EP1050726B1 - Système frigorifique - Google Patents

Système frigorifique Download PDF

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Publication number
EP1050726B1
EP1050726B1 EP00109558A EP00109558A EP1050726B1 EP 1050726 B1 EP1050726 B1 EP 1050726B1 EP 00109558 A EP00109558 A EP 00109558A EP 00109558 A EP00109558 A EP 00109558A EP 1050726 B1 EP1050726 B1 EP 1050726B1
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EP
European Patent Office
Prior art keywords
refrigeration
circuit
freezing
compressor
line
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.)
Expired - Lifetime
Application number
EP00109558A
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German (de)
English (en)
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EP1050726A3 (fr
EP1050726A2 (fr
Inventor
Klaus Koch
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
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Application filed by Linde Kaeltetechnik GmbH filed Critical Linde Kaeltetechnik GmbH
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Publication of EP1050726A3 publication Critical patent/EP1050726A3/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
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2400/16—Receivers
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves

Definitions

  • the invention relates to a refrigeration system according to the preamble of claim 1 and a method for defrosting this refrigeration system.
  • US-A-4 474 026 discloses a refrigeration system according to the preamble of claim 1.
  • Refrigeration systems are operated, for example, in supermarkets. They generally supply a variety of Kälte Toom, such as refrigerators, refrigerators and freezers. For this purpose circulates in them a one- or multi-component refrigerant or refrigerant mixture.
  • a refrigeration system - as known from DE-PS 39 28 430 - has a condenser, in which the pressurized refrigerant is condensed by indirect heat exchange, preferably against outside air.
  • the liquid refrigerant from the condenser is fed to a sump.
  • so much refrigerant must always be present so that even with maximum refrigeration demand, the evaporator of all refrigeration consumers can be filled.
  • the excess refrigerant must be collected during these times in the designated collection container.
  • the refrigerant is supplied to the Kältestedem.
  • Each refrigeration consumer is preceded by an expansion device, preferably an expansion valve, in which the refrigerant flowing into the refrigeration appliance or the evaporator (s) of the refrigeration consumer is expanded.
  • the so-relaxed refrigerant is evaporated in the evaporators of the refrigerant consumers and thus cools the corresponding refrigeration cabinets and rooms.
  • the thus evaporated refrigerant is then supplied via a suction line to a compressor unit.
  • These compressor units can be configured in one or more stages. As a rule, the individual compressor stages have several compressors connected in parallel. These compress the refrigerant and convey it via a riser in turn to the already mentioned condenser. While the compressor unit normally stands, for example, in a machine room arranged in the basement of a supermarket, the liquefier is located on the roof of the supermarket.
  • Object of the present invention is to provide a refrigeration system of the generic type, which makes a lower investment and operating costs and installation effort required.
  • the refrigeration system shown in FIG. 1 has only one condenser or condenser V. This can be - downstream according to an advantageous embodiment of the invention - a sump S1.
  • the liquid refrigerant from the condenser V is fed via line 1 to the collection container S1.
  • the refrigerant passes through the liquid lines 2 and 3 and 4 to the Kältestedem the normal cooling and freezing cycle.
  • the consumers V1 and V2 shown in the figure 1 for any number of consumers of Normal cooling circuit
  • the consumers V3 and V4 shown in Figure 1 are for any number of consumers of the freezing circuit.
  • Each refrigeration consumer V1 to V4 is preceded or assigned an expansion valve a to d, in which the refrigerant flowing into the refrigeration consumer 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 V1 to V4 and thus cools the corresponding refrigerated cabinets and rooms of the normal and the deep-freeze circuit.
  • the vaporized in the Kälte Toothem V1 and V2 of the normal refrigeration cycle refrigerant is supplied via a suction line 5 of the compressor unit of the normal refrigeration cycle.
  • This is - upstream according to a further advantageous embodiment of the refrigeration system according to the invention - a Saugsammel concerneder S2.
  • the compressor unit of the normal cooling circuit is formed in one stage only and has a plurality, preferably three parallel compressors; For the sake of clarity, only two compressors C1 and C2 connected in parallel are shown in the figure. These suck in via the lines 6 and 7 refrigerant from the Saugsammel matterser S2 and promote the compressed refrigerant via the pressure line 8 to a desuperizer E. After passing through the Enthitzers E, the refrigerant is again supplied via line 9 to the already described condenser or condenser V.
  • FIG. 1 does not show the required further cooling or subcooling of the refrigerant in the liquid line 4, which can take place, for example, in indirect heat exchange with the refrigerant conveyed in the line 10.
