EP1957888B1 - Circuit de refrigeration a deux temperatures - Google Patents

Circuit de refrigeration a deux temperatures Download PDF

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Publication number
EP1957888B1
EP1957888B1 EP05816391A EP05816391A EP1957888B1 EP 1957888 B1 EP1957888 B1 EP 1957888B1 EP 05816391 A EP05816391 A EP 05816391A EP 05816391 A EP05816391 A EP 05816391A EP 1957888 B1 EP1957888 B1 EP 1957888B1
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EP
European Patent Office
Prior art keywords
pressure
medium
compressor
refrigerant
temperature refrigeration
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.)
Not-in-force
Application number
EP05816391A
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German (de)
English (en)
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EP1957888A1 (fr
Inventor
Neelkanth S. Gupte
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Carrier Corp
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Carrier Corp
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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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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

Definitions

  • the present invention relates to a combined medium and low temperature refrigeration circuit and particularly to a respective CO 2 refrigeration circuit and a corresponding method.
  • Such dual temperature refrigeration circuits are known to circulate a refrigerant in a predetermined flow direction through a heat-rejecting heat exchanger, a medium temperature refrigeration consumer, a low temperature refrigeration consumer and a compressor unit which returns the refrigerant pressure to the high pressure present in the heat rejecting heat exchanger.
  • the medium and low temperature refrigeration consumers are arranged in parallel in the circuit, i.e. the refrigerant leaving the heat-rejecting heat exchanger is branched so that part thereof flows through the medium temperature refrigeration consumer and the remainder through the low temperature refrigeration consumer.
  • the compressor unit generally is a two stage compressor unit with a low pressure compressor set and a medium pressure compressor set with the low pressure compressor set being connected to the exit of the low temperature refrigeration consumer and compresses the refrigerant leaving the same up to a pressure level which corresponds to the pressure level present at the outlet of the medium temperature refrigeration consumer.
  • Both the refrigerant leaving the outlet of the medium temperature refrigeration consumer as well as the refrigerant leaving the outlet of the low pressure compressor are directed to the inlet of the medium pressure compressor which compresses the refrigerant up to the required high pressure as present in the heat rejecting heat exchanger. While such dual temperature refrigeration circuit is satisfying the refrigeration needs, there still is a requirement for improving the efficiency.
  • EP 0 485 146 A discloses a combined medium and low temperature refrigeration circuit and a corresponding operation method according to the preamble of claims 1 and 11.
  • the refrigeration circuit comprises a medium pressure expansion device and an intermediate pressure vapor separator with the medium pressure expansion device connected to the liquid portion of the medium pressure vapor separator, the liquid portion of the intermediate pressure vapor separator connected to the low temperature refrigeration consumer, and the vapor portion of the intermediate pressure vapor separator being connected to the compressor unit.
  • Such additional medium pressure expansion device and a joint intermediate pressure vapor separator may further reduce the temperature and the pressure of the refrigerant before it will finally be directed to the low temperature refrigeration consumer and the dimensions of the low temperature refrigeration consumer can further be reduced. It is to be noted that together with the reduction of the dimension of the respective refrigeration consumer, the temperature and pressure reduction as provided through the vapor-liquid separation also allows substantially smaller dimensions for the conduits leading towards the respective refrigeration consumer.
  • the medium and low temperature refrigeration consumers are arranged in line so that the refrigerant will initially be used in the medium temperature refrigeration consumer and subsequently the remaining liquid portion of the refrigerant will be used in the low temperature refrigeration consumer.
  • the medium temperature refrigeration consumer may be arranged and/or operated so that the exiting refrigerant is a two-phase refrigerant with part thereof being liquid and the remainder gaseous. Such two-phase refrigerant is separated in the medium pressure vapor separator with the gaseous portion thereof being compressed and returned to the heat rejecting heat exchanger and the liquid portion thereof being used for the low temperature refrigeration consumer.
  • the serial arrangement directs substantially cooler liquid refrigerant but with a reduced pressure towards the low temperature refrigeration consumer.
  • the refrigerant leaving the low temperature refrigeration consumer will be compressed in the compressor unit either directly to the pressure level as required for the heat rejecting heat exchanger or in a first stage up to an intermediate pressure level, for example the pressure level of the gaseous medium pressure refrigerant, and in a second step up to the pressure level as present in the heat rejecting heat exchanger.
  • the compressor unit may comprise a plurality of individual compressors, it may also comprise one or two compressor sets, for example a low pressure compressor set and a medium pressure compressor set. Each of the low and medium compressor sets may also comprise one or a plurality of individual compressors.
  • the refrigeration circuit may further comprise a high pressure vapour separator having a vapor portion and a liquid portion, which is arranged between the heat rejecting heat exchanger and the medium temperature refrigeration consumer, and having its vapor portion connected to the inlet of the compressor unit and its liquid portion connected to the medium temperature refrigeration consumer.
  • a high pressure vapour separator having a vapor portion and a liquid portion, which is arranged between the heat rejecting heat exchanger and the medium temperature refrigeration consumer, and having its vapor portion connected to the inlet of the compressor unit and its liquid portion connected to the medium temperature refrigeration consumer.
