EP3995758B1 - Wärmeaustauscheinheit für ein kühlgerät mit einem wärmespeicher und verwendung von co2 als kältemittel - Google Patents

Wärmeaustauscheinheit für ein kühlgerät mit einem wärmespeicher und verwendung von co2 als kältemittel Download PDF

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Publication number
EP3995758B1
EP3995758B1 EP20205893.9A EP20205893A EP3995758B1 EP 3995758 B1 EP3995758 B1 EP 3995758B1 EP 20205893 A EP20205893 A EP 20205893A EP 3995758 B1 EP3995758 B1 EP 3995758B1
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EP
European Patent Office
Prior art keywords
heat exchange
exchange unit
refrigerant
thermal storage
compressor
Prior art date
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EP20205893.9A
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English (en)
French (fr)
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EP3995758A1 (de
Inventor
Takahiro Yamaguchi
Stefan VANDAELE
Kris Van de Velde
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Daikin Europe NV
Daikin Industries Ltd
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Daikin Europe NV
Daikin Industries Ltd
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Publication date
Application filed by Daikin Europe NV, Daikin Industries Ltd filed Critical Daikin Europe NV
Priority to EP20205893.9A priority Critical patent/EP3995758B1/de
Priority to JP2023524921A priority patent/JP2023546495A/ja
Priority to US18/032,961 priority patent/US20230392829A1/en
Priority to PCT/JP2021/040591 priority patent/WO2022097680A1/en
Publication of EP3995758A1 publication Critical patent/EP3995758A1/de
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Publication of EP3995758B1 publication Critical patent/EP3995758B1/de
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    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits 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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/003—Indoor unit with water as a heat sink or heat source
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel 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
    • 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
    • F25B2400/24—Storage receiver heat
    • 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
    • F25B2600/2501—Bypass 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off 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
    • 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
    • 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
    • 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
    • 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

Definitions

  • the present invention relates to a heat exchange unit for a refrigerant circuit for cooling and/or heating purposes.
  • the invention relates to a heat exchange unit for a refrigerant circuit for a refrigeration apparatus with a thermal storage particularly a thermal storage with a phase changing material (PCM). Even more particular, the invention relates to a heat exchange unit for a refrigerant circuit for a refrigeration apparatus with a thermal storage using CO 2 as a refrigerant.
  • PCM phase changing material
  • a refrigerating apparatus which includes a refrigerant circuit performing a refrigeration cycle.
  • the refrigerating apparatus of this type has been widely used for coolers such as refrigerators and freezers for storing food etc. and air conditioners for cooling/heating an inside of a room.
  • EP 2 844 924 B1 discloses an air-conditioning system comprising: a chiller system including a compressor, a condenser, an expansion device and an evaporator, a phase change material in thermal communication with the condenser, an actuator coupled to the phase change material; and a controller providing a trigger signal to the actuator to initiate changing the phase change material from a supercooled state to a solid state, wherein the phase change material includes a coolant supply line in thermal communication with the phase change material and the coolant supply line is coupled to the chiller system.
  • the phase change material is selected so that the phase change material transitions from liquid to solid when cooling demand on the chiller system is low or non-existent. This may occur in the evening, when ambient temperatures are lower.
  • the solid or frozen phase change material absorbs energy from the condenser, improving the efficiency of the condenser when the chiller system is running and increasing efficiency and capacity of the chiller system.
  • the air-conditioning system described in EP 2 844 924 B1 aims to provide a system that is capable of balancing cooling demand by using a phase change material as a heat buffer between the condenser and the ambient air temperature.
  • the phase change material absorbs the heat from the condenser and release it to the outside air. Due to its thermal capacity and the latent heat release, the phase change material will heat up slower than air and thus result in higher energy efficiency.
  • the phase change material is cooled down faster by the fresher air temperature using the fan only.
  • phase change material active cooling of the phase change material with the fan is inefficient, therefore, said system is particularly not suitable for regions with warmer climates, where air temperatures at night remain high.
  • the described system is not able to realize big improvements with regard to energy efficiency but will "flatten out” the energy consumption pattern due to the thermal response time of the phase change material. This is in particular true, since the active cooling of the phase change material also causes heating of the condenser, as the condenser is in thermal communication with the phase change material, and no control of the use of the phase change material is possible.
  • fluorocarbon has been conventionally used as a refrigerant in refrigeration systems.
  • Montreal Protocol in 1987 and the Kyoto Protocol in 1997 artificially developed substitute chlorofluorocarbons, whose ozone depletion potential is low, have become commonly used as refrigerants.
  • natural refrigerants such as carbon dioxide, ammonia, hydrocarbons (isobutene, propane, etc.), water and air, has progressed.
  • These natural refrigerants are materials that have the property that, when compared with the aforementioned chlorofluorocarbons and substitute chlorofluorocarbons, their GWP (Global Warming Potential) value is extremely low.
  • carbon dioxide is known as a material whose ozone depletion potential is zero, whose global warming potential is also much lower in comparison to conventional refrigerants, which has no toxicity, is non-flammable, and whose efficiency in creating a high temperature is good among natural refrigerants, and from environmental/energy aspects and safety aspects, carbon dioxide is garnering attention as a refrigerant in air conditioners.
  • CO 2 carbon dioxide
  • fluorinated refrigerants performs at high outside temperatures with a lower efficiency than fluorinated refrigerants. Accordingly, on an annual base the performance of an air conditioner system using CO 2 as a refrigerant is lower compared to fluorinated refrigerants, particularly in warmer climates.
