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WO2024204077A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2024204077A1
WO2024204077A1 PCT/JP2024/011724 JP2024011724W WO2024204077A1 WO 2024204077 A1 WO2024204077 A1 WO 2024204077A1 JP 2024011724 W JP2024011724 W JP 2024011724W WO 2024204077 A1 WO2024204077 A1 WO 2024204077A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
flow path
radiator
heat
branch
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.)
Pending
Application number
PCT/JP2024/011724
Other languages
English (en)
Japanese (ja)
Inventor
庸貴 椛島
正喜 山口
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Priority to EP24723690.4A priority Critical patent/EP4462037A4/fr
Priority to CN202480006664.0A priority patent/CN120548445A/zh
Publication of WO2024204077A1 publication Critical patent/WO2024204077A1/fr
Anticipated expiration legal-status Critical
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • 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

Definitions

  • the present invention relates to a refrigeration cycle device.
  • Patent document 1 describes a compressor system in which multiple compressors are connected in parallel.
  • a refrigeration cycle device that uses the compressor system of Patent Document 1 to increase the amount of refrigerant circulated and increase the amount of refrigerant available for cooling an object, thereby ensuring refrigeration capacity.
  • the total capacity of the compressors needs to be increased as the refrigeration capacity required for cooling the object increases. More specifically, it is necessary to increase the number of compressors or the capacity of each compressor, which leads to increased equipment costs and an increase in the size of the entire refrigeration cycle device.
  • the present disclosure proposes a refrigeration cycle device in which the total capacity of the compressors is reduced compared to a case in which the refrigeration capacity is ensured by increasing the amount of refrigerant circulated.
  • a refrigeration cycle apparatus includes a first compression element that compresses a drawn refrigerant and discharges it to a first flow path, a radiator that is provided in the first flow path and passes the refrigerant through and radiates heat extracted from the passing refrigerant, a branching section that branches the refrigerant after passing through the radiator in the first flow path into a first branch and a second branch, a first pressure reduction element that reduces the pressure of the refrigerant branched to the first branch and causes it to flow into the second flow path, a heat exchanger that performs heat exchange between the refrigerant flowing through the second flow path and the refrigerant branched to the second branch, a second pressure reduction element that reduces the pressure of the refrigerant after heat exchange by the heat exchanger in the second branch, a cooler that cools an object by heat exchange between the refrigerant after pressure reduction by the second pressure reduction element and the object and causes the refrigerant after heat exchange to be drawn into the first compression element, a first compression element that compress
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the first aspect, wherein the junction joins the third flow path at a position in the first flow path after the refrigerant has passed through the radiator, and the junction includes a second radiator that is provided in the third flow path and radiates heat extracted by passing the refrigerant compressed by the second compression element through the second flow path.
  • heat radiation from the radiator can be increased compared to a case in which the junction joins the third flow path at a position in the first flow path before the refrigerant has passed through the radiator.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the second aspect, in which the capacity of the first compression element is larger than the capacity of the second compression element. In this case, heat dissipation from the radiator can be increased compared to a case in which the capacity of the first compression element is smaller than the capacity of the second compression element.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the third aspect, further comprising a third pressure reducing element provided in the third flow path and reducing the pressure of the refrigerant after passing through the second radiator. In this case, a compression ratio in the second compression element can be set large.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the second aspect, further comprising a fourth pressure reducing element provided in the first flow path after the refrigerant has passed through the radiator and before the merging portion merges with the third flow path, the fourth pressure reducing element reducing the pressure of the refrigerant after the refrigerant has passed through the radiator.