  • the high pressure vapor separator also allows to reduce the temperature and pressure in advance of the medium temperature refrigeration consumer. This increases the efficiency of the medium temperature refrigeration consumer and allows smaller dimensions thereof.
  • the refrigeration circuit may further comprise an intermediate expansion device between the heat rejecting heat exchanger and the high temperature vapor separator.
  • an intermediate expansion device By means of the intermediate expansion device, a two-phase refrigerant can be generated even if the refrigerant leaving the heat rejecting heat exchanger is purely gaseous.
  • the expansion device can be a controllable expansion device in order to control the conditions in the high pressure vapor separator, like temperature, pressure, proportion of the liquid to gaseous refrigerant, etc.
  • the refrigeration circuit may further comprise a pressure regulated valve in a line between the vapor portion of the high pressure vapor separator and a compressor unit.
  • a pressure regulated valve in a line between the vapor portion of the high pressure vapor separator and a compressor unit.
  • the proportion between the gaseous and liquid refrigerant in the high pressure vapor separator can be controlled by means of such pressure regulated valve.
  • Another type of controllable valve may also be provided for. It is possible to connect this controllable valve as well as any other controllable element in the circuit to an individual control or alternatively to the overall control of the circuit.
  • a refrigeration consumer may comprise at least one expansion device and at least one evaporator.
  • the expansion device can be a controllable expansion device for controlling the condition in the evaporator and particularly the condition of the refrigerant at the outlet of the evaporator.
  • the velocity of the refrigerant flow through the evaporator can be controlled so that the refrigerant at the outlet can have any condition between two-phase refrigerant and super heated refrigerant.
  • the refrigeration performance and thus the temperature next to the refrigeration consumer can be controlled thereby.
  • the compressor unit may comprise a low pressure compressor set, a medium pressure compressor set and a high pressure vapor compressor.
  • the low pressure compressor set can be connected to the low temperature refrigeration consumer
  • the medium pressure compressor set can be connected to the liquid portion of the medium pressure vapor separator
  • the high pressure vapor compressor can be connected to the vapor portion of the high pressure vapor separator.
  • the low pressure compressor set and the medium pressure compressor set can form a two stage compressor with the outlet of the low pressure compressor set being connected in the inlet of the high pressure compressor set.
  • the high pressure compressor set compresses gaseous refrigerant from the medium pressure to the high pressure as present in the heat rejecting heat exchanger, the pressure difference over the high pressure vapor compressor will typically be substantially less.
  • the high pressure vapor compressor can be a controllable compressor.
  • the compressor unit may further comprise an intermediate compressor between the vapor portion of the intermediate pressure vapor separator and the medium pressure compressor set. Similar to the high pressure vapor compressor, the intermediate compressor is compressing only over a reduced pressure difference as compared to the low pressure compressor set. This applies particularly, if the intermediate compressor operates merely between the intermediate pressure and the medium pressure levels. Again, a plurality of intermediate compressors can be provided. It is possible to use a controllable intermediate compressor.
  • the refrigeration circuit may further comprise a pressure regulating valve between the vapor portion of the intermediate pressure vapor separator and the compressor unit and the intermediate compressor, respectively.
  • the refrigeration circuit may further comprise a superheat sensor associated to the exit of the low temperature refrigeration consumer and connected to a control for securing superheat of the refrigerant.
  • Control can be a local superheat control which controls the refrigeration consumer's expansion valve, etc. but can also be the general refrigeration circuit control.
  • the refrigeration circuit may use a refrigerant which is working also in a super critical condition, for example CO 2 .
  • the refrigeration apparatus can be a refrigeration system for a supermarket, and industrial refrigeration system, etc.
  • the medium temperature refrigeration consumer(s) can be display cabinet and the likes, for example for milk products, meat, vegetables and fruits, with a medium refrigeration level of less than 10°C down to around 0°C.
  • the low temperature refrigeration consumer(s) can be freezers with a refrigeration level of - 20°C and below.
  • Another embodiment of the present invention relates to a method for operating a combined medium and low temperature refrigeration circuit according to claim 11.
  • the method may further comprise the following steps:
  • the method may further comprise in advance of step (d) the step of expanding the high pressure refrigerant leaving the heat rejecting heat exchanger and preferably regulating the pressure of the gaseous high pressure refrigerant.
  • the method may further comprise the following step:
  • Fig. 1 shows a combined medium and low temperature refrigeration circuit 2 for circulating a refrigerant in a predetermined flow direction as indicated by the arrows, comprising in flow direction a heat rejecting heat exchanger 4, a plurality of medium temperature refrigeration consumers 6, a medium pressure vapor separator 8 having a vapor portion 10 and a liquid portion 12, a plurality of low temperature refrigeration consumers 14 as well as a compressor unit 16.
  • the compressor unit 16 comprises a plurality of individual compressors 18 some of which are grouped together to compressor sets, like a low pressure 2-stage compressor set comprising a first stage low pressure compressor set 20 and a second stage low pressure compressor set 22.
  • the compressors and compressor sets may all be located at the same location, but may also be located at different places within the circuit 2.
  • the outlets 28 and 30 of the second stage low pressure compressor set 22 and the medium pressure compressor set 24 are connected with the inlet 32 of the heat rejecting heat exchanger 4.
