EP1895246A2 - 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
EP1895246A2
EP1895246A2 EP07020311A EP07020311A EP1895246A2 EP 1895246 A2 EP1895246 A2 EP 1895246A2 EP 07020311 A EP07020311 A EP 07020311A EP 07020311 A EP07020311 A EP 07020311A EP 1895246 A2 EP1895246 A2 EP 1895246A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
collecting container
compressor unit
refrigeration circuit
circuit according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07020311A
Other languages
German (de)
English (en)
Other versions
EP1895246A3 (fr
EP1895246B3 (fr
EP1895246B1 (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 Corp
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
Application filed by Linde Kaeltetechnik GmbH filed Critical Linde Kaeltetechnik GmbH
Publication of EP1895246A2 publication Critical patent/EP1895246A2/fr
Publication of EP1895246A3 publication Critical patent/EP1895246A3/fr
Application granted granted Critical
Publication of EP1895246B1 publication Critical patent/EP1895246B1/fr
Publication of EP1895246B3 publication Critical patent/EP1895246B3/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • 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
    • 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—Component parts or details not otherwise provided for in this subclass
    • 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—Component parts or details not otherwise provided for in this subclass
    • 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—Component parts or details not otherwise provided for in this subclass
    • 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—Component parts or details not otherwise provided for in this subclass
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/198—Intermediate pressures
    • 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 variety of refrigerants, such as refrigerators, refrigerators and freezers. For this purpose circulates in them a one- or multi-component refrigerant or refrigerant mixture.
  • the circulating in the refrigeration cycle one- or multi-component refrigerant is in a condenser or gas cooler A - hereinafter referred to only as a condenser - which is usually outside the supermarket, for example, on the roof, arranged 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 consumers F and F ' shown in the figure 1 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 on.
  • the compressed in the compressor unit H refrigerant is then fed via the pressure line 1 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 supplied via the line G' of the compressor unit H.
  • the liquefied in the condenser K refrigerant of the freezing circuit is supplied via line L to the collector M of the freezing circuit.
  • the refrigerant to the consumer P - this is for any number of consumers -, which is preceded by a relaxation device O, supplied and evaporated in this.
  • the suction line Q the vaporized refrigerant is fed to the single-stage or multi-stage compressor unit R, in this pressure compressed between 25 and 40 bar and then fed via the pressure line S to the aforementioned capacitor K.
  • R 404A As a refrigerant of the normal refrigeration cycle, for example, R 404A is used, while for the freezing cycle carbon dioxide is used.
  • the compressor units H and R shown in Figure 1, the collector C and M and the capacitor K are usually arranged in a separate machine room. However, 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. As long as this line network operates at pressures of no more than 35 to 40 bar, this is acceptable to the supermarket operators both from a psychological point of view and for cost reasons.
  • Object of the present invention is to provide a generic refrigeration cycle and a method for operating a refrigeration cycle, which avoids the disadvantages mentioned.
  • a refrigeration cycle which is characterized in that between the condenser and the collecting container, an intermediate-expansion device is arranged.
  • HFC (s) HFC (s) or CO 2
  • 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. This connection between the pressure line 7 and the line 2 or 2 ', 2 ", for example, via the dashed lines connecting line 18, in which a valve j is arranged, take place.