  • a compression ratio in the first compression element can be set to be large.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the first to fifth aspects, in which at least a part of the refrigerant is carbon dioxide. In this case, heat dissipation in the radiator is greater than in the case of using a non-azeotropic refrigerant not containing carbon dioxide.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the first aspect, further comprising: temperature sensors for measuring a temperature of the refrigerant at a position in the first flow path before passing through the radiator and before the third flow path merges with the junction, and at a position in the third flow path before the refrigerant merges with the first flow path at the junction, and a control unit for controlling circulation of the refrigerant based on the temperature of the refrigerant measured by the temperature sensors, wherein the control unit controls the flow resistance of the first pressure reduction element to increase when the temperature of the refrigerant measured in the first flow path is higher than the temperature of the refrigerant measured in the third flow path.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the first aspect, further comprising: temperature sensors for measuring a temperature of the refrigerant at a position in the first flow path before passing through the radiator and before the third flow path merges with the junction, and at a position in the third flow path before the refrigerant merges with the first flow path at the junction, and a control unit for controlling circulation of the refrigerant based on the temperature of the refrigerant measured by the temperature sensors, wherein the control unit controls the flow rate of the second compression element to be increased when the temperature of the refrigerant measured in the first flow path is higher than the temperature of the refrigerant measured in the third flow path.
  • an enthalpy difference between the refrigerant compressed by the first compression element and the refrigerant compressed by the second compression element is reduced.
  • FIG. 1 is a diagram showing a schematic configuration example of an air conditioning device to which the present embodiment is applied; 1 is a schematic diagram of a refrigerant circuit according to a first embodiment.
  • FIG. 1 is a pressure-specific enthalpy diagram illustrating a refrigeration cycle of a refrigerant circulating in a refrigerant circuit according to a first embodiment.
  • FIG. FIG. 6 is a schematic diagram of a refrigerant circuit according to a second embodiment.
  • FIG. 11 is a schematic diagram of a refrigerant circuit according to a third embodiment.
  • FIG. 10 is a schematic diagram of a refrigerant circuit according to a fourth embodiment.
  • FIG. 13 is a diagram illustrating a refrigerant circuit of an application example.
  • 1A is a schematic diagram of a refrigerant circuit in a conventional refrigeration cycle device
  • FIG. 1B is a pressure-specific enthalpy diagram illustrating a refrigeration cycle of a refrigerant circulating in the ref
  • FIG. 8 is a diagram for explaining a conventional refrigeration cycle device, where (a) is a schematic diagram of a refrigerant circuit 10' in the conventional refrigeration cycle device, and (b) is a pressure-specific enthalpy diagram illustrating the refrigeration cycle of the refrigerant circulating in the refrigerant circuit 10'.
  • the horizontal axis is specific enthalpy [kJ/kg]
  • the vertical axis is absolute pressure [MPa.abs] based on absolute vacuum.
  • the lines connecting the devices are pipes that serve as the flow path of the refrigerant.
  • a refrigeration cycle 300' is shown using thick lines, and points 10a' to 10f' on the refrigeration cycle 300' correspond to positions 10a' to 10f' of the refrigerant circuit 10', respectively. Therefore, points 10a' to 10f' in the refrigeration cycle 300' are expressed as positions 10a' to 10f'.
  • Fig. 8(b) also shows a saturated liquid line 301, a saturated vapor line 302, a critical point 303, and a 45°C isotherm 304 of the carbon dioxide refrigerant.
  • the refrigerant circuit 10' includes two compressors 12' and 13' connected in parallel, a radiator 14', a pressure reducing valve 18', and a cooler 19', and circulates carbon dioxide, which is an example of a refrigerant. More specifically, the refrigerant that has passed through the cooler 19' and exchanged heat with the object branches into two branches at the branching section 30' (position 10a'). Of the branched refrigerant, the refrigerant that flows through one branch is compressed by the compressor 12', and the refrigerant that flows through the other branch is compressed by the compressor 13', and then merges at the merging section 20' (position 10b').
  • the merged refrigerant passes through the radiator 14' to radiate heat (position 10e'). Then, the refrigerant that has radiated heat passes through the pressure reducing valve 18' to be depressurized (position 10f') and passes through the cooler 19' again (position 10a').