  • the heat rejecting heat exchanger 4 can be a conventional condenser in case of a conventional refrigerant and can be a gascooler in case of a refrigerant which is at least partially operated in a supercritical condition.
  • a high pressure vapor separator 34 having a vapor portion 36 and a liquid portion 38 is provided between the heat rejecting heat exchanger 4 and the medium temperature refrigeration consumers 6.
  • the vapor portion 36 of the high pressure vapor separator 34 is connected with the outlet 40 of the heat rejecting heat exchanger 4 via heat exchanger outlet line 42.
  • An expansion device 44 is located in the heat exchanger outlet line 42.
  • the liquid portion 38 of the high pressure vapor separator 34 is connected to the medium temperature refrigeration consumers 6 by means of a high pressure liquid line 46.
  • the vapor portion 36 of the high pressure vapor separator 34 is connected by means of the high pressure vapor line 48 to a high pressure vapor compressor 50.
  • a pressure regulated valve 52 is arranged in the high pressure vapor line 58.
  • Each of the medium and low temperature refrigeration consumers 6 and 14, respectively may comprise at least one expansion device 54 and 56, respectively, and at least one evaporator 58 and 60, respectively.
  • the compressor unit 16 comprises a plurality of compressor sets 20, 22 and 24 as well as individual compressors 18, 50.
  • the compressor unit 16 comprises a plurality of inlets at different pressure levels with the inlets 62 to the first stage compressor set 20 of the low pressure compressor set 20, 22 being at the lower most pressure level, the inlet 26 to the medium pressure compressor set 24 being at a higher medium pressure level and the inlet 64 to the high pressure vapor com pressor 50 being as compared therewith at the highest level.
  • the pressure of the refrigerant in the heat rejecting heat exchanger 4 can be up to 120 bar and is typically approximately 85 bar in "summer mode” and approximately 45 bar in "winter mode”.
  • the refrigerant flowing through the heat exchanger outlet line 42 is expanded in expansion valve 44 which reduces the pressure to between approximately 30 and 40 bar and preferably 36 bar with such pressure being typically independent from a "winter mode" and "summer mode”.
  • the high pressure receiver or high pressure vapor separator 34 collects and separates liquid and gaseous refrigerant in the liquid and vapor portions 38 and 36, respectively.
  • the high pressure liquid line 46 directs the liquid refrigerant from the liquid portion 38 to the expansion devices 54 of the medium temperature refrigeration consumers 6.
  • the medium temperature refrigeration consumers 6 cool down to approximately 1 to 10°C. They can be arranged or controlled so that there is a two-phase refrigerant present at the outlet thereof. Such two-phase refrigerant is fed to the medium pressure vapor separator 8 where it is collected and separated in a vapor portion 10 and liquid portion 12, respectively. Gaseous refrigerant from the vapor portion 10 is directed to the inlet 26 of the medium pressure compressor 24.
  • the input pressure is typically between 20 and 30 bar and approximately 26 bar, which results in a temperature of the refrigerant of approximately -10°C in the medium temperature refrigeration consumers 6.
  • a high pressure line 66 returns the compressed, hot, gaseous refrigerant to the heat rejecting heat exchange 4.
  • gaseous refrigerant from the vapor portion 36 of the hight pressure vapor separator 34 is directed through high pressure vapor line 48 and pressure controlled valve 52 to the inlet 64 of the high pressure vapor compressor 50 and returned to high pressure line 66 to the heat rejecting heat exchanger 4.
  • the liquid refrigerant from the liquid portion 12 of the medium temperature vapor separator 8 is directed to and through the low temperature refrigeration consumers 14.
  • the low temperature refrigeration consumers 14 are arranged or controlled so as to provide super heated gaseous refrigerant only to the inlet 68 of the first stage low temperature compressor set 20.
  • a superheat sensor (not shown) can be associated to the exit of the low temperature refrigeration consumers 14 or the inlet 68 to the first stage low temperature compressor set 20 in order to ensure that no liquid refrigerant may enter the first stage low temperature compressor set 20.
  • an internal heat exchanger (not shown) can be provided for between the low temperature refrigeration consumers 14 and the inlet 68.
  • the pressure at the inlet 68 is typically between 8 and 20 bar and preferably approximately 12 bar which results in a temperature of the refrigerant of approximately -37°C in the low temperature refrigeration consumers 14.
  • gaseous refrigerant is returned through the low pressure compressor 26 and 22, respectively and the high pressure line 66 to the heat rejecting heat exchanger 4.
  • Fig. 2 corresponds substantially to the embodiment of fig. 1 . Accordingly, corresponding elements are indicated with corresponding reference numbers.
  • the main difference between the two embodiments results in a different routing of the liquid refrigerant leaving the liquid portion 12 of the medium temperature vapor separator 8 as compared to Fig. 1 .
  • a medium pressure expansion device 70 and an intermediate pressure vapor separator 72 having a vapor portion 74 and a liquid portion 76 are additionally arranged subsequent to the medium temperature vapor separator 8.
  • a pressure regulated intermediate valve 78 as well as an intermediate compressor 80 connect the vapor portion 74 of the intermediate pressure vapor separator 72 to the intermediate pressure level between first stage low pressure compressor set 20 and second stage low pressure compressor set 22.
  • the intermediate compressor 80 can be a single compressor or a plurality of compressors and may further be a controllable compressor.
  • the pressure difference over intermediate compressor 80 is substantially less than the pressure difference over the first stage low pressure compressor set 20.
  • the pressures and temperatures are by and large the same as with the embodiment of Fig. 1 and for the intermediate vapor separator 72 the saturation temperature is approximately half way between the low temperature and medium temperature evaporator temperatures.
  • the pressure regulated valves 52 and 78 allow to hold or control the back pressure feeding into the expansion valves for the medium and low temperature cases.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Chemical & Material Sciences (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Central Heating Systems (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air-Conditioning For Vehicles (AREA)