  • This connection between the collecting container 3 and the input of the compressor unit 6 can take place, for example, via a connecting line 12, which, as shown in FIG. 2, opens into the suction line 11.
  • the selected intermediate pressure can now be kept constant for all operating conditions.
  • a scheme such that a constant difference value to the suction pressure exists. This ensures that the throttle steam fraction at the evaporators is comparatively small, with the result that the liquid and suction lines can be dimensioned correspondingly smaller.
  • This also applies to the condensate line, since now no gaseous components have to flow through them back into the condenser 1.
  • a portion of the withdrawn from the collector 3 via line 4 refrigerant is fed via line 8 one or more frozen consumers - represented by the heat exchanger E4-, which is also preceded by a relaxation valve d supplied.
  • this partial refrigerant flow is fed via the suction line 9 to the compressor unit 10 and compressed therein to the inlet pressure of the compressor unit 6.
  • the thus compressed refrigerant partial stream is then fed via line 11 to the input side of the compressor unit 6.
  • a heat exchanger E1 can be arranged upstream of the collecting container 3.
  • 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 desuperheated refrigerant can now be withdrawn from the condenser or gas cooler 1 or the line 2 via line 13, in which an expansion valve f is provided, and withdrawn from the line in the heat exchanger E1 rechargeable, the heat exchanger E1 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 Shown in FIG. 3 is 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 withdrawn 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 line 4 shown in FIGS. 2 and 3, with a temperature level below the ambient temperature are exposed to heat radiation. This has the consequence that the refrigerant flowing inside the liquid line partially evaporates, thus resulting in the formation of undesirable vapor contents. To prevent this, refrigerant so far either by an expansion of a partial flow of the refrigerant and subsequent evaporation or by an internal heat transfer against a suction gas stream, which is thereby overheated, subcooled.
  • the temperature interval between the suction and liquid line or the circulating refrigerant therein may be too low to realize an internal heat transfer for the required supercooling of the refrigerant flowing in the liquid line.
  • the invention further developing is therefore - as already mentioned - proposed to cool the withdrawn from the sump 3 via line 4 refrigerant in the heat exchanger and subcooler E5 against the relaxed from the sump 3 via line 12 and in the valve e flash gas.
  • the expanded refrigerant which has been overheated in the heat exchanger E5 is fed via the line sections 12 'and 11 to the inlet of the compressor unit 6.
  • the procedure described thus has the additional advantage that the reliability of the compressor or compressor unit 6 is increased due to a safe overheating of the flash gas stream.
  • FIGS. 4 and 5 show two further, mutually alternative embodiments of the refrigeration cycle of the invention and the inventive method for operating a refrigeration cycle. For the sake of clarity, only sections of the refrigeration cycle according to the invention shown in FIGS. 2 and 3 are shown in FIGS. 4 and 5.
  • 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 overheated in this against the compressed in the compressor unit 6 refrigerant.
  • the flash gas stream to be overheated is overheated in the heat exchanger E6 against the entire refrigerant stream compressed in the compressor unit 6, which is supplied via line 7 to the condenser or desuperheater (not shown in FIG. 4).
  • 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.
  • FIG. 5 Shown in FIG. 5 is a procedure in which the flash gas stream withdrawn from the collecting container 3 via the line 12, the opened valve g and the line 16 is overheated in the heat exchanger E7 against the compressed refrigerant flow in the line 7.
  • the flash gas stream after passing through the heat exchanger E7, may be supplied to the compressor unit 6 in the form that one or more cylinders of the multi-cylinder compressors scavenge the flash gas at a higher pressure level.
  • the valves x, y, and z can be provided