  • the specific enthalpy and pressure of the refrigerant change due to each device, and a refrigerant refrigeration cycle is established. More specifically, as shown in FIG. 8(b), from position 10a' to position 10b', the pressure and specific enthalpy of the refrigerant increase due to compression by compressors 12' and 13' and the acquisition of heat of compression. Also, from position 10b' to position 10e', the specific enthalpy of the refrigerant decreases due to heat dissipation in radiator 14'. Furthermore, from position 10e' to position 10f', the pressure of the refrigerant decreases due to pressure reduction by pressure reducing valve 18'. Furthermore, from position 10f' to position 10a', the specific enthalpy of the refrigerant increases due to heat exchange with the object in cooler 19'.
  • the ability of a cooler to cool an object (sometimes referred to as "refrigeration capacity") is determined according to the amount of heat (heat absorption) that the refrigerant passing through the cooler takes from the object. Therefore, in a conventional refrigeration cycle device using a refrigerant circuit 10', the refrigeration capacity of the cooler 19' is determined according to the product of the amount of change in specific enthalpy when moving from position 10f' to position 10a' and the amount of refrigerant passing through the cooler 19'.
  • the amount of refrigerant circulating in the refrigerant circuit 10' is increased, and the amount of refrigerant passing through the cooler 19' is increased. More specifically, the number of compressors connected in parallel to the compressors 12', 13' is increased, or the capacities of the compressors 12', 13' are increased. Therefore, in a refrigeration cycle apparatus using the conventional refrigerant circuit 10', the greater the refrigeration capacity to be secured, the greater the total capacity of the compressors. Note that the "total capacity" is the total value of the capacities of all the compressors provided in the refrigerant circuit.
  • a refrigeration cycle apparatus to which the embodiment of the present invention is applied has a configuration that suppresses the total capacity of the compressors, compared to a case in which the refrigerant circulation amount is increased to ensure refrigeration capacity.
  • FIG. 1 is a diagram showing a schematic configuration example of an air conditioning device 1 to which this embodiment is applied.
  • an air-conditioning apparatus 1 to which this embodiment is applied includes a refrigerant circuit 10 through which a refrigerant circulates, and a control unit 50 that controls the circulation of the refrigerant in the refrigerant circuit 10.
  • the control unit 50 is connected by wire or wirelessly to each device (described later using FIG. 2) included in the refrigerant circuit 10, and is capable of transmitting control signals to each device.
  • the air conditioning device 1 is an example of a refrigeration cycle device in this embodiment.
  • the air conditioner 1 cools the air it takes in and supplies it to the space as cold air to cool the space. More specifically, the air conditioner 1 cools the air by extracting heat from the air through heat exchange between the air, which is an example of a target object, and the refrigerant passing through a cooler (details will be described later using Figure 2) built into the refrigerant circuit 10. The cooled air is then supplied to the space as cold air from an air outlet of the indoor unit or the like (not shown), to cool the space.
  • the control unit 50 controls the circulation of the refrigerant in the refrigerant circuit 10 by sending control signals to each device included in the refrigerant circuit 10. It also controls the amount of cool air that the air conditioning device 1 supplies to the space.
  • the control unit 50 according to this embodiment has, for example, an operation panel or a controller that accepts operations from a user, and performs control according to operation input from the user, such as temperature setting and air volume setting. It also has, for example, a temperature sensor that measures the temperature of the space, and performs control according to the measured value. It also has, for example, a temperature sensor that measures the temperature of the refrigerant in the refrigerant circuit 10, and performs control according to the measured value. Additionally, the control unit 50 may acquire information relating to the operation of each device included in the refrigerant circuit 10, such as an effective value of the operation in response to a control value, and perform control according to the acquired information.