  • EP 3 242 096 A1 being directed to a regenerative air conditioner comprising a refrigerant circuit to which a compressor section, an outdoor heat exchanger and an indoor heat exchanger are connected; and a thermal storage section in which heat is exchanged between the refrigerant in the refrigerant circuit and a thermal storage medium
  • a heat exchange unit according to the preamble of claim 1.
  • a refrigerant circuit for a refrigeration apparatus with a thermal storage which is using carbon dioxide (CO 2 ) as refrigerant, allowing the storage of thermal energy, particularly cold, for example when outside temperatures are low, preferably during the night, and use the thermal energy during peak temperatures during the day when transcritical conditions occur or during peak demand, in order to substantially prevent a decrease in cooling efficiency, which is particularly due to the use of a natural refrigerant like carbon dioxide, while ensuring a high cooling capacity and providing flexibility with regard to charging the thermal storage with cold.
  • the provided refrigerant circuit should also be able to store thermal energy, particularly cold, even during peak temperatures when for example much/excess PV power (CO 2 neutral energy generation) is available.
  • FIG. 1 shows a conventional air-conditioning system 100 having a supercooled phase change material (PCM).
  • a chiller system includes a compressor 110, a first heat exchanger 112, an expansion device 114 and a second heat exchanger 116.
  • the first heat exchanger 112 may be used as a condenser coil and may be located outside of a building or space to be conditioned.
  • the second heat exchanger 116 may be used as an evaporator coil.
  • refrigerant is subjected to a vapor compression cycle through compressor 110, condenser 112, expansion device 114 and evaporator 116. Heat is absorbed at evaporator 116 and heat is discharged at condenser 112.
  • the system of Fig. 1 may be a water chiller system.
  • Evaporator 116 is in thermal communication with a heat exchanger 118 (e.g., a coil) that carries a fluid coolant, e.g., water.
  • a supply pump 120 circulates coolant from heat exchanger 118 cooled by evaporator 116 to a supply valve 122.
  • Supply valve 22 supplies chilled water to a local zone terminal where a fan draws air over a coil to chill a space as known in the art.
  • a return valve 124 receives fluid returned from the local zone terminal and provides the return fluid to heat exchanger 118.
  • the condenser coil 112 as shown in Fig. 1 is in thermal communication with a phase change material 126.
  • a fan 128 draws air through the phase change material 126 to aid in cooling the phase change material 126.
  • a controller 132 then initiates the transition of the phase change material 126 from supercooled liquid to solid.
  • An actuator 130 is used to initiate the transition of the phase change material 126 from supercooled liquid to solid when the phase change material 126 is in a supercooled state.
  • the actuator 130 includes a thermoelectric cooler for freezing the phase change material 126.
  • Controller 132 receives a phase change material temperature signal from a phase change material sensor 134 and an ambient temperature signal from an ambient temperature sensor 136.
  • the phase change material 126 is selected so that the phase change material transitions from liquid to solid when cooling demand on the chiller system is low or non-existent. This may occur in the evening, when ambient temperatures are low. During the day, the solid or frozen phase change material 126 absorbs energy from the condenser 112 when the chiller system is running and increasing efficiency and capacity of the chiller system.
  • Fig. 2 is a refrigerant circuit 1 diagram illustrating a configuration of a refrigerant circuit of a first embodiment.
  • the shown refrigerant circuit uses CO 2 as refrigerant and includes one compressor 10, a heat-source-side heat exchanger of an outdoor unit of a so called "Conveni-Pack", including usually coolers such as refrigerators and freezers for storing food etc. and air conditioners (indoor units) for cooling/heating an inside of a room, particularly a show room/shopping room.
  • Conveni-Pack usually coolers such as refrigerators and freezers for storing food etc.
  • air conditioners indoor units for cooling/heating an inside of a room, particularly a show room/shopping room.
  • the refrigerant circuit only one indoor unit and one cooler are illustrated as example, but the refrigerant circuit can naturally include several coolers and air conditioners.
  • the shown refrigerant circuit further includes a thermal storage unit 100 and a heat exchange unit 200, which will be explained later in more detail.
  • the thermal storage unit 100 includes a thermal storage 20 including/accumulating a thermal storage material 21, which is a phase changing material (PCM).
  • the shown refrigerant circuit further includes a first fluid communication pipe 30 that connects a fluid side of the heat-source-side heat exchanger 11 with one side of the thermal storage 20 and a second fluid communication pipe 40 that connects the expansion device 12 and the other side of the thermal storage 20.
  • the term "connect” is used in the present disclosure to define that two entities, for example the “one side of the thermal storage” and the “thermal storage”, are connected with each other by a connecting means such as a "liquid pipe” or a “gas pipe” in such a manner that a fluid like a refrigerant can be liquid-tight and gas-tight transferred/exchanged/flow from one entity to the other one.
  • the connecting means provides a fluidic connection.
  • the refrigerant circuit 1 further includes a first switching mechanism 31, which is located on the first fluid communication pipe 30 and fluidically connects the heat-source-side heat exchanger 11, the thermal storage 20, a third fluid communication pipe 50 and a first gas communication pipe 60 with each other, wherein the third fluid communication pipe 50 is fluidically connecting to the expansion device 12 and the first gas communication pipe 60 is fluidically connecting to a suction side of the compressor 10.
  • a first switching mechanism 31 which is located on the first fluid communication pipe 30 and fluidically connects the heat-source-side heat exchanger 11, the thermal storage 20, a third fluid communication pipe 50 and a first gas communication pipe 60 with each other, wherein the third fluid communication pipe 50 is fluidically connecting to the expansion device 12 and the first gas communication pipe 60 is fluidically connecting to a suction side of the compressor 10.