  • the device for subcooling the refrigerant in the liquid line 4 of the freezing circuit is spatially as close as possible to the Kältearranged V3 and V4 of the freezing circuit arranged.
  • a low-pressure suction collecting container S3 can be connected upstream of the compressor unit of the deep-freeze circuit.
  • the compressor unit of the deep-freeze circuit is preferably formed in at least two stages, again for the sake of clarity, each compressor stage is represented by two parallel compressors C3 and C5 and C4 and C6.
  • the compressors C3 and C5 of the first compressor stage suck via the lines 11 and 12 gaseous refrigerant from the low-pressure suction collecting container S3 and convey the compressed to an intermediate pressure refrigerant via line 13 into the intermediate pressure suction collecting container S4.
  • the compressors C4 and C6 of the second compressor stage via the lines 14 and 15 refrigerant and then convey the compressed refrigerant via the pressure line 16 also before the already mentioned desuperheater E in the line.
  • the compressor unit of the freezing cycle can also be configured in three or more stages; In this case, the individual compressor stages could each be preceded by separate suction collecting containers. It should be noted that, of course, can be dispensed with such Saugsammel practicer.
  • the refrigeration system according to the invention has a lower investment and operating costs and installation costs compared to the known solutions. It also allows - as will be explained - further structural design - methods and procedures that are difficult or impossible to implement with the previous solutions.
  • Refrigeration system or arranged in the refrigeration consumers evaporator must be defrosted at regular intervals, as Verreifept or icing of the evaporator lead to a reduction in the efficiency of the evaporator.
  • electro-defrosting One possibility of defrosting is so-called electro-defrosting.
  • the evaporators are defrosted by means arranged on and / or in them heaters.
  • the pressure lines 8 and 16 of the compressor units C1 / C2 and C3 / C4 / C5 / C6 via a defrosting line 30, which preferably z. B. by means of a valve e, lockable, connected to the suction line 10 of the compressor unit C3 / C4 / C5 / C6 of the freezing circuit.
  • the supply of refrigerant from the compressor unit C1 / C2 of the normal refrigeration circuit to the condenser V is now interrupted, the compressor unit C3 / C4 / C5 / C6 of the freezing circuit turned off and the heated refrigerant via the open deflation line 30 of the suction line 10 and over this supplied to the refrigeration consumers V3 and V4 of the freezing circuit.
  • the flow course of the refrigerant during the defrosting phase is represented by the large, framed arrows.
  • the refrigerant flowing through the refrigeration consumers V3 and V4 of the freezing cycle or the evaporator thereof is supplied via the lines 3 and 4 to the refrigeration consumers V1 and V2 of the normal refrigeration cycle and then conveyed back to the compressor unit C1 / C2 of the normal refrigeration cycle via the suction line 5.
  • the compressor unit C1 / C2 thus operates as a heat pump.
  • the defrosting line 30 is closed again by closing the valve e, the compressor unit C3 / C4 / C5 / C6 of the deep-freezing circuit is switched on and switched to the cooling mode.
  • the refrigerant now flows again via the pressure lines 8 and 16 and the common pressure line 9 from the compressor units C1 / C2 and C3 / C4 / C5 / C6 to the condenser V.
  • a further advantageous embodiment of the refrigeration system according to the invention is therefore characterized in that at least one of the refrigeration consumers V3 and V4 of the freezing circuit or the evaporators of this refrigerated consumer a directly controlled Solenoid valve, which is arranged parallel to the corresponding expansion valve of the refrigeration consumer, is connected upstream.
  • FIG. 2 shows the immediate region of the cold consumer V3 shown in FIG. this is the area encircled by a broken line in FIG.
  • a direct-controlled solenoid valve c ' is now provided parallel to the expansion valve c in a bypass line 41.
  • the refrigerant flows through the not shown in Figure 2 Abtau réelle 30 and the suction line 10 in the evaporator of Kälteshuers V3 and then via lines 42 and 41 in the liquid line 4. Is in one of the evaporator reaches the preset defrost end temperature - what For example, can be registered by means of a corresponding defrost probe -, the solenoid valve c 'is closed.
  • the direct-operated solenoid valve c acts in the currentless coil as a check valve with an opening pressure of about 1.5 bar, which is due to the valve. Closing a solenoid valve at the appropriate defrost end temperature shifts defrosting power to those evaporators that have not yet reached defrost end temperature. An already defrosted evaporator is therefore not supplied unnecessarily refrigerant, but only more those evaporators that are not completely defrosted. These thus reach the specified defrost end temperature in a shorter time.