  • the refrigerant circuit 10 is a circuit that establishes a refrigeration cycle of the refrigerant as the refrigerant circulates, and enables cooling of an object by heat exchange with the refrigerant. More specifically, the refrigerant circuit 10 according to the present embodiment establishes a refrigeration cycle of the carbon dioxide refrigerant by circulating the carbon dioxide refrigerant, which is an example of a refrigerant, while adjusting the specific enthalpy and pressure, and enables cooling of the air by extracting heat from the air through heat exchange on the low pressure side.
  • the carbon dioxide refrigerant circulating through the refrigerant circuit 10 may be simply referred to as the "refrigerant".
  • the refrigerant circuit 10 not only the refrigerant but also a fluid other than the refrigerant, such as a lubricating oil for ensuring lubrication in the compressor, which will be described later, may circulate.
  • FIG. 2 is a schematic diagram of the refrigerant circuit 10 according to the first embodiment.
  • a refrigerant circuit 10 according to the first embodiment includes compressors 12, 13 that compress a refrigerant, a radiator 14 that extracts heat from the refrigerant and radiates the heat, a refrigerant-refrigerant heat exchanger 17 that performs heat exchange between the refrigerants, electric valves 16, 18 whose opening degree can be adjusted, and a cooler 19 that cools air by heat exchange with the refrigerant passing through it.
  • the refrigerant circuit 10 also includes a temperature sensor 501 that measures the temperature of the refrigerant compressed by the compressor 12 and discharged, and a temperature sensor 502 that measures the temperature of the refrigerant compressed by the compressor 13.
  • the refrigerant circuit 10 may also include a pressure sensor and a temperature sensor that measure the pressure and temperature of the refrigerant at each point, a receiver that can store the refrigerant, a pressure switch as a protection mechanism, a filter, a heat sink, an oil separator, and the like.
  • the lines connecting the devices are flow paths through which the refrigerant flows, and are, for example, metal pipes.
  • the flow paths of the refrigerant circuit 10 are provided with a branching section 15 that branches the flow paths and a merging section 20 that merges the flow paths.
  • the section from the compressor 12 to the branching section 15 is referred to as a first flow path 101
  • the section from the motor-operated valve 16 to the compressor 13 is referred to as a second flow path 102
  • the section from the compressor 13 to the merging section 20 is referred to as a third flow path 103
  • the section from the motor-operated valve 18 to the compressor 12 is referred to as a fourth flow path 104.
  • each flow path may be formed of a single seamless pipe, or may be formed by connecting two or more pipes by a flange structure (not shown).
  • various devices may be included in the middle of the flow path.
  • the compressor 12 is a device that compresses the refrigerant drawn from the fourth flow path 104 and discharges the refrigerant to the first flow path 101.
  • the compressor 13 is a device that compresses the refrigerant drawn from the second flow path 102 and discharges the refrigerant to the third flow path 103.
  • the mechanisms of the compressors 12 and 13 are not limited, and various mechanisms such as an oscillating type, a scroll type, or a rotary type may be used.
  • the operating frequency and the amount of sucked/discharged refrigerant are controlled according to a control signal from the control unit 50.
  • the "operating frequency” refers to the frequency of operation of the parts for compressing the refrigerant performed within the compressor. Specifically, for example, it is the frequency of oscillation of an oscillator in an oscillatory compressor, or the frequency of rotation of a rotor in a scroll compressor or a rotary compressor.
  • the compressor 12 is an example of a first compression element
  • the compressor 13 is an example of a second compression element.
  • the radiator 14 is a device provided in the first flow path 101, which extracts heat from the refrigerant by heat exchange between the passing refrigerant and a fluid such as air or water, and radiates the heat.
  • the radiator 14 is provided between the junction 20 and the branching portion 15 in the first flow path 101.
  • various types of heat exchangers such as a tube-type heat exchanger or a plate-type heat exchanger, can be used.
  • the fluid that has exchanged heat with the refrigerant is heated by the heat extracted from the refrigerant.
  • air may be used as the fluid, and the heated air may be supplied to the space as hot air to be used for space heating.
