EP1895246B3 - Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique - Google Patents

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

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Publication number
EP1895246B3
EP1895246B3 EP07020311.2A EP07020311A EP1895246B3 EP 1895246 B3 EP1895246 B3 EP 1895246B3 EP 07020311 A EP07020311 A EP 07020311A EP 1895246 B3 EP1895246 B3 EP 1895246B3
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EP
European Patent Office
Prior art keywords
refrigerant
collecting container
compressor unit
line
refrigeration circuit
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
EP07020311.2A
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German (de)
English (en)
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EP1895246A3 (fr
EP1895246A2 (fr
EP1895246B1 (fr
Inventor
Bernd Heinbokel
Andreas Gernemann
Uwe Schierhorn
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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
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Publication of EP1895246A2 publication Critical patent/EP1895246A2/fr
Publication of EP1895246A3 publication Critical patent/EP1895246A3/fr
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Publication of EP1895246B1 publication Critical patent/EP1895246B1/fr
Publication of EP1895246B3 publication Critical patent/EP1895246B3/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. Furthermore, the invention relates to a method for operating a refrigeration cycle.
  • liquefier should be understood to mean both liquefier and gas cooler.
  • Generic refrigeration cycles are well known. They are for example in refrigeration systems, so-called composite refrigeration systems, such as those used in supermarkets, implemented. Composite refrigeration systems generally supply a variety of refrigerants, such asderäüme, refrigerators and freezers.
  • the liquid refrigerant from the condenser A is fed via line B to a (refrigerant) 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 vaporized in the Kälte Tootem F and F 'of the normal cooling circuit refrigerant is then fed via the suction line G of the compressor unit H and compressed in this to the desired pressure between 10 and 25 bar usually the compressor unit H is formed only one stage and has a plurality of parallel connected compressor on.
  • 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 Tiefkühlniklaufes is supplied via line L to the collector M of the freezing circuit From this is via the line N, the refrigerant to the consumer P - this is for any number of consumers - which is preceded by a relaxation device O, respectively and evaporated in this.
  • 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.
  • a refrigeration system includes a condenser for releasing heat into the environment, a refrigerant tank receiving refrigerant and allowing a mixture of the gas-phase and liquid-phase refrigerant, the liquid-phase refrigerant collecting in the lower portion of the container, means for refrigerating from the outlet side of the condenser to the tank, at least a first compressor that passes the refrigerant through the condenser, at least one evaporator operating in a low temperature environment, at least one second compressor that draws refrigerant through the low temperature evaporator, and a heat exchange line the lower portion of the container, which is normally immersed in liquid refrigerant, wherein the outlet of the second compressor is connected to the inlet end of the heat exchange line.
  • a cooling device for a motor vehicle is known.
  • the refrigerant is sucked into the inner part of a first compression chamber, which is the ninth cylinder of a compressor consisting of ten cylinders, from a suction port for cooling, and the refrigerant is sucked into a chamber having an inclined plate from an intake port, with a higher pressure than the refrigerant sucked into the inner part of the second compressor, which is a first cylinder, from a suction port to the refrigerant flow into the inner parts of the first and second compressors by the differences in pressure when a piston reached a connection hole.
  • the pressure for the refrigerant within the two compressors is raised before being compressed by a compressor, and the same amount of refrigerant suction can be obtained by a more compact compressor.
  • a refrigeration cycle which comprises a two-stage compressor on the high pressure side, an internal heat exchanger between the gas withdrawn at low pressure by the high pressure compressor and the gas expelled from the gas cooler, and a receiver having carbon dioxide in the liquid / gaseous state , From the collecting tank, a pump pumps the liquid CO 2 to the normal cooling refrigeration consumer, from where it flows back to the collecting tank.
  • the liquid CO 2 passes from the sump via a thermostatic valve to the direct expansion evaporator of a refrigerated refrigeration consumer, and after evaporation therein, the CO 2 is withdrawn by a low pressure compressor, vaporized and returned to the sump in the gaseous state where the gas is deprived and then withdrawn through the two-stage high-pressure compressor at the same pressure level, without a valve being arranged in the line leading from the collecting container to the two-stage high-pressure compressor.
  • the JP 1 318860 A shows a refrigeration cycle with a compressor having a normal refrigerant compressor section 4 and a freezer compressor section 3, with a sump 8, with a normal refrigerant evaporator 12 and a cryogenic evaporator 10.
  • Liquid refrigerant is from the bottom of the sump 8 via a line 8a to the normal cooling evaporator 12 and a separate line, in which a pressure reducer 9 is arranged, fed to a deep-freeze evaporator 10. From the deep-freeze evaporator 10, the refrigerant evaporated there then reaches the deep-freeze compressor section 3, and the refrigerant evaporated in the normal-temperature evaporator 12 enters the normal-length refrigerant compressor section 4. Gaseous refrigerant passes from the upper section of the sump 8 to the normal-low-pressure section 4 at the same pressure level in this line, a valve is provided.
  • 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.
  • 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 4 shown embodiments explained in more detail.
  • FIG. 2 its 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 fed via the pressure line 7 to the condenser or gas cooler 1 and condensed in this against external flow or deprived.
  • the refrigerant is supplied to the refrigerant collector 3 via the lines 2, 2 'and 2 ", but according to the invention it is expanded in the intermediate expansion device a to an intermediate pressure of 5 to 40 bar and the collector 3 must be designed only to a lower pressure.
  • 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 sump 3. preferably with the gas space, connected or connectable.
  • This connection between the pressure line 7 and the collecting container 3 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 liquefier 1 and the collecting 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.
  • refrigerant is withdrawn from the collector 3 and the refrigerant consumers or their heat exchangers E2 and E3 supplied. This is preceded by a respective expansion valve b and c, in which the refrigerant flowing into the refrigeration consumer is expanded.
  • the refrigerant evaporated in the refrigeration consumers E2 and E3 is then fed back to the compressor unit 6 via the suction line 5 or sucked out of the evaporators E2 and E3 by the latter.
  • 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 to the compressor unit 10 via the suction line 9 and compressed thereinto to the inlet pressure of the compressor unit 6.
  • the refrigerant partial stream thus compressed is then fed via line 11 to the inlet side of the compressor unit 6.
  • 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.
  • 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 subcooling takes place - in accordance with an advantageous embodiment of the invention - in heat exchange with the withdrawn from the reservoir 3 via line 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 to a suction gas stream, which is thereby overheated, undercooled
  • 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 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, Aunosti the refrigeration cycle of the invention or the inventive method for operating a Käftekrelsmoores.
  • Aunosti the refrigeration cycle of the invention or the inventive method for operating a Käftekrelsmoores 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
  • 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 supplied 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)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Details Of Measuring And Other Instruments (AREA)
  • Transmitters (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)

