EP1789732B1 - Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique - Google Patents

Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique Download PDF

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Publication number
EP1789732B1
EP1789732B1 EP05775838A EP05775838A EP1789732B1 EP 1789732 B1 EP1789732 B1 EP 1789732B1 EP 05775838 A EP05775838 A EP 05775838A EP 05775838 A EP05775838 A EP 05775838A EP 1789732 B1 EP1789732 B1 EP 1789732B1
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EP
European Patent Office
Prior art keywords
line
refrigerant
collecting container
refrigeration circuit
compressor unit
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.)
Active
Application number
EP05775838A
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German (de)
English (en)
Other versions
EP1789732A1 (fr
Inventor
Bernd Heinbokel
Andreas Gernemann
Uwe Schierhorn
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.)
Carrier Kaeltetechnik Deutschland GmbH
Original Assignee
Linde Kaeltetechnik GmbH
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
Priority claimed from DE102004038640A external-priority patent/DE102004038640A1/de
Priority to EP10181303.8A priority Critical patent/EP2264385B1/fr
Priority to EP07020311.2A priority patent/EP1895246B3/fr
Priority to EP10167202.0A priority patent/EP2244040B1/fr
Priority to DK10181303.8T priority patent/DK2264385T3/en
Priority to DK07020311.2T priority patent/DK1895246T6/da
Application filed by Linde Kaeltetechnik GmbH filed Critical Linde Kaeltetechnik GmbH
Priority to DK10167202T priority patent/DK2244040T3/da
Publication of EP1789732A1 publication Critical patent/EP1789732A1/fr
Publication of EP1789732B1 publication Critical patent/EP1789732B1/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 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 evaporated refrigerant is fed to the single or multi-stage compressor unit R, in this to a 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.
  • 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 collector, which in the lower part of the medium pressure separator collecting, larger liquid Hästoffmassestromanteil supplied to the evaporator, the separating in the upper part of the medium pressure separating, smaller vapor Häffenmassestromanteil a second throttle level close to the Evaporating pressure relaxes.
  • 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 refrigeration cycle comprising a compressor, which comprises a Hochlichsaugeingang and a Niedrigdrucksaugeingang with a condenser, with a collecting container, the liquid refrigerant in its lower part and gaseous refrigerant in its upper part, with a line which the liquid refrigerant of the Capacitor to the Sump leads, with a pressure reducing valve in this line, with a high-pressure cooler, with a line leading from the lower part of the sump to the radiator, with a line leading from the radiator to the upper part of the sump, with a line, which leads from the upper part of the collecting container to the high-pressure inlet of the compressor, with a low-pressure radiator, with a line leading from the lower part of the collecting container to the low-pressure radiator, with a pressure reducing valve in this line and with a line coming from the low-pressure radiator the low pressure suction inlet of the compressor leads.
  • the EP 0 180 904 B1 discloses a cooling device with a multi-cylinder piston compressor, which also includes a subcooler for the refrigerant liquid in the line between the condenser and expansion element.
  • 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.
  • a refrigeration cycle which is characterized in that between the condenser and the collecting container, an intermediate-expansion device is arranged.
  • 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 collecting container 3 preferably the gas space, connected to the input of the compressor unit 6 or connectable.
  • This connection between the collecting container 3 and the input of the compressor unit 6 can, for example, via a connecting line 12, as in the FIG. 2 shown, in the suction line 11 opens, done.
  • 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 to one or more frozen consumers - represented by the heat exchanger E4 -, which is also preceded by an expansion 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 or 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 above described method 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 inventive method for operating a refrigeration cycle.
  • the FIG. 4 only a section of the in the FIG. 2 and 3 illustrated refrigeration circuit according to the invention shown.
  • the method according to the invention for operating a refrigeration cycle further develops that at least a partial flow of the flash gas withdrawn from the collecting container is at least temporarily overheated against at least a partial flow of the compressed refrigerant.
  • 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)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (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)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
  • Details Of Measuring And Other Instruments (AREA)
  • Transmitters (AREA)

Claims (19)