Claims (15)

  1. Circuit de réfrigération combiné basse et moyenne température (2) pour faire circuler un fluide frigorigène dans un sens d'écoulement prédéterminé,
    comprenant dans le sens d'écoulement
    (a) un échangeur de chaleur rejetant de la chaleur (4) ;
    (b) un élément de consommation de réfrigération moyenne température (6) ;
    (c) un séparateur de vapeur à pression moyenne (8) présentant une partie de vapeur (10) et une partie de liquide (12), le séparateur de vapeur à pression moyenne (8) étant raccordé à l'élément de consommation de réfrigération moyenne température (6) ;
    (d) un élément de consommation de réfrigération basse température (14) ; et
    (e) une unité de compression (16) comportant une entrée raccordée à la partie de vapeur (10) du séparateur de vapeur à pression moyenne (8) et à l'élément de consommation de réfrigération basse température (14),
    caractérisé en ce qu'il comprend en outre un dispositif de dilatation à pression moyenne (70) et un séparateur de vapeur à pression intermédiaire (72), le dispositif de dilatation à pression moyenne (70) étant raccordé à la partie de liquide (12) du séparateur de vapeur à pression moyenne (8), la partie de liquide (76) du séparateur de vapeur à pression intermédiaire (72) étant raccordée à l'élément de consommation de réfrigération basse température (14), et la partie de vapeur (74) du séparateur de vapeur à pression intermédiaire (72) étant raccordée à l'unité de compression (16).
  2. Circuit de réfrigération (2) selon la revendication 1, comprenant en outre un séparateur de vapeur haute pression (34) présentant une partie de vapeur (36) et une partie de liquide (38), entre l'échangeur de chaleur rejetant de la chaleur (4) et l'élément de consommation de réfrigération moyenne température (6), sa partie de vapeur (36) étant raccordée à l'entrée de l'unité de compression (16) et sa partie de liquide (38) à l'élément de consommation de réfrigération moyenne température (6).
  3. Circuit de réfrigération (2) selon la revendication 2, comprenant en outre un dispositif de dilatation (44) entre l'échangeur de chaleur rejetant de la chaleur (4) et le séparateur de vapeur haute température (34).
  4. Circuit de réfrigération (2) selon la revendication 2 ou 3, comprenant en outre une valve régulée par pression (52) sur une ligne (48) entre la partie de vapeur (36) du séparateur de vapeur haute pression (34) et l'unité de compression (16).
  5. Circuit de réfrigération (2) selon l'une quelconque des revendications 1 à 4, dans lequel un élément de consommation de réfrigération (6 ; 14) comprend au moins un dispositif de dilatation (54 ; 56) et au moins un évaporateur (58 ; 60).
  6. Circuit de réfrigération (2) selon l'une quelconque des revendications 1 à 5, dans lequel l'unité de compression (16) comprend un ensemble compresseur basse pression (20, 22), un ensemble compresseur moyenne pression (24) et un compresseur de vapeur haute pression (50), l'ensemble compresseur basse pression étant raccordé à l'élément de consommation de réfrigération basse température (14), l'ensemble compresseur moyenne pression (24) étant raccordé à la partie de vapeur du séparateur de vapeur à pression moyenne (8), et le compresseur de vapeur haute pression (50) étant raccordé à la partie de vapeur (36) du séparateur de vapeur à haute pression (34).
  7. Circuit de réfrigération (2) selon la revendication 1, dans lequel l'unité de compression (16) comprend en outre un compresseur intermédiaire (80) entre la partie de vapeur (36) du séparateur de vapeur à pression intermédiaire (72) et l'ensemble compresseur moyenne pression (24).
  8. Circuit de réfrigération (2) selon la revendication 1 ou 7, comprenant en outre une valve de régulation de pression (78) entre la partie de vapeur (74) du séparateur de vapeur à pression intermédiaire (72) et l'unité de compression (16).