  • the evaporators After completion of the defrosting phase, the evaporators are simultaneously sucked off via the compressors of the normal and deep-freeze circuits. As soon as the evaporator pressure drops lower than the temperature of the T (hermostatic) E (xpansions) V (entil) sensor, refrigerant is automatically re-injected into the evaporator. The cooling of the evaporator of the deep-freeze cycle takes about 5 minutes. For this purpose, in addition to the power of the compressor of the deep-freeze circuit and the performance of the compressor of the normal refrigeration cycle available because the cold spots or cold consumers of the normal refrigeration cycle are switched to forced cooling during defrosting the evaporator of the refrigeration consumers V3 and V4 of the freezing circuit and thereby temperatures below the target Achieve value. For the entire freezer area, therefore, a significantly lower defrost time compared to the electric defrost can be achieved.
  • the implementation of the described defrosting requires in the refrigeration system according to the invention compared to a refrigeration system in which a Elektroabtauung is performed, no overhead on piping and fittings. Since defrosting the evaporator of the refrigeration consumers V3 and V4 of the freezing circuit no power must be forced on - as is the case for example in the case of an electro defrost - is to be considered in the energy balance only the cooling after defrosting.
  • the defrosting per se is pure heat pump operation from the normal cooling composite set or the compressor unit C1 / C2.
  • Another advantage is the fact that the pipe insulation in poorly ventilated floor ducts and / or not moisten under the refrigerators, since they are forcibly heated every 48 hours during the defrosting process.
  • the goods are exposed to a lower temperature load, since only three times a week - for example on Tuesdays, Thursdays and Saturdays - must be defrosted. With separate refrigerant circuits and a cold gas defrost This is not possible because after 48 hours of cooling in the freezing circuit no defrosting for the first defrosting would be available.
  • the refrigeration system is operated in a so-called energy-saving mode.
  • energy-saving operation in this case those operating conditions are to be understood in which at the cooling furniture down the night blinds or drove over, the lights are off, the refrigerator doors are no longer open and thus no flow of goods - ie the removal or cross of goods or in the refrigerated cabinets or cold rooms - takes place.
  • the cooling demand is often so low during these times that it comes in the compressor unit of the normal cooling circuit to a so-called.
  • Pump-down circuit is the suction of the evaporator of the refrigerated consumer to understand. This has the consequence that on the one hand cooling points with a low cooling demand, the setpoint temperatures no longer reach and on the other the switching frequency of the compressor of the normal cooling circuit is unnecessarily and undesirably high, since the increased switching frequency of these compressors leads to a reduction in their service life.
  • a further advantageous embodiment of the refrigeration system according to the invention is characterized in that the freezing circuit has an at least two-stage compressor unit C3 / C4 / C5 / C6 and the suction side of the normal refrigeration cycle with the or one of the intermediate pressure sides of the freezing circuit is in operative connection. If the compressor stages C1 and C2 of the normal cooling circuit and at least one compressor stage C4 and C6 of the deep-freeze circuit, which is not the first compressor stage C3 and C5, are preceded by suction collecting containers S2 and S4, these are preferably in operative connection with one another.
  • This embodiment of the refrigeration system according to the invention now allows further advantageous procedures, as they can not be realized with the known refrigeration systems or only with a corresponding effort.
  • An operative connection between the suction side of the normal cooling circuit and the or one of the intermediate pressure sides of the freezing circuit or between the suction collecting container the normal cooling circuit and the or one of the intermediate pressure suction collecting the Tiefkühlniklaufes can be realized according to an advantageous embodiment of the refrigeration system according to the invention via at least one connecting line 20.
  • a further embodiment of the refrigeration system according to the invention is characterized in that an oil compensation line 21 connecting the suction collecting container S2 of the normal refrigeration circuit and the intermediate pressure suction collecting container S4 of the freezing circuit is provided.
  • the refrigeration system according to the invention thus offers a plurality of advantages over the known refrigeration systems, in particular with regard to the defrosting of the evaporator and the energy-saving operation. It allows this with a reduced installation effort and thus lower investment costs. As both energy consumption and maintenance are reduced, operating costs also decrease. Furthermore, compliance with the future legal requirements is possible with the defrost method described.
  • the invention could be realized not only in a refrigeration system with an at least two-stage compressor unit of the freezing circuit - as shown in Figure 1 - but also with a single-stage compressor unit.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Defrosting Systems (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)