  1. Circuit frigorifique, dans lequel circule un réfrigérant à un ou plusieurs composants, en particulier du CO2, le circuit frigorifique permettant un fonctionnement supercritique et comportant dans le sens d'écoulement un condenseur/dispositif de refroidissement de gaz (1), un dispositif de détente intermédiaire (a), un récipient collecteur (3), un dispositif de détente (b, c) monté en amont d'un évaporateur (E2, E3), un évaporateur (E2, E3) et une unité de compression comprimante à un étage (6), la chambre des gaz du récipient collecteur (3) étant raccordée ou raccordable à l'entrée de l'unité de compression (6) et une vanne de détente (e) étant prévue dans la conduite de raccordement (11, 12) entre la chambre des gaz du récipient collecteur (3) et l'entrée de l'unité de compression (6), caractérisé
    en ce qu'un échangeur de chaleur/sous-refroidisseur (E5) est disposé entre le récipient collecteur (3) et le dispositif de détente (b, c) monté en amont d'un évaporateur (E2, E3), et en ce que dans l'échangeur de chaleur/sous-refroidisseur (E5) a lieu un sous-refroidissement du réfrigérant soutiré du récipient collecteur (3) par rapport à la vapeur instantanée détendue par la vanne de détente (e) et soutirée du récipient collecteur (3) par le biais de la conduite de raccordement (11, 12).
  2. Circuit frigorifique selon la revendication 1, dans lequel un récupérateur de chaleur (E1) est monté en amont du récipient collecteur (3).
  3. Circuit frigorifique selon la revendication 2, dans lequel l'entrée du récupérateur de chaleur (E1) est raccordée ou raccordable (2, 13) à la sortie du condenseur/dispositif de refroidissement de gaz (1).
  4. Circuit frigorifique selon la revendication 2 ou 3, dans lequel la conduite (2) est divisée par le condenseur/dispositif de refroidissement de gaz (1) en une première section de conduite (2') et une deuxième section de conduite (13), une vanne de détente (f) étant disposée dans la deuxième section de conduite (13), et le réfrigérant étant évaporé dans la deuxième section de conduite (13) dans le récupérateur de chaleur (E1) par rapport au réfrigérant dans la première section de conduite (2').
  5. Circuit frigorifique selon la revendication 4, dans lequel la deuxième section de conduite (13, 14) est raccordée ou raccordable à l'entrée du compresseur (6') de l'unité de compression (6) en aval du récupérateur de chaleur (E1).
  6. Circuit frigorifique selon la revendication 4 ou 5, dans lequel il est prévu une conduite d'alimentation (7) servant à amener le réfrigérant compressé par l'unité de compression (6) au condenseur/dispositif de refroidissement de gaz (1), et dans lequel la conduite d'alimentation (7) est raccordée ou raccordable à la conduite (2, 2', 2") raccordant le condenseur/dispositif de refroidissement de gaz (1) et le récipient collecteur (3).
  7. Circuit frigorifique selon l'une quelconque des revendications 4 à 6, dans lequel il est prévu une conduite d'alimentation (7) servant à amener le réfrigérant compressé par l'unité de compression (6) au condenseur/dispositif de refroidissement de gaz (1), et dans lequel la conduite (18), dans laquelle il est prévu une vanne (j), raccorde la première section de conduite (2') en aval du récupérateur de chaleur (E1) à la conduite d'alimentation (7) en aval de l'unité de compression (6).
  8. Circuit frigorifique selon l'une quelconque des revendications précédentes, dans lequel la chambre des gaz du récipient collecteur (3) est raccordée ou raccordable à l'entrée d'un compresseur (6') de l'unité de compression (6).
  9. Circuit frigorifique selon l'une quelconque des revendications précédentes, dans lequel il est prévu une conduite d'alimentation (7) servant à amener le réfrigérant compressé depuis l'unité de compression (6) au condenséur/dispositif de refroidissement de gaz (1), et dans lequel la conduite d'alimentation (7) est raccordée ou raccordable au récipient collecteur (3), de préférence à la chambre des gaz de ce dernier.