Claims (16)

  1. Circuit frigorifique, présentant, dans le sens d'écoulement, un condenseur/refroidisseur de gaz (1), un dispositif de détente intermédiaire (a), un récipient collecteur (3), un dispositif de détente (b, c) installé en amont d'un évaporateur (E2, E3), un évaporateur (E2, E3) et un groupe compresseur (6), un autre groupe compresseur (10) ainsi qu'au moins un consommateur congélateur (E4) étant prévus avec une soupape de détente (d) installée en amont, un réfrigérant étant prélevé du récipient collecteur (3) lors du fonctionnement par l'intermédiaire d'un conduit d'aspiration (4), étant détendu dans le dispositif de détente (b, c) et étant amené aux évaporateurs (E2, E3) et puis, après l'évaporation dans les évaporateurs (E2, E3), étant amené au groupe compresseur (6) par l'intermédiaire d'un conduit d'aspiration (5) et un flux partiel de réfrigérant provenant du récipient collecteur (3) également étant amené à l'au moins un consommateur congélateur (E4) par l'intermédiaire du conduit d'aspiration (4) et d'un conduit (8) déviant de ce dernier et étant amené, après l'évaporation s'y déroulant, à l'autre groupe compresseur (10), le circuit frigorifique permettant un fonctionnement surcritique, l'autre groupe compresseur (10) compressant, lors du fonctionnement, le flux partiel de réfrigérant à la pression d'entrée du groupe compresseur (6) et l'amenant, par l'intermédiaire d'un conduit d'aspiration (11), qui débouche dans le conduit d'aspiration (5) avant le groupe compresseur (6), au côté d'entrée du groupe compresseur (6), et le compartiment à gaz du récipient collecteur (3) étant relié ou pouvant être relié à l'entrée du groupe compresseur (6), et une soupape de détente (e) étant prévue dans le conduit de liaison (11, 12) entre le compartiment à gaz du récipient colleteur (3) et l'entrée du groupe compresseur (6).
  2. Circuit frigorifique selon la revendication 1, un échangeur de chaleur (E1) étant installé en amont du récipient collecteur (3).
  3. Circuit frigorifique selon la revendication 2, l'échangeur de chaleur (E1) étant relié ou pouvant être relié côté entrée à la sortie du condenseur (1).
  4. Circuit frigorifique selon la revendication 2 ou 3, l'échangeur de chaleur (E1) étant relié ou pouvant être relié côté sortie à l'entrée d'un compresseur (6') du groupe compresseur (6).
  5. Circuit frigorifique selon l'une quelconque des revendications précédentes, le compartiment à gaz du récipient collecteur (3) étant relié ou pouvant être relié à l'entrée du groupe compresseur (6).
  6. Circuit frigorifique selon l'une quelconque des revendications précédentes, le compartiment à gaz du récipient collecteur (3) étant relié ou pouvant être relié à l'entrée d'un compresseur (6') du groupe compresseur (6).
  7. Circuit frigorifique selon l'une quelconque des revendications précédentes, le conduit de pression (7) étant relié ou pouvant être relié au récipient collecteur (3), de préférence au compartiment à gaz de ce dernier, ou au conduit (2, 2', 2") reliant le condenseur/refroidisseur de gaz (1) et le récipient collecteur (3).
  8. Circuit frigorifique selon l'une quelconque des revendications précédentes, un échangeur de chaleur/ sous-refroidisseur (E5) étant disposé entre le récipient collecteur (3) et le dispositif de détente (c, b, d) installé en amont d'un évaporateur.