Claims (18)

  1. Installation frigorifique pour le refroidissement d'au moins un consommateur de froid au moyen d'un circuit de réfrigération normal et pour le refroidissement de plus d'un consommateur de froid au moyen d'un circuit de surgélation, chacun des circuits comportant une unité de compresseur, un seul condenseur étant prévu, et les conduites sous pression des unités de compresseur se rejoignant en amont du condenseur, et les consommateurs de froid du circuit de surgélation étant reliés chacun, au niveau de points de raccordement, à une conduite d'aspiration (10) commune reliée à l'unité de compresseur (C3/C4/C5/C6) du circuit de surgélation, caractérisée en ce que les conduites sous pression (8, 16) des compresseurs (C1/C2/C3/C4/C5/C6) sont reliées à la conduite d'aspiration (10) de l'unité de compresseur (C3/C4/C5/C6), par l'intermédiaire d'une conduite de dégivrage (30) qui est raccordée, entre l'unité de compresseur (C3/C4/C5/C6) du circuit de surgélation et le point de raccordement situé le plus près de celle-ci et menant vers un consommateur de froid (V3), à la conduite d'aspiration (10) de l'unité de compresseur (C3/C4/C5/C6) du circuit de surgélation.
  2. Installation frigorifique selon la revendication 1, caractérisée en ce que la conduite de dégivrage (30) est réalisée de manière à pouvoir être fermée.
  3. Installation frigorifique selon la revendication 1 ou 2, caractérisée en ce que seulement un collecteur (S1) est monté en aval du condenseur (V).
  4. Installation frigorifique selon l'une quelconque des revendications précédentes, caractérisée en ce que seulement une conduite de liquide (2) est disposée entre le condenseur (V) ou le collecteur (S1) et les conduites de liquide (3, 4) du circuit de réfrigération normal et du circuit de surgélation.
  5. Installation frigorifique selon l'une quelconque des revendications précédentes, caractérisée en ce que le dispositif destiné à surrefroidir le réfrigérant dans la conduite de liquide (4) du circuit de surgélation est situé dans l'espace aussi près que possible des consommateurs de froid (V3, V4) du circuit de surgélation.
  6. Installation frigorifique selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une vanne électromagnétique (c') à commande directe, qui est montée parallèlement à la vanne d'expansion (c) correspondante du consommateur de froid (V3, V4), est située en amont d'au moins un des consommateurs de froid (V3, V4) du circuit de surgélation.
  7. Installation frigorifique selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un refroidisseur (E) est monté en amont du condenseur (V).
  8. Installation frigorifique selon la revendication 7, caractérisée en ce que les conduites sous pression (8, 16) des unités de compresseur (C1/C2, C3/C4/C5/C6) se rejoignent en amont du refroidisseur (E).
  9. Installation frigorifique selon l'une quelconque des revendications précédentes, caractérisée en ce que le circuit de surgélation comporte une unité de compresseur (C3/C4/C5/C6) avec au moins deux niveaux et le côté aspiration du circuit de réfrigération normal est en liaison active avec le ou l'un des côtés de pression intermédiaire du circuit de surgélation.
  10. Installation frigorifique selon l'une quelconque des revendications précédentes, caractérisée en ce qu'au moins un niveau de compresseur (C1/C2) du circuit de réfrigération normal et un niveau de compresseur (C4/C6) du circuit de surgélation, sachant qu'il ne s'agit pas du premier niveau de compresseur (C3/C5), sont montés en amont de récipients collecteurs à aspiration (S2, S4) et que ceux-ci sont en liaison active.
  11. Installation frigorifique selon la revendication 9 ou 10, caractérisée en ce que la liaison active est réalisée par au moins une conduite de liaison (20).
  12. Installation frigorifique selon la revendication 11, caractérisée en ce qu'il est prévu une conduite de compensation d'huile (21) reliant le récipient collecteur à aspiration (S2) du circuit de réfrigération normal et le ou l'un des récipients collecteurs à aspiration de pression intermédiaire (S4) du circuit de surgélation.
  13. Installation frigorifique selon la revendication 10, caractérisée en ce que la fonction du récipient collecteur à aspiration (S2) du circuit de réfrigération normal et du récipient collecteur à aspiration de pression intermédiaire (S4) du circuit de surgélation est réalisée dans un récipient collecteur à aspiration.
  14. Procédé de dégivrage d'une installation frigorifique selon l'une quelconque des revendications 1 à 13, dans lequel un réfrigérant chauffé est acheminé hors de l'unité de compresseur (C1/C2) du circuit de réfrigération normal par l'intermédiaire de la conduite de dégivrage (30) vers la conduite d'aspiration (10) de l'unité de compresseur (C3/C4/C5/C6) du circuit de surgélation et par l'intermédiaire de celle-ci vers les consommateurs de froid (V3, V4) du circuit de surgélation.
  15. Procédé selon la revendication 14, dans lequel, pendant le processus de dégivrage, l'acheminement du réfrigérant hors de l'unité de compresseur (C1/C2) du circuit de réfrigération normal vers le condenseur est interrompu et l'unité de compresseur (C3/C4/C5/C6) du circuit de surgélation est déconnectée.
  16. Procédé selon la revendication 14 ou 15, dans lequel le réfrigérant acheminé vers les consommateurs de froid (V3, V4) du circuit de surgélation est acheminé ensuite vers les consommateurs de froid (V1, V2) du circuit de réfrigération normal et est refoulé ensuite vers l'unité de compresseur (C1, C2) du circuit de réfrigération normal, l'unité de compresseur (C1, C2) du circuit de réfrigération normal fonctionnant en tant que pompe à chaleur.
  17. Procédé selon l'une quelconque des revendications 14 à 16, dans lequel une vanne électromagnétique (c') à commande directe, qui est montée parallèlement à la vanne d'expansion correspondante du consommateur de froid, est montée en amont d'au moins un des consommateurs de froid (V3, V4) du circuit de surgélation ou en amont des évaporateurs dudit au moins un consommateur de froid, et dans lequel le réfrigérant, pendant le processus de dégivrage, afflue depuis la conduite d'aspiration (10) dans l'évaporateur dudit au moins un consommateur de froid (V3, V4) et à travers la vanne électromagnétique (c') ouverte.
  18. Procédé selon la revendication 17, dans lequel la vanne électromagnétique (c') est fermée lorsqu'une température finale de dégivrage prédéfinie est atteinte dans l'évaporateur correspondant dudit au moins un consommateur de froid (V3, V4).
EP00109558A 1999-05-05 2000-05-04 Système frigorifique Expired - Lifetime EP1050726B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19920726 1999-05-05
DE19920726A DE19920726A1 (de) 1999-05-05 1999-05-05 Kälteanlage