  10. Circuit frigorifique selon la revendication 9, dans lequel il est prévu une vanne de détente (h) dans la conduite (17) qui raccorde la conduite d'alimentation (7) au récipient collecteur (3).
  11. Circuit frigorifique selon l'une quelconque des revendications précédentes, dans lequel il est prévu une conduite d'alimentation (7) servant à amener le réfrigérant compressé depuis l'unité de compression (6) au condenseur/dispositif de refroidissement de gaz (1), et dans lequel il est prévu un échangeur de chaleur (E6) dans lequel la vapeur instantanée soustraite du récipient collecteur (12) est surchauffée par rapport au réfrigérant compressé dans la conduite d'alimentation (7).
  12. Circuit frigorifique selon la revendication 11, dans lequel la vapeur instantanée après avoir traversé l'échangeur de chaleur/surchauffeur (E6) est amenée par une conduite (16') à l'entrée du compresseur (6') de l'unité de compression (6).
  13. Circuit frigorifique selon l'une quelconque des revendications précédentes, dans lequel le réfrigérant soustrait du récipient collecteur (3) est amené par une conduite (8) à un ou plusieurs consommateurs frigorifiques (E4) en amont desquels est montée une vanne de détente (d).
  14. Circuit frigorifique selon la revendication 13, dans lequel il est prévu une unité de compression (10) qui est alimentée par le biais d'une conduite d'aspiration (9) avec le réfrigérant évaporé dans le consommateur frigorifique (E4), et dans lequel le réfrigérant compressé dans l'unité de compression (10) est amené à l'unité de compression (6) par le biais d'une conduite d'aspiration (11).
  15. Procédé de fonctionnement supercritique d'un circuit frigorifique selon l'une quelconque des revendications précédentes, dans lequel circule un réfrigérant à un ou plusieurs composants, en particulier du CO2, une détente du réfrigérant à une pression intermédiaire de 5 à 40 bars ayant lieu dans le dispositif de détente intermédiaire (a) disposé entre le condenseur/dispositif de refroidissement de gaz (1) et le récipient collecteur (3), caractérisé
    en ce que la pression intermédiaire est maintenue constante par la vanne de détente (e) dans la conduite de raccordement (11, 12) entre la chambre des gaz du récipient collecteur (3) et l'entrée de l'unité de compression (6), et en ce que le réfrigérant soustrait du récipient collecteur (3) est soumis dans un échangeur de chaleur/sous-refroidisseur (E5) à un sous-refroidissement par rapport à la vapeur instantanée soustraite du récipient collecteur (3) par le biais de la conduite de raccordement (11, 12) et détendue dans la vanne de détente (e).
  16. Procédé selon la revendication 15, dans lequel le réfrigérant (2) est refroidi avant sa détente intermédiaire (a).
  17. Procédé selon la revendication 16, dans lequel le refroidissement (E1) du réfrigérant (2) a lieu par rapport à un flux partiel du réfrigérant (13).
  18. Procédé selon l'une quelconque des revendications 15 à 17, dans lequel au moins un flux partiel de la vapeur instantanée (12) soustraite du récipient collecteur (3) est surchauffé au moins temporairement par rapport au réfrigérant comprimé (7).
  19. Procédé selon l'une quelconque des revendications 15 à 18, dans lequel la pression intermédiaire est régulée au moyen d'au moins une vanne (e, h, j) à une valeur constante et/ou à une différence constante par rapport à la pression d'aspiration.
EP05775838A 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique Active EP1789732B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP07020311.2A EP1895246B3 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique
EP10167202.0A EP2244040B1 (fr) 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
DK10181303.8T DK2264385T3 (en) 2004-08-09 2005-07-29 Cooling circuits and method for operating a cooling circuit.
DK07020311.2T DK1895246T6 (da) 2004-08-09 2005-07-29 Kølekredsløb og fremgangsmåde til drift af et kølekredsløb
EP10181303.8A EP2264385B1 (fr) 2004-08-09 2005-07-29 Cycle frigorifique et procédé d'operation d'un cycle frigorifique
DK10167202T DK2244040T3 (da) 2004-08-09 2005-07-29 Kølekredsløb og fremgangsmåde til drift af et kølekredsløb