  • water may be used as the fluid, and the heated water may be supplied to a user to be used for hot water supply.
  • the radiator 14 can also be used as a heater that heats the fluid.
  • the motor-operated valves 16 and 18 are configured to include a valve such as a ball valve and a motor for driving the valve, and the motor adjusts the valve opening to adjust the pressure of the refrigerant flowing. More specifically, the motor-operated valve 16 is provided between the first branch 151 and the second flow path 102, and reduces the pressure of the refrigerant flowing from the first branch 151 by throttling and expanding the refrigerant according to the valve opening, and then flows it to the second flow path 102.
  • a valve such as a ball valve and a motor for driving the valve
  • the motor-operated valve 18 is provided between the refrigerant-refrigerant heat exchanger 17 and the cooler 19 in the second branch 152, and reduces the pressure of the refrigerant flowing from the refrigerant-refrigerant heat exchanger 17 side by throttling and expanding the refrigerant according to the valve opening, and then flows it to the cooler 19 side.
  • the opening of the motor-operated valve 16 and the opening of the motor-operated valve 18 are adjusted by driving and controlling the respective motors according to a control signal from the control unit 50.
  • the motor-operated valves 16, 18 have flow resistance according to their respective openings. The flow resistance is an index of how difficult it is for the refrigerant to flow through the motor-operated valves 16, 18.
  • the motor-operated valve 16 is an example of a first pressure reducing element
  • the motor-operated valve 18 is an example of a second pressure reducing element.
  • a solenoid valve that drives a valve using a solenoid may be used.
  • the refrigerant-refrigerant heat exchanger 17 is a device that performs heat exchange between the refrigerant flowing through the second flow path 102 and the refrigerant flowing through the second branch 152. More specifically, the refrigerant-refrigerant heat exchanger 17 performs heat exchange between the refrigerant that branches into the first branch 151 at the branching section 15 and flows through the second flow path 102 in a state where the pressure is reduced by the motor-operated valve 16, and the refrigerant that branches into the second branch 152 at the branching section 15.
  • the refrigerant flowing through the second flow path 102 extracts heat from the refrigerant flowing through the second branch 152, and as a result, the refrigerant flowing through the second branch 152 is cooled.
  • the cooler 19 is provided in the fourth flow path 104 and is a device that extracts heat from the air and cools the air by heat exchange between the refrigerant passing through the cooler 19.
  • a heat exchanger such as a tube-type heat exchanger can be used.
  • the air exchanges heat with the refrigerant in the cooler 19, and the cooled air is supplied to a space through an air passage (not shown) to cool the space. In this way, the cooling function of the air conditioner 1 (see FIG. 1 ) is realized.
  • the refrigerant (position 10a) after passing through the cooler 19 and cooling the air is compressed by the compressor 12 and discharged into the first flow path 101 (position 10b).
  • the refrigerant discharged into the first flow path 101 is merged with the third flow path 103 at the merging section 20 (position 10c), passes through the radiator 14 to dissipate heat, and then branches into the first branch 151 and the second branch 152 at the branching section 15 (position 10d).
  • the refrigerant branched into the first branch 151 is depressurized by the motor-operated valve 16 and flows into the second flow path 102 (position 10g), and exchanges heat with the refrigerant branched into the second branch 152 in the refrigerant-refrigerant heat exchanger 17 (position 10h). Then, the refrigerant is compressed by the compressor 13 and discharged into the third flow path 103 (position 10i), and merges with the first flow path 101 at the junction 20 (position 10c).
  • the refrigerant (position 10e) after branching into the second branch 152 and exchanging heat in the refrigerant-refrigerant heat exchanger 17 is decompressed by the motor-operated valve 18 (position 10f), and passes through the cooler 19 to cool the air (position 10a).
  • the refrigerant circuit 10 establishes a refrigeration cycle of the refrigerant.