  9. Circuit de réfrigération (2) selon l'une quelconque des revendications 1 à 8, comprenant en outre un capteur de surchauffe associé à la sortie de l'élément de consommation de réfrigération basse température (14) et raccordé à une commande de sécurisation de surchauffe du fluide frigorigène.
  10. Circuit de réfrigération (2) selon l'une quelconque des revendications 1 à 9, dans lequel le fluide frigorigène est le CO2.
  11. Procédé d'actionnement d'un circuit de réfrigération moyenne et basse température (2) pour faire circuler un fluide frigorigène dans un sens d'écoulement prédéterminé, le circuit de réfrigération (2) comprenant dans le sens d'écoulement un échangeur de chaleur rejetant de la chaleur (4), un élément de consommation de réfrigération moyenne température (6), un élément de consommation de réfrigération basse température (14) et une unité de compression (16), chacun d'entre eux comportant une entrée et une sortie, respectivement, le procédé comprenant les étapes suivantes :
    (a) séparer le fluide frigorigène moyenne pression liquide quittant la sortie de l'élément de consommation de réfrigération moyenne température (6) du fluide frigorigène gazeux quittant la même sortie ;
    (b) diriger le fluide frigorigène moyenne pression gazeux vers l'entrée de l'unité de compression (16) ; caractérisé en ce qu'il comprend en outre les étapes suivantes :
    (c) dilater le fluide frigorigène moyenne pression liquide à une pression intermédiaire ;
    (d) séparer le fluide frigorigène à pression intermédiaire liquide du fluide frigorigène à pression intermédiaire gazeux ;
    (e) diriger le fluide frigorigène à pression intermédiaire gazeux vers l'entrée de l'unité de compression (16) ; et
    (f) diriger le fluide frigorigène à pression intermédiaire gazeux liquide vers l'élément de consommation de réfrigération basse température (14).
  12. Procédé selon la revendication 11, comprenant en outre les étapes suivantes :
    b') séparer le fluide frigorigène haute pression liquide quittant la sortie de l'échangeur de chaleur rejetant de la chaleur (4) du fluide frigorigène gazeux quittant la même sortie ;
    b') diriger le fluide frigorigène haute pression gazeux vers l'entrée de l'unité de compression (16) ; et
    b''') diriger le fluide frigorigène haute pression liquide vers l'entrée de l'élément de consommation de réfrigération moyenne température (6).
  13. Procédé selon la revendication 12, comprenant en outre avant l'étape (b') l'étape consistant à dilater le fluide frigorigène haute pression quittant l'échangeur de chaleur rejetant de la chaleur (4).
  14. Procédé selon l'une quelconque des revendications 11 à 13, comprenant en outre l'étape suivante
    (g) réguler la surchauffe du fluide frigorigène basse pression gazeux entrant dans l'entrée de l'unité de compression (16).
  15. Procédé selon l'une quelconque des revendications 11 à 14, dans lequel l'unité de compression (16) comprend un ensemble compresseur basse pression (20, 22), un ensemble compresseur moyenne pression (24), un compresseur à vapeur haute pression (50) et un compresseur intermédiaire (80) et dans lequel le fluide frigorigène gazeux quittant l'élément de consommation de réfrigération basse température (14) est dirigé vers l'ensemble compresseur basse pression (20, 22), le fluide frigorigène moyenne pression gazeux est dirigé vers l'ensemble compresseur moyenne pression (24), le fluide frigorigène haute pression gazeux est dirigé vers le compresseur à vapeur haute pression (50) et le fluide frigorigène à pression intermédiaire gazeux est dirigé vers le compresseur intermédiaire (80).
EP05816391A 2005-11-04 2005-11-04 Circuit de refrigeration a deux temperatures Not-in-force EP1957888B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2005/040047 WO2007053149A1 (fr) 2005-11-04 2005-11-04 Circuit de refrigeration a deux temperatures