  • the shown refrigerant circuit 1 further includes a second switching mechanism 41 located on the second fluid communication pipe 40 and fluidically connects the thermal storage 20, the expansion device 12 and a fourth fluid communication pipe 70 with each other, wherein the fourth fluid communication pipe 70 is fluidically connecting to a utilization-side heat exchanger 80A.
  • Fig. 2 also shows that the refrigerant circuit 1 further comprises a receiver 201, which is located on the third fluid communication pipe 50, between the expansion device 12 and the utilization-side heat exchanger 80A, wherein the receiver 201 is configured to separate the refrigerant coming from the expansion device in a subcritical state into liquid refrigerant and gas refrigerant.
  • a receiver 201 which is located on the third fluid communication pipe 50, between the expansion device 12 and the utilization-side heat exchanger 80A, wherein the receiver 201 is configured to separate the refrigerant coming from the expansion device in a subcritical state into liquid refrigerant and gas refrigerant.
  • the shown refrigerant circuit 1 also indicates that the refrigerant circuit 1 can further include an additional utilization-side heat exchanger 80B communicating on its liquid side with the expansion device 12 via the receiver 201 and on its gas side with the compressor 10.
  • the utilization-side heat exchanger 80A can be a heat exchanger of an air-conditioner, particularly of an indoor unit, and the additional utilization-side heat exchanger 80B can be a heat exchanger of a cooler such as a refrigerator or a freezer.
  • Fig. 3 is a refrigerant circuit diagram illustrating a configuration of a thermal storage unit of a fist embodiment.
  • the shown thermal storage unit 100 is part of the above described refrigerant circuit 1, wherein the switching mechanism 1 is configured according to a first alternative.
  • the shown thermal storage unit 100 includes the thermal storage 20 including the above described thermal storage material 21, which is a phase changing material (PCM), a thermal storage unit gas port 62 communicating to the utilization-side heat exchanger 80A, disposed outside the thermal storage unit 100, a first thermal storage unit fluid port 72 communicating to the utilization-side heat exchanger 80A, a second thermal storage unit fluid port 32A communicating to the heat-source-side heat exchanger 11, disposed outside the thermal storage unit 100, and a third thermal storage unit fluid port 52A communicating to the expansion device 12 disposed outside the thermal storage unit 100.
  • PCM phase changing material
  • the shown thermal storage unit 100 further includes the first switching mechanism 31 communicating among the second thermal storage unit fluid port 32A, the third thermal storage fluid port 52A, the thermal storage unit gas port 62 and one side of the thermal storage 20, and the second switching mechanism 41 communicating among the first thermal storage unit fluid port 72, the third thermal storage unit fluid port 52A and the other side of the thermal storage 20.
  • thermal storage unit 100 further includes a refrigerant heat exchange pipe 22 that is disposed inside the thermal storage 20, particularly inside the thermal storage material 21.
  • the first switching mechanism 31 is fluidically connected with one side of the refrigerant heat exchange pipe 22 and the second switching mechanism 41 is fluidically connected with the other end of the refrigerant heat exchange pipe 22.
  • the first switching mechanism 31 includes: a first valve 31A, which is a three-way valve, communicating among the second thermal storage unit fluid port 32A, the third thermal storage unit fluid port 52A and the thermal storage 20, and a second valve 31B, which is a three-way valve and located between the first valve 31A and the thermal storage 20, communicating among the first valve 31A, the thermal storage 20 and the thermal storage unit gas port 62.
  • a first valve 31A which is a three-way valve, communicating among the second thermal storage unit fluid port 32A, the third thermal storage unit fluid port 52A and the thermal storage 20
  • a second valve 31B which is a three-way valve and located between the first valve 31A and the thermal storage 20, communicating among the first valve 31A, the thermal storage 20 and the thermal storage unit gas port 62.
  • a check valve 31A provided that stops a backflow from the third thermal storage unit fluid port 52A to the first valve 31A.
  • the shown second switching mechanism 41 is a valve, which is a three-way valve, fluidically connecting the first thermal storage unit fluid port 72, the third thermal storage unit fluid port 52A and the thermal storage 20 with each other, wherein an expansion device 101 is located between the second switching mechanism 41 and the first thermal storage unit fluid port 72.
  • the second thermal storage unit fluid communication pipe 40 is connected with the third thermal storage unit fluid communication pipe 50 between the third thermal storage unit fluid port 52A and the check valve 53.
  • a thermal storage unit gas communication pipe 60 fluidically connects the thermal storage unit gas port 62 and the first switching mechanism 31, particularly the second valve 31B, with each other.
  • Fig. 4 is a refrigerant circuit diagram illustrating a configuration of the thermal storage unit 100 according to a second embodiment, particularly an alternative configuration.
  • the illustrated refrigerant circuit corresponds to the refrigerant circuit disclosed in Fig. 3 except the configuration of the first switching mechanism.
  • the first first valve 31A is a four-way valve that fluidically connects the second thermal storage unit fluid port 32A, the thermal storage 20, the thermal storage unit gas port 62 and the third thermal storage unit fluid port 52A.
  • Fig. 5 is a refrigerant circuit diagram illustrating a configuration of a thermal storage unit 100 according to a third embodiment, particularly a third alternative.
  • the shown alternative does not use the above described refrigerant heat exchange pipe 22, instead uses a heat exchanger 102.