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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)
  • Transmitters (AREA)
  • Details Of Measuring And Other Instruments (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
EP07020311.2A 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique Expired - Lifetime EP1895246B3 (fr)

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
EP05775838A EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP05775838A Division EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique

Publications (4)

Publication Number Publication Date
EP1895246A2 true EP1895246A2 (fr) 2008-03-05
EP1895246A3 EP1895246A3 (fr) 2009-02-11
EP1895246B1 EP1895246B1 (fr) 2016-11-23
EP1895246B3 EP1895246B3 (fr) 2018-05-02

Family

ID=34961069

Family Applications (6)

Application Number Title Priority Date Filing Date
EP05715407.2A Expired - Lifetime EP1782001B1 (fr) 2004-08-09 2005-02-18 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP05723393A Expired - Lifetime EP1794510B1 (fr) 2004-08-09 2005-02-18 Circuit de réfrigération à co2 avec sous-refroidissement de l'agent réfrigérant liquide contre la vapeur instantanée de la bouteille accumulatrice et méthode pour exploiter celui-ci
EP07020311.2A Expired - Lifetime EP1895246B3 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique
EP10167202.0A Expired - Lifetime EP2244040B1 (fr) 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP10181303.8A Expired - Lifetime EP2264385B1 (fr) 2004-08-09 2005-07-29 Cycle frigorifique et procédé d'operation d'un cycle frigorifique
EP05775838A Expired - Lifetime EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique

Family Applications Before (2)

Application Number Title Priority Date Filing Date
EP05715407.2A Expired - Lifetime EP1782001B1 (fr) 2004-08-09 2005-02-18 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP05723393A Expired - Lifetime 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

Family Applications After (3)

Application Number Title Priority Date Filing Date
EP10167202.0A Expired - Lifetime EP2244040B1 (fr) 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP10181303.8A Expired - Lifetime EP2264385B1 (fr) 2004-08-09 2005-07-29 Cycle frigorifique et procédé d'operation d'un cycle frigorifique
EP05775838A Expired - Lifetime EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique

Country Status (10)

Country Link
US (2) US7644593B2 (fr)
EP (6) EP1782001B1 (fr)
KR (2) KR20070050046A (fr)
CN (3) CN100507402C (fr)
AT (1) ATE544992T1 (fr)
AU (2) AU2005278162A1 (fr)
DK (5) DK1794510T3 (fr)
NO (1) NO343330B1 (fr)
RU (1) RU2362096C2 (fr)
WO (1) WO2006022829A1 (fr)

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Publication number Priority date Publication date Assignee Title
US20080196420A1 (en) * 2004-08-09 2008-08-21 Andreas Gernemann Flashgas Removal From a Receiver in a Refrigeration Circuit
DK2008039T3 (da) 2006-03-27 2017-01-02 Carrier Corp Kølesystem med parallelle flertrins-economizer-kredsløb med udledning til en hovedkompressors mellemtrinstryk
US8418482B2 (en) * 2006-03-27 2013-04-16 Carrier Corporation Refrigerating system with parallel staged economizer circuits using multistage compression
EP2005079B1 (fr) * 2006-03-27 2016-12-07 Carrier Corporation Système de réfrigération avec circuits d'économiseur étagés en parallèle et compresseur principal à un ou deux étages
JP5028481B2 (ja) * 2006-06-01 2012-09-19 キャリア コーポレイション 冷凍システム用の多段圧縮機ユニット
EP2021705B1 (fr) * 2006-06-01 2013-03-20 Carrier Corporation Système et procédé pour un ajustement commandé de soupape de détente
WO2008019689A2 (fr) * 2006-08-18 2008-02-21 Knudsen Køling A/S Système de réfrigération transcritique doté d'un surpresseur
DE102006050232B9 (de) * 2006-10-17 2008-09-18 Bitzer Kühlmaschinenbau Gmbh Kälteanlage
US20080289350A1 (en) * 2006-11-13 2008-11-27 Hussmann Corporation Two stage transcritical refrigeration system
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AU2005270472B2 (en) 2011-01-06
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AU2005270472A1 (en) 2006-02-16
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RU2007107807A (ru) 2008-09-20
CN100582603C (zh) 2010-01-20
CN100507402C (zh) 2009-07-01
EP1789732B1 (fr) 2011-03-23
US20080078203A1 (en) 2008-04-03
US7644593B2 (en) 2010-01-12
CN101713596A (zh) 2010-05-26
NO343330B1 (no) 2019-02-04
DK2264385T3 (en) 2018-07-23
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DK1794510T3 (da) 2012-05-21
DK1895246T3 (da) 2017-03-06
CN101713596B (zh) 2012-08-08
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KR20070046847A (ko) 2007-05-03
DK2244040T3 (da) 2019-12-02
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DK1782001T3 (en) 2017-03-13
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US8113008B2 (en) 2012-02-14
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