Publications (3)

Publication Number Publication Date
EP1050726A2 EP1050726A2 (fr) 2000-11-08
EP1050726A3 EP1050726A3 (fr) 2002-08-14
EP1050726B1 true EP1050726B1 (fr) 2007-01-24

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EP00109558A Expired - Lifetime EP1050726B1 (fr) 1999-05-05 2000-05-04 Système frigorifique

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EP (1) EP1050726B1 (fr)
AT (1) ATE352760T1 (fr)
DE (2) DE19920726A1 (fr)
ES (1) ES2278558T3 (fr)
PT (1) PT1050726E (fr)

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DE20115270U1 (de) * 2001-09-15 2001-11-22 Teko Ges Fuer Kaeltetechnik Mb Kühlanlage und zugehörige Schaltungsanordnung
JP3818115B2 (ja) * 2001-10-04 2006-09-06 株式会社デンソー エジェクタサイクル
EP1422487A3 (fr) * 2002-11-21 2008-02-13 York Refrigeration APS Dégivrage par gaz chaud pour installations frigorifiques
DE10332859A1 (de) * 2003-07-18 2005-02-10 Linde Kältetechnik GmbH & Co. KG Heißgasabtauverfahren für Kälteanlagen
GB2405688A (en) * 2003-09-05 2005-03-09 Applied Design & Eng Ltd Refrigerator
DE102004038640A1 (de) 2004-08-09 2006-02-23 Linde Kältetechnik GmbH & Co. KG Kältekreislauf und Verfahen zum Betreiben eines Kältekreislaufes
EP1782001B1 (fr) * 2004-08-09 2016-11-30 Carrier Corporation Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP2496893B1 (fr) * 2009-11-06 2019-01-02 Carrier Corporation Circuit de réfrigération et procédé de dégivrage sélectif d'unités consommatrices de froid d'un circuit de réfrigération
JP5533207B2 (ja) 2010-05-06 2014-06-25 株式会社日本自動車部品総合研究所 ヒートポンプサイクル
CN104534755A (zh) * 2014-12-02 2015-04-22 青岛澳柯玛超低温冷冻设备有限公司 一种具有自动化霜功能的制冷系统
CN106642852A (zh) * 2016-12-30 2017-05-10 中原工学院 一种制冷装置三级复合式快速融霜系统
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EP1050726A3 (fr) 2002-08-14
DE50013996D1 (de) 2007-03-15
ATE352760T1 (de) 2007-02-15
ES2278558T3 (es) 2007-08-16
PT1050726E (pt) 2007-03-30
EP1050726A2 (fr) 2000-11-08
DE19920726A1 (de) 2000-11-09

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