  • the heat exchanger 102 is preferably a plate heat exchanger, which is on one side communicating with the first switching mechanism 31 and the second switching mechanism 41 and on the other side with the one side of the thermal storage 20 and the other side of the thermal storage 20.
  • the thermal storage unit 100 includes a circulating pump 103 that is located on the second thermal storage unit fluid communication pipe 40, between the heat exchanger 102 and the thermal storage 20. Accordingly, the thermal storage has a closed loop, particularly using water as coolant.
  • the circulating pump circulates the coolant through the thermal storage 20, thereby the coolant exchanges heat with the thermal storage material 21 of the thermal storage, and then to the heat exchanger 102, where the coolant again exchanges heat with the refrigerant of the refrigerant circuit 1.
  • the circulating pump 103 is able to control the amount of thermal energy exchanged between the thermal storage 20, particularly the thermal storage material 21, and the refrigerant of the refrigerant circuit 1.
  • Fig. 6 is a refrigerant circuit diagram illustrating a configuration of a heat exchange unit 200 according to the invention.
  • the shown heat exchange unit 200 includes the compressor 10, the heat-source-side heat exchanger 11 the expansion device 12, a heat exchange unit gas port 92 communicating to the utilization-side heat exchanger 80A disposed outside the heat exchange unit 200, a first heat exchange unit fluid port 96 communicating to the utilization-side heat exchanger 80A, a second heat exchange unit fluid port 32B communicating to the heat-source-side heat exchanger 11, a third heat exchange unit fluid port 52B communicating to the expansion device 12.
  • the shown second heat exchange unit fluid port 32B is fluidically connected to the above described thermal storage unit 100 disposed outside the heat exchange unit 200 and the third heat exchange unit fluid port 52B is also fluidically connected to the thermal storage unit 100.
  • the shown heat exchange unit 200 further includes a heat exchange unit gas communication pipe 90 communicating between the heat exchange unit gas port 92 and the at least one compressor 10, a first heat exchange unit fluid communication pipe 30 communicating between the second heat exchange unit fluid port 32B and the heat-source-side heat exchanger 11, and a second heat exchange unit fluid communication pipe 50 communicating between the third heat exchange unit fluid port 52B and the first heat exchange unit fluid port 96.
  • the expansion device 12 is located on the second heat exchange unit fluid communication pipe 50, between the first heat exchange unit fluid port 96 and the third heat exchange unit fluid port 52B.
  • the shown heat exchange unit 200 further includes the above described receiver 201, which is located on the second heat exchange unit fluid communication pipe 50, between the first heat exchange unit fluid port 96 and the expansion device 12, wherein the receiver 201 is configured to separate liquid refrigerant and gas refrigerant.
  • the heat exchange unit 200 further includes a fourth heat exchange unit fluid port 203 fluidically connecting the expansion device 12 and the additional utilization-side heat exchanger 80B disposed outside the heat exchange unit 200.
  • the shown heat exchange unit 200 further includes a third heat exchange unit fluid communication pipe 202 fluidically connecting the fourth heat exchange unit fluid port 203 with the expansion device 12 and is connected with the second heat exchange unit fluid communication pipe 50 between the first heat exchange unit fluid port 96 and the receiver 201.
  • Fig. 7 is a refrigerant circuit diagram illustrating a configuration of a refrigeration apparatus 300 of a first embodiment during a normal refrigeration and cooling operation.
  • the shown refrigeration apparatus 300 includes the above described refrigerant circuit 1, the thermal storage unit 100 and the heat exchange unit 200, which are further detailed for explanatory purposes.
  • the shown heat exchange unit 200 further includes a subcooling heat exchanger 204, which is located between the first heat exchange unit fluid port 96 and the receiver 201.
  • the refrigeration apparatus 300 includes three coolers such as refrigerators and freezers for storing food etc. and three air conditioners (indoor units) for cooling/heating an inside of a room, particularly a show room/shopping room.
  • the three indoor units are each provided with one utilization-side heat exchanger 380A - 380C and the three refrigerators are each provided with one additional utilization-side heat exchanger 301A - 301C.
  • the shown heat exchange unit 200 further includes a second compressor 310B and a third compressor 310C that are provided parallel to each other and upstream of the above described compressor 10 of the basic configuration.
  • the three compressors 310A - 310B build a two-stage compressor system, wherein the second compressor 310B communicates with the additional utilization-side heat exchangers 301A - 301C to build a refrigeration circuit and the third compressor 310C communicates with the utilization-side heat exchangers 380A - 380C to build an air-conditioning circuit.
  • the three compressors 310A - 310C can be variable capacity compressors and/or fixed capacity compressors, depending on the requirements of the refrigerant apparatus.
  • All of the three compressors 310A - 310C are hermetic scroll compressors.
  • the shown heat exchange unit 200 further includes an injection pipe 206 fluidically connecting a gas side of the receiver 201 with a suction side of the first compressor 10, 310A, wherein the injection pipe 206 is configured to inject intermediate-pressure refrigerant collected by the receiver 201 into the first compressor 10, 310A.
  • the injection pipe 206 joins with two high-pressure pipes 207, 208 communicating between high-pressure sides of the second compressor 310B and the third compressor 310C and the suction side of the first compressor 10, 310A, before connecting to a suction side of the first compressor 10, 310A.
  • the injection pipe 206 is provided with an expansion device 207, which is preferably located before the connection point of the injection pipe 206 with the high-pressure pipes 207, 208.