  9. Circuit frigorifique selon l'une quelconque des revendications précédentes, l'échangeur de chaleur/sous-refroidisseur (E5) étant relié ou pouvant être relié côté entrée au compartiment à gaz du récipient collecteur (3).
  10. Procédé servant à faire fonctionner un circuit frigorifique selon l'une quelconque des revendications précédentes, présentant les étapes suivantes consistant à :
    détendre le réfrigérant dans le dispositif de détente intermédiaire (a) disposé entre le condenseur/refroidisseur de gaz (1) et le récipient collecteur (3) à une pression intermédiaire allant de 5 à 40 bar,
    prélever le réfrigérant du récipient collecteur (3) et l'amener aux évaporateurs (E2, E3) par l'intermédiaire d'un conduit d'aspiration (4),
    détendre le réfrigérant dans les soupapes de détente (b, c) installées en amont des évaporateurs (E2, E3),
    évaporer le réfrigérant dans les évaporateurs (E2, E3) et amener le réfrigérant évaporé au groupe compresseur (6) par l'intermédiaire d'un conduit d'aspiration (5),
    amener un flux partiel de réfrigérant provenant du récipient collecteur (3) à l'au moins un consommateur congélateur (E4) par l'intermédiaire du conduit d'aspiration (4) et d'un conduit (8) déviant de ce dernier,
    évaporer le flux partiel de réfrigérant dans l'au moins un consommateur congélateur (E4),
    amener le flux partiel de réfrigérant évaporé à l'autre groupe compresseur (10);
    un fonctionnement supercritique devenant possible,
    l'autre groupe compresseur (10) compressant le flux partiel de réfrigérant à la pression d'entrée du groupe compresseur (6) et l'amenant, par l'intermédiaire d'un conduit d'aspiration (11), qui débouche dans le conduit d'aspiration (5) avant le groupe compresseur (6); au côté d'entrée du groupe compresseur (6), et la pression intermédiaire étant régulée à une valeur constante au moyen d'une soupape de détente (e) prévue dans le conduit de liaison (11, 12) entre le compartiment à gaz du récipient collecteur (3) et l'entrée du groupe compresseur (6).
  11. Procédé selon la revendication 10, le réfrigérant (2) étant refroidi avant sa détente intermédiaire (a).
  12. Procédé selon la revendication 11, le refroidissement (E1) du réfrigérant (2) se déroulant contrairement à un flux partiel du réfrigérant (13).
  13. Procédé selon l'une quelconque des revendications 10 à 12, le réfrigérant (4) prélevé du récipient collecteur (3) étant sous-refroidi.
  14. Procédé selon la revendication 13, le sous-refroidissement (E5) du réfrigérant (4) prélevé du récipient collecteur (3) se déroulant contrairement au gaz de vaporisation éclair (12) prélevé du récipient collecteur (3).
  15. Procédé selon l'une quelconque des revendications 10 à 14, au moins un flux partiel du gaz de vaporisation éclair (12) prélevé du récipient collecteur (3) étant surchauffé au moins de manière temporaire contrairement au réfrigérant (7) condensé.
  16. Procédé selon l'une quelconque des revendications 10 à 15, la pression intermédiaire étant régulée à une valeur constante au moyen au moins d'une soupape (e, h, j) et/ou à une différence constante par rapport à la pression d'aspiration.
EP07020311.2A 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique Active EP1895246B3 (fr)