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
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

Related Child Applications (6)

Application Number Title Priority Date Filing Date
EP10181303.8A Division EP2264385B1 (fr) 2004-08-09 2005-07-29 Cycle frigorifique et procédé d'operation d'un cycle frigorifique
EP10167202.0A Division EP2244040B1 (fr) 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP07020311.2A Division EP1895246B3 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique
EP07020311.2 Division-Into 2007-10-17
EP10167202.0 Division-Into 2010-06-24
EP10181303.8 Division-Into 2010-09-28

Publications (2)

Publication Number Publication Date
EP1789732A1 EP1789732A1 (fr) 2007-05-30
EP1789732B1 true EP1789732B1 (fr) 2011-03-23

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Application Number Title Priority Date Filing Date
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
EP05715407.2A Active EP1782001B1 (fr) 2004-08-09 2005-02-18 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP05775838A Active EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede 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
EP07020311.2A Active EP1895246B3 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique
EP10167202.0A Active EP2244040B1 (fr) 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant

Family Applications Before (2)

Application Number Title Priority Date Filing Date
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
EP05715407.2A Active EP1782001B1 (fr) 2004-08-09 2005-02-18 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant

Family Applications After (3)

Application Number Title Priority Date Filing Date
EP10181303.8A Active EP2264385B1 (fr) 2004-08-09 2005-07-29 Cycle frigorifique et procédé d'operation d'un cycle frigorifique
EP07020311.2A Active EP1895246B3 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique
EP10167202.0A Active EP2244040B1 (fr) 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant

Country Status (11)

Country Link
US (2) US7644593B2 (fr)
EP (6) EP1794510B1 (fr)
KR (2) KR20070050046A (fr)
CN (3) CN100507402C (fr)
AT (1) ATE544992T1 (fr)
AU (2) AU2005278162A1 (fr)
DK (4) DK1794510T3 (fr)
HK (2) HK1101199A1 (fr)
NO (1) NO343330B1 (fr)
RU (1) RU2362096C2 (fr)
WO (1) WO2006022829A1 (fr)

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US11852391B2 (en) 2013-05-03 2023-12-26 Hill Phoenix, Inc. Systems and methods for pressure control in a CO2 refrigeration system

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NO20071229L (no) 2007-03-06
US20080078203A1 (en) 2008-04-03
HK1144011A1 (en) 2011-01-21
EP2264385B1 (fr) 2018-04-11
EP1895246B3 (fr) 2018-05-02
CN101040153A (zh) 2007-09-19
DK2264385T3 (en) 2018-07-23
DK1794510T3 (da) 2012-05-21
EP2244040A2 (fr) 2010-10-27
RU2362096C2 (ru) 2009-07-20
EP1789732A1 (fr) 2007-05-30
US7644593B2 (en) 2010-01-12
ATE544992T1 (de) 2012-02-15
EP1782001A1 (fr) 2007-05-09
EP1794510A1 (fr) 2007-06-13
CN101713596A (zh) 2010-05-26
DK1895246T6 (da) 2019-06-11
EP2264385A2 (fr) 2010-12-22
CN100507402C (zh) 2009-07-01
EP2244040B1 (fr) 2019-08-28
KR20070046847A (ko) 2007-05-03
EP1895246A2 (fr) 2008-03-05
EP2264385A3 (fr) 2011-10-19
AU2005270472A1 (en) 2006-02-16
AU2005278162A1 (en) 2006-03-02
US20080104981A1 (en) 2008-05-08
KR20070050046A (ko) 2007-05-14
HK1101199A1 (en) 2007-10-12
NO343330B1 (no) 2019-02-04
EP1895246A3 (fr) 2009-02-11
EP2244040A3 (fr) 2011-10-12
US8113008B2 (en) 2012-02-14
EP1794510B1 (fr) 2012-02-08
DK1895246T3 (da) 2017-03-06
CN101014815A (zh) 2007-08-08
RU2007107807A (ru) 2008-09-20
CN100582603C (zh) 2010-01-20
WO2006022829A8 (fr) 2007-03-22
AU2005270472B2 (en) 2011-01-06
CN101713596B (zh) 2012-08-08
WO2006022829A1 (fr) 2006-03-02
DK2244040T3 (da) 2019-12-02
EP1895246B1 (fr) 2016-11-23
EP1782001B1 (fr) 2016-11-30

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