式会社 冷凍装置
US6981377B2 (en) * 2002-02-25 2006-01-03 Outfitter Energy Inc System and method for generation of electricity and power from waste heat and solar sources
JP2003254661A (ja) 2002-02-27 2003-09-10 Toshiba Corp 冷蔵庫
US6694763B2 (en) * 2002-05-30 2004-02-24 Praxair Technology, Inc. Method for operating a transcritical refrigeration system
DE10258524A1 (de) * 2002-12-14 2004-07-15 Volkswagen Ag Kältemittelkreislauf für eine Kfz-Klimaanlage

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
GIROTTO S ET AL: "COMMERCIAL REFRIGERATION SYSTEM WITH CO2 AS REFRIGERANT EXPERIMENTAL RESULTS", INTERNATIONAL CONGRESS OF REFRIGERATION. PROCEEDINGS - CONGRESINTERNATIONAL DU FROID. COMPTES RENDUS, XX, XX, 17 August 2003 (2003-08-17), pages 1 - 08, XP000962253 *

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KR20070046847A (ko) 2007-05-03
US8113008B2 (en) 2012-02-14
EP1895246A3 (fr) 2009-02-11
EP1782001A1 (fr) 2007-05-09
EP2264385B1 (fr) 2018-04-11
CN101713596B (zh) 2012-08-08
RU2007107807A (ru) 2008-09-20
HK1101199A1 (en) 2007-10-12
DK1895246T6 (da) 2019-06-11
EP1789732A1 (fr) 2007-05-30
NO20071229L (no) 2007-03-06
WO2006022829A1 (fr) 2006-03-02
EP1895246B3 (fr) 2018-05-02
CN101040153A (zh) 2007-09-19
AU2005278162A1 (en) 2006-03-02
EP2264385A3 (fr) 2011-10-19
WO2006022829A8 (fr) 2007-03-22
EP2264385A2 (fr) 2010-12-22
EP1794510A1 (fr) 2007-06-13
EP2244040A3 (fr) 2011-10-12
DK2244040T3 (da) 2019-12-02
DK2264385T3 (en) 2018-07-23
CN101014815A (zh) 2007-08-08
US20080078203A1 (en) 2008-04-03
EP1895246B1 (fr) 2016-11-23
EP1782001B1 (fr) 2016-11-30
NO343330B1 (no) 2019-02-04
CN100582603C (zh) 2010-01-20
CN100507402C (zh) 2009-07-01
EP1794510B1 (fr) 2012-02-08
US7644593B2 (en) 2010-01-12
EP1789732B1 (fr) 2011-03-23
DK1794510T3 (da) 2012-05-21
AU2005270472B2 (en) 2011-01-06
ATE544992T1 (de) 2012-02-15
KR20070050046A (ko) 2007-05-14
EP2244040A2 (fr) 2010-10-27
EP1895246A2 (fr) 2008-03-05
CN101713596A (zh) 2010-05-26
AU2005270472A1 (en) 2006-02-16
US20080104981A1 (en) 2008-05-08
DK1895246T3 (da) 2017-03-06
RU2362096C2 (ru) 2009-07-20

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