  • FIG. 7 illustrates the refrigeration apparatus 300 in a normal refrigeration and cooling operation. Accordingly, all three compressors 310A - 310C are turned on, which means, the second compressor 310B draws low pressure refrigerant from the additional utilization-side heat exchangers 301A - 301C of the three coolers and the third compressor 310C draws refrigerant from the utilization-side heat exchanger 380C of one of the three indoor units.
  • the two compressors 310B, 310C provide intermediate-pressure refrigerant to the first compressor 310A, which further compresses the refrigerant and discharges high-pressure refrigerant which flows to the heat-source-side heat exchanger 11, which acts as a gas cooler.
  • Such refrigerant is cooled by dissipating heat to outdoor air supplied by an outdoor fan.
  • the high-pressure refrigerant flowing out from the heat-source-side heat exchanger 11 flows via the first fluid communication pipe 30 to the first switching mechanism 31, particularly the first valve 31A, which is a three-way valve.
  • the three-way valve 31A is in a state, in which the first fluid communication pipe 30 is communicating with the third fluid communication pipe 50 and a flow to the second valve 31B is blocked.
  • the high-pressure refrigerant flows directly to the expansion device 12, which is an expansion valve, without flowing through the thermal storage 20 or exchanging heat with the thermal storage 20 via the heat exchanger 102.
  • the expansion device 12 which is an expansion valve, without flowing through the thermal storage 20 or exchanging heat with the thermal storage 20 via the heat exchanger 102.
  • the expansion device 12 Flowing through the expansion device 12, the pressure of the cooled high-pressure refrigerant is reduced, and the refrigerant is changed into intermediate-pressure refrigerant in a gas-liquid two-phase state (subcritical refrigerant).
  • the intermediate-pressure refrigerant flows to the receiver 201, a part of the refrigerant, particularly liquid intermediate-pressure refrigerant, flows from the receiver 201 to a first flow path 204A of the subcooling heat exchanger 204.
  • the refrigerant flowing into the first flow path 204A is cooled by intermediate-pressure refrigerant flowing through the second flow path 204B, and the degree of subcooling of such refrigerant is increased.
  • a part of the so subcooled liquid refrigerant flows through an expansion device 205, particularly a subcooling expansion valve, thereby reducing the pressure of the intermediate-pressure refrigerant further.
  • the intermediate-pressure refrigerant flows into the second flow path 204B of the subcooling heat exchanger 204 and is evaporated by absorbing heat from the refrigerant flowing through the first flow path 204A of the subcooling heat exchanger 204.
  • the subcooled intermediate-pressure refrigerant flows so as to be branched into two main pipes providing the refrigerant to the refrigeration circuit and the air-conditioning circuit, where the refrigerant is branched again into three pipes providing the utilization-side heat exchangers 380A - 380C of the indoor units and the additional utilization-side heat exchangers 301A - 301C of the coolers with liquid refrigerant.
  • the refrigerant flows through an expansion device, particularly an air-conditioning expansion valve or a cooler expansion valve, where the pressure of the intermediate-pressure refrigerant is reduced.
  • Such refrigerant flows through the utilization-side heat exchangers and is evaporated by absorbing heat from example room air supplied by an air-conditioning fan of the indoor units.
  • the evaporated refrigerant of the utilization-side heat exchangers 380A - 380C of the indoor units is rejoined and flows via a suction pipe back to a suction side of the third compressor 310C.
  • the evaporated refrigerant of the additional utilization-side heat exchangers 301A - 301C of the coolers is rejoined and flows via a suction pipe back to a suction side of the second compressor 310B.
  • the air-conditioning circuit and the refrigeration circuit are a closed loop.
  • the evaporated refrigerant of the subcooling heat exchanger 204 is joined with intermediate-pressure refrigerant discharged from the second compressor 310B and the third compressor 310C and provided to the suction side of the first compressor 310A.
  • gas intermediate-pressure refrigerant separated by the receiver 201 from the liquid intermediate-pressure refrigerant of the supercritical refrigerant flows through an expansion device to reduce the pressure to a similar pressure as the pressure of the intermediate-pressure refrigerant discharged by the second compressor 310B and the third compressor 310C.
  • Fig. 8 is a refrigerant circuit diagram illustrating the refrigeration apparatus 300 of Fig. 7 during a refrigeration operation using the thermal storage.
  • the first switching mechanism 31, in particular the first and second valve, and the second switching valve are set in such a way that the high-pressure refrigerant flowing out from the heat-source-side heat exchanger 11 flows via the first fluid communication pipe 30 into the first and second valve and then into the thermal storage, thereby exchanging heat with the thermal storage 20.
  • the high-pressure refrigerant is cooled.
  • the high-pressure refrigerant flows via the second switching mechanism via the expansion device 12 back to the receiver 201.
  • the pressure of the cooled high-pressure refrigerant is reduced and the refrigerant is changed into intermediate-pressure refrigerant in a gas-liquid two-phase state (supercritical refrigerant).
  • a part of the refrigerant flows then from the receiver 201 to the first flow path 204A of the subcooling heat exchanger 204.
  • the refrigerant flowing into the first flow path 204A is cooled by intermediate-pressure refrigerant flowing through the second flow path 204B, and the degree of subcooling of such refrigerant is increased.
  • a part of the so subcooled liquid refrigerant flows through the expansion device 205 thereby reducing the pressure of the intermediate-pressure refrigerant further.
  • the intermediate-pressure refrigerant flows into the second flow path 204B of the subcooling heat exchanger 204 and is evaporated by absorbing heat from the refrigerant flowing through the first flow path 204A of the subcooling heat exchanger 204.