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DE102004038640A DE102004038640A1 (de) 2004-08-09 2004-08-09 Kältekreislauf und Verfahen zum Betreiben eines Kältekreislaufes
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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
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
EP10167202.0A Active EP2244040B1 (fr) 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP07020311.2A Active EP1895246B3 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procédé 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
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
EP10167202.0A Active EP2244040B1 (fr) 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant

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EP (6) EP1782001B1 (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)
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WO2006022829A8 (fr) 2007-03-22
EP1895246A3 (fr) 2009-02-11
AU2005278162A1 (en) 2006-03-02
DK1895246T6 (da) 2019-06-11
EP2244040A3 (fr) 2011-10-12
ATE544992T1 (de) 2012-02-15
EP1794510A1 (fr) 2007-06-13
EP1782001A1 (fr) 2007-05-09
CN100507402C (zh) 2009-07-01
US8113008B2 (en) 2012-02-14
AU2005270472B2 (en) 2011-01-06
RU2362096C2 (ru) 2009-07-20
US20080104981A1 (en) 2008-05-08
DK2264385T3 (en) 2018-07-23
EP1895246A2 (fr) 2008-03-05
US7644593B2 (en) 2010-01-12
EP1789732A1 (fr) 2007-05-30
US20080078203A1 (en) 2008-04-03
DK2244040T3 (da) 2019-12-02
CN101014815A (zh) 2007-08-08
CN100582603C (zh) 2010-01-20
HK1101199A1 (en) 2007-10-12
EP2264385B1 (fr) 2018-04-11
NO20071229L (no) 2007-03-06
DK1794510T3 (da) 2012-05-21
EP1895246B1 (fr) 2016-11-23
WO2006022829A1 (fr) 2006-03-02
NO343330B1 (no) 2019-02-04
AU2005270472A1 (en) 2006-02-16
DK1895246T3 (da) 2017-03-06
EP2244040A2 (fr) 2010-10-27
KR20070050046A (ko) 2007-05-14
EP1789732B1 (fr) 2011-03-23
RU2007107807A (ru) 2008-09-20
CN101040153A (zh) 2007-09-19
EP2244040B1 (fr) 2019-08-28
EP1794510B1 (fr) 2012-02-08
CN101713596B (zh) 2012-08-08
EP2264385A3 (fr) 2011-10-19
CN101713596A (zh) 2010-05-26
EP1782001B1 (fr) 2016-11-30
HK1144011A1 (en) 2011-01-21
KR20070046847A (ko) 2007-05-03
EP2264385A2 (fr) 2010-12-22

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