Publications (2)

Publication Number Publication Date
EP1957888A1 EP1957888A1 (fr) 2008-08-20
EP1957888B1 true EP1957888B1 (fr) 2009-08-12

Family

ID=36590237

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05816391A Not-in-force EP1957888B1 (fr) 2005-11-04 2005-11-04 Circuit de refrigeration a deux temperatures

Country Status (8)

Country Link
US (1) US20080307805A1 (fr)
EP (1) EP1957888B1 (fr)
CN (1) CN101351675B (fr)
AT (1) ATE439559T1 (fr)
DE (1) DE602005016028D1 (fr)
ES (1) ES2330128T3 (fr)
TW (1) TW200732610A (fr)
WO (1) WO2007053149A1 (fr)

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US11215386B2 (en) 2016-03-31 2022-01-04 Carrier Corporation Refrigeration circuit

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WO2012095186A1 (fr) * 2011-01-14 2012-07-19 Carrier Corporation Système de réfrigération et procédé de fonctionnement d'un système de réfrigération
ITTV20120010A1 (it) * 2012-01-19 2013-07-20 Enex Srl Sistema frigorifero di tipo booster con refrigerante r744.
EP2729742B1 (fr) * 2011-07-05 2020-09-02 Carrier Corporation Circuit de réfrigération et système de chauffage et de refroidissement
MX350051B (es) * 2012-05-11 2017-08-23 Hill Phoenix Inc Sistema de refrigeración de dióxido de carbono con módulo de aire acondicionado integrado.
US9625183B2 (en) * 2013-01-25 2017-04-18 Emerson Climate Technologies Retail Solutions, Inc. System and method for control of a transcritical refrigeration system
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US10808966B2 (en) * 2017-03-02 2020-10-20 Heatcraft Refrigeration Products Llc Cooling system with parallel compression
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Also Published As

Publication number Publication date
CN101351675A (zh) 2009-01-21
CN101351675B (zh) 2010-05-26
ATE439559T1 (de) 2009-08-15
DE602005016028D1 (de) 2009-09-24
EP1957888A1 (fr) 2008-08-20
US20080307805A1 (en) 2008-12-18
TW200732610A (en) 2007-09-01
WO2007053149A1 (fr) 2007-05-10
ES2330128T3 (es) 2009-12-04

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