  • the subcooled intermediate-pressure refrigerant flows then so as to provide the refrigerant only to the refrigeration circuit and not to the air-conditioning circuit, where the refrigerant is branched again into three pipes providing the additional utilization-side heat exchangers 301A - 301C of the coolers with liquid refrigerant.
  • the refrigerant flows through the cooler expansion valve, where the pressure of the intermediate-pressure refrigerant is reduced.
  • Such refrigerant flows through the additional utilization-side heat exchangers and is evaporated by absorbing heat from storage room air within the coolers.
  • the third compressor 310 is turned off.
  • the second compressor 310 draws low pressure refrigerant from the additional utilization-side heat exchangers 301A - 301C of the coolers and provides intermediate-pressure refrigerant via the high-pressure pipe 207 to the first compressor 310A, which further compresses the refrigerant and discharges high-pressure refrigerant which flows to the heat-source-side heat exchanger 11, which acts as a gas cooler.
  • Such refrigerant is cooled by dissipating heat to outdoor air supplied by an outdoor fan.
  • the high-pressure refrigerant flowing out from the heat-source-side heat exchanger 11 flows then via the first fluid communication pipe 30 back to the first switching mechanism 31, thereby closing the refrigerant circuit.
  • Fig. 9 is a refrigerant circuit diagram illustrating the refrigeration apparatus of Fig. 7 during a refrigeration and cooling operation using the thermal storage.
  • the refrigeration and cooling operation using the thermal storage is similar to the above with regard to Fig 8 described refrigeration (only) operation using the thermal storage, except that all three compressors 310A to 310C are in use.
  • the second compressor 310B draws low pressure refrigerant from the additional utilization-side heat exchangers 301A - 301C of the three coolers and the third compressor 310C draws refrigerant from the utilization-side heat exchanger 380C of one of the three indoor units, which is the provided as intermediate-pressure refrigerant to the first compressor 310A, which further compresses the refrigerant and discharges high-pressure refrigerant which flows to the heat-source-side heat exchanger 11.
  • Such refrigerant flows then as described above through the thermal storage 20, the expansion device 12, the receiver 201, the subcooling heat exchanger 204 and is then branched into the two main pipes providing the refrigerant to the refrigeration circuit and the air-conditioning circuit, closing the refrigerant circuit.
  • Fig. 10 is a refrigerant circuit diagram illustrating the refrigeration apparatus of Fig. 7 during an only charging operation of the thermal storage.
  • the second compressor 310B is turned off.
  • the third compressor 310C draws the refrigerant directly from the thermal storage 20 and provides intermediate-pressure refrigerant to the first compressor which compresses the refrigerant further and discharges high-pressure refrigerant which flows to the heat-source-side heat exchanger 11, which acts as a gas cooler.
  • the high-pressure refrigerant flowing out from the heat-source-side heat exchanger 11 flows then via the first fluid communication pipe 30 to the first switching mechanism 31.
  • the first valve 31A is set in such a manner that the high-pressure refrigerant flows as described above with Fig. 7 directly to the expansion device 12.
  • the intermediate-pressure refrigerant in a gas-liquid two-phase state flows to the receiver 201 and from there liquid intermediate-pressure refrigerant flows then to the first flow path 204A of the subcooling heat exchanger 204.
  • the refrigerant flowing into the first flow path 204A is cooled by intermediate-pressure refrigerant flowing through the second flow path 204B, and the degree of subcooling of such refrigerant is increased.
  • the subcooled intermediate-pressure refrigerant flows then via the second valve 31B back to the thermal storage 20 and by flowing through the thermal storage 20 cools the thermal storage 20, in particular the thermal storage material, thereby charges the thermal storage with cold.
  • Fig. 11 is a refrigerant circuit diagram illustrating the refrigeration apparatus of Fig. 7 during a refrigeration operation while charging the thermal storage.
  • the refrigeration operation while charging the thermal storage is similar to the above with regard to Fig. 10 described only charging operation of the thermal storage, except that all three compressors 310A - 310C are in use and that the second compressor 310B connects the additional utilization-side heat exchangers 301A - 301C of the coolers to the refrigerant circuit 1.
  • the thermal storage 20 can be charged while performing a refrigeration operation.
  • Fig. 12 is a refrigerant circuit diagram illustrating a configuration of a refrigeration apparatus 300 of a second embodiment having a capacity increasing unit 320.
  • the refrigerant apparatus 300 of the second embodiment mostly corresponds to the refrigerant apparatus of the first embodiment described with regard to Fig. 7 .
  • the thermal storage unit 100 instead of being provided with the thermal storage unit 100, the two connecting pipes connecting the second heat exchanger unit fluid port 32B and the third heat exchanger unit fluid port 52B have an open end. Meaning, the unit connected via the second and third heat exchanger unit fluid ports 32B and 52B with the refrigerant apparatus 300, in particular with the heat exchanger unit 200, is not shown.
  • the thermal storage unit 100 also a heat exchanger, particularly a plate heat exchanger
  • a capacity increasing unit or a combi unit including a thermal storage unit and a capacity increasing unit can be connected to the heat exchanger unit 200.
  • Fig. 13 is a refrigerant circuit diagram illustrating a capacity increasing unit 320.
  • the capacity increasing unit 320 is basically an independent refrigerant circuit that can be added to or connected with the refrigerant apparatus 300, in order to increase the refrigeration and cooling capacity of the refrigerant apparatus 300.
  • the capacity increasing unit 320 includes a heat exchanger, a compressor and an expansion device which build a closed refrigerant circuit.
  • the heat exchanger is configured to exchange heat with the heat exchanger unit 200. Therefore, the heat exchanger can be connected with the second and third heat exchanger unit fluid ports 32B and 52B.
  • the capacity increasing unit 320 is provided with a heat-source-side heat exchanger that cools down the refrigerant flowing there through by dissipating heat to outdoor air supplied by an outdoor fan.
  • Fig. 14 is a refrigerant circuit diagram illustrating a combi unit 330 having a capacity increasing unit 320 and a thermal storage unit.
  • the capacity increasing unit 320 includes a heat exchanger, a compressor and an expansion device which build a closed refrigerant circuit.
  • the thermal storage unit is arranged between the heat exchanger unit 200 and the thermal storage unit.
  • the combi unit 330 additionally includes a circulating pump that circulates a refrigerant or a coolant like water, cooled by the capacity increasing unit through the thermal storage unit, in order to charge the thermal storage unit with thermal energy, particularly cold.
  • the thermal storage unit is provided with a heat exchanger that is used to exchange heat with the refrigerant circuit of the refrigerant apparatus 300, in particular with the heat exchanger unit 200.
  • the capacity increasing unit may include a closed refrigerant circuit including a heat exchanger, a compressor, a heat-source-side heat exchanger cooled by a fan and an expansion device, wherein the heat exchanger exchanges heat with the heat exchange unit.
  • the combi unit may include a capacity increasing unit, comprising a closed refrigerant circuit including a heat exchanger, a compressor, a heat-source-side heat exchanger cooled by a fan and an expansion device, and a thermal storage unit comprising a heat exchanger, a thermal storage, including a thermal storage material, particularly a phase changing material (PCM), and a circulating pump, wherein the heat exchanger exchanges heat with the heat exchange unit.
  • a capacity increasing unit comprising a closed refrigerant circuit including a heat exchanger, a compressor, a heat-source-side heat exchanger cooled by a fan and an expansion device
  • a thermal storage unit comprising a heat exchanger, a thermal storage, including a thermal storage material, particularly a phase changing material (PCM), and a circulating pump, wherein the heat exchanger exchanges heat with the heat exchange unit.
  • PCM phase changing material

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (9)

  1. Wärmetauschereinheit (200) für eine Kühlvorrichtung, die CO2 als Kältemittel verwendet und eine Wärmespeichereinheit (100) und einen nutzungsseitigen Wärmetauscher (80A) einschließt,
    umfassend:
    mindestens einen Verdichter (10),
    einen wärmequellenseitigen Wärmetauscher (11),
    eine Expansionsvorrichtung (12),
    einen Wärmeaustauscheinheit-Gasanschluss (92), der so ausgebildet ist, dass er mit dem nutzungsseitigen Wärmetauscher (80A) kommuniziert, der außerhalb der Wärmeaustauscheinheit (200) angeordnet ist,
    einen ersten Wärmetauschereinheit-Fluidanschluss (96), der so ausgebildet ist, dass er mit dem nutzungsseitigen Wärmetauscher (80A) kommuniziert,
    einen zweiten Wärmetauschereinheit-Fluidanschluss (32B), der mit dem wärmequellenseitigen Wärmetauscher (11) kommuniziert,
    einen dritten Wärmetauschereinheit-Fluidanschluss (52B), der mit der Expansionsvorrichtung (12) kommuniziert, und
    eine Wärmetauschereinheit-Gasverbindungsleitung (90), die zwischen dem Wärmetauschereinheit-Gasanschluss (92) und dem mindestens einen Verdichter (10) kommuniziert,
    wobei
    ein Auslass des mindestens einen Verdichters (10) über eine Kältemittelleitung mit einem Einlass des wärmequellenseitigen Wärmetauschers (11) verbunden ist, ein Auslass des wärmequellenseitigen Wärmetauschers (11) über eine erste Wärmetauscher-Fluidverbindungsleitung (30) mit dem zweiten Wärmetauschereinheit-Fluidanschluss (32B) verbunden ist, der dritte Wärmetauschereinheit-Fluidanschluss (52B) über eine zweite Wärmetauschereinheit-Fluidverbindungsleitung (50) mit einem Einlass der Expansionsvorrichtung (12) verbunden ist und ein Auslass der Expansionsvorrichtung (12) über die zweite Wärmetauschereinheit-Fluidverbindungsleitung (50) mit dem ersten Wärmetauschereinheit-Fluidanschluss (96) verbunden ist, und
    der zweite Wärmetauschereinheit-Fluidanschluss (32B) und der dritte Wärmetauschereinheit-Fluidanschluss (52B) so ausgebildet sind, dass sie mit der Wärmespeichereinheit (100) kommunizieren, die einen Wärmespeicher (20) einschließt, der ein Wärmespeichermaterial (21) einschließt oder ansammelt,
    dadurch gekennzeichnet, dass
    die Wärmetauschereinheit (200) weiter einen Empfänger (201) umfasst, der an der zweiten Wärmetauschereinheit-Fluidverbindungsleitung (50), insbesondere zwischen dem ersten Wärmetauschereinheit-Fluidanschluss (96) und der Expansionsvorrichtung (12), angeordnet ist, wobei der Empfänger (201) so ausgebildet ist, dass er flüssiges Kältemittel und gasförmiges Kältemittel trennt.
  2. Wärmetauschereinheit (200) nach Anspruch 1, weiter umfassend einen vierten Wärmeaustauscheinheit-Fluidanschluss (203), der so ausgebildet ist, dass er zwischen der Expansionsvorrichtung (12) und einem weiteren nutzungsseitigen Wärmeaustauscher (80B) kommuniziert, der außerhalb der Wärmeaustauscheinheit (200) angeordnet ist.
  3. Wärmetauschereinheit (200) nach Anspruch 2, weiter umfassend eine dritte Wärmetauschereinheit-Fluidverbindungsleitung (202), die zwischen dem vierten Wärmetauschereinheit-Fluidanschluss (203) und der Expansionsvorrichtung (12) kommuniziert und vorzugsweise mit der zweiten Wärmetauschereinheit-Fluidverbindungsleitung (50) zwischen dem ersten Wärmetauschereinheit-Fluidanschluss (96) und dem Empfänger (201) verbunden ist.
  4. Wärmetauschereinheit (200) nach einem der vorstehenden Ansprüche, weiter umfassend einen Unterkühlungswärmetauscher (204), der vorzugsweise zwischen dem ersten Wärmetauschereinheit-Fluidanschluss (96) und der Expansionsvorrichtung (12), bevorzugter zwischen dem ersten Wärmetauschereinheit-Fluidanschluss (96) und dem Empfänger (201), angeordnet ist.
  5. Wärmetauschereinheit (200) nach einem der vorstehenden Ansprüche, weiter umfassend einen zweiten Verdichter (310B, 310C), der stromaufwärts von dem mindestens einen Verdichter (10, 310A) vorgesehen ist, um ein zweistufiges Verdichtersystem zu bilden.
  6. Wärmetauschereinheit (200) nach einem der Ansprüche 1 bis 4, weiter umfassend einen zweiten und einen dritten Verdichter (310B, 310C), die parallel zueinander und stromaufwärts des mindestens einen Verdichters (10, 310A) vorgesehen sind, um ein zweistufiges Verdichtersystem zu bilden, wobei vorzugsweise der zweite Verdichter (310B) mit dem weiteren nutzungsseitigen Wärmetauscher (80B, 301A) kommuniziert, um einen Kältekreislauf zu bilden, und der dritte Verdichter (310C9) mit dem nutzungsseitigen Wärmetauscher (80A, 380A) kommuniziert, um einen Klimatisierungskreislauf zu bilden.
  7. Wärmetauschereinheit (200) nach Anspruch 5 oder 6, weiter umfassend eine Einspritzleitung (206), die zwischen einer Gasseite des Empfängers (201) und einer Saugseite des mindestens einen Verdichters (10, 310A) kommuniziert, wobei die Einspritzleitung (206) so ausgebildet ist, dass sie ein Mitteldruck-Kältemittel in den Verdichter (10, 310A) einspritzt.
  8. Wärmetauschereinheit (200) nach Anspruch 7, wobei die Einspritzleitung (206) vor dem Verbinden mit einer Saugseite des mindestens einen Verdichters (10, 310A) in zwei Hochdruckleitungen (207, 208) mündet, die zwischen der Hochdruckseite des zweiten und dritten Verdichters (310B, 310C) und der Saugseite des mindestens einen Verdichters (10, 310A) kommunizieren.
  9. Wärmetauschereinheit (200) nach Anspruch 8, wobei die Einspritzleitung (206) mit einer Expansionsvorrichtung (209) versehen ist, die vorzugsweise vor der Verbindungsstelle der Einspritzleitung (206) mit den Hochdruckleitungen (207, 208) angeordnet ist.
EP20205893.9A 2020-11-05 2020-11-05 Wärmeaustauscheinheit für ein kühlgerät mit einem wärmespeicher und verwendung von co2 als kältemittel Active EP3995758B1 (de)

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EP20205893.9A EP3995758B1 (de) 2020-11-05 2020-11-05 Wärmeaustauscheinheit für ein kühlgerät mit einem wärmespeicher und verwendung von co2 als kältemittel
JP2023524921A JP2023546495A (ja) 2020-11-05 2021-11-04 蓄熱器を有する冷却装置のための冷媒回路および冷媒回路を制御する方法
US18/032,961 US20230392829A1 (en) 2020-11-05 2021-11-04 Refrigerant circuit for a refrigeration apparatus with a thermal storage and method for controlling a refrigerant circuit
PCT/JP2021/040591 WO2022097680A1 (en) 2020-11-05 2021-11-04 Refrigerant circuit for a refrigeration apparatus with a thermal storage and method for controlling a refrigerant circuit

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JP6849036B1 (ja) * 2019-09-30 2021-03-24 ダイキン工業株式会社 熱源ユニットおよび冷凍装置
WO2022271872A1 (en) * 2021-06-22 2022-12-29 Booz Allen Hamilton Inc. Thermal management systems for extended operation
CN115218298A (zh) * 2022-06-16 2022-10-21 上海伯涵热能科技有限公司 一种冷凝器过冷段采用微通道换热器的超高能效除湿机

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JP2006003023A (ja) * 2004-06-18 2006-01-05 Sanyo Electric Co Ltd 冷凍装置
WO2010097874A1 (ja) 2009-02-27 2010-09-02 ダイキン工業株式会社 冷凍装置
KR101325319B1 (ko) * 2011-10-25 2013-11-08 엘지전자 주식회사 축열식 냉난방 장치
ES2729992T3 (es) 2012-05-03 2019-11-07 Carrier Corp Sistema de aire acondicionado que utiliza material de cambio de fase sobreenfriado
JP6020549B2 (ja) * 2014-12-26 2016-11-02 ダイキン工業株式会社 蓄熱式空気調和機

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