  • FIGS. 3 is a pressure-specific enthalpy diagram illustrating a refrigeration cycle 300 of a refrigerant circulating through the refrigerant circuit 10 according to the first embodiment.
  • the horizontal axis represents specific enthalpy [kJ/kg]
  • the vertical axis represents absolute pressure [MPa.abs] based on an absolute vacuum.
  • the refrigeration cycle 300 is indicated by a thick line. Points 10a to 10i on the refrigeration cycle 300 correspond to positions 10a to 10i of the refrigerant circuit 10 shown in Fig. 2, respectively.
  • Fig. 3 also indicates a saturated liquid line 301, a saturated vapor line 302, a critical point 303, and a 45°C isotherm 304 of the carbon dioxide refrigerant.
  • the refrigerant compressed by the compressor 12 and having acquired the heat of compression is discharged into the first flow path 101, so that the pressure and specific enthalpy of the refrigerant rise from position 10a to position 10b in the refrigeration cycle 300.
  • the third flow path 103 joins at the joining section 20, so that the specific enthalpy of the refrigerant changes from position 10b to position 10c.
  • the refrigerant after joining releases heat by heat exchange with the fluid in the radiator 14, so that the specific enthalpy of the refrigerant drops from position 10c to position 10d.
  • the refrigerant at position 10c is pressurized and heated by the compressors 12 and 13, and reaches a high temperature of, for example, more than 45°C. Therefore, even if the fluid with which the heat exchange takes place in the radiator 14 is at room temperature (15°C to 25°C), it can still take heat from the refrigerant.
  • the first branch 151 branched off at the branching section 15 is depressurized by the motor-operated valve 16 and flows into the second flow path 102, so the pressure of the refrigerant drops from position 10d to position 10g.
  • the temperature of the refrigerant flowing through the second flow path 102 drops and becomes lower than the temperature of the refrigerant flowing through the second branch 152.
  • the refrigerant flowing through the second flow path 102 absorbs heat from the refrigerant in the first branch 151 through heat exchange with the refrigerant in the first branch 151 in the refrigerant-refrigerant heat exchanger 17, and the specific enthalpy rises from position 10g to position 10h.
  • the refrigerant in the second branch 152 loses heat through heat exchange, so the specific enthalpy drops from position 10d to position 10e.
  • the refrigerant in the second branch 152 after passing through the refrigerant-refrigerant heat exchanger 17 is depressurized by the motor-operated valve 18, and the pressure of the refrigerant decreases from position 10e to position 10f. Then, the depressurized refrigerant exchanges heat with the air in the cooler 19 to remove heat, and the specific enthalpy of the refrigerant increases from position 10f to position 10a.
  • the refrigerant at position 10f is in a state where it has been depressurized and cooled by the motor-operated valve 18, and is at a sufficiently low temperature relative to the air to be cooled. Therefore, in the cooler 19, it is possible to remove heat from the air with which it exchanges heat.
  • the refrigerant in the second flow path 102 is compressed by the compressor 13 and acquires heat of compression, so that the pressure and specific enthalpy of the refrigerant increase from position 10h to position 10i.
  • the refrigeration cycle 300 of the refrigerant circuit 10 is established.
  • the refrigerant that cools the air in the cooler 19 has had heat removed by heat exchange between refrigerants in the refrigerant-refrigerant heat exchanger 17 before being decompressed by the motor-operated valve 18.
  • the refrigerant that cools the air in the cooler 19 of the refrigerant circuit 10 (position 10f in FIGS. 2 and 3) has a lower specific enthalpy than the refrigerant that cools the air in the cooler 19' of the conventional refrigerant circuit 10' (position 10f' in FIG. 8).
  • the amount of heat removed by the refrigerant per unit amount in the cooler 19 is larger than in the conventional refrigerant circuit 10' where heat exchange between refrigerants is not performed, and the refrigeration capacity can be ensured without increasing the amount of refrigerant circulating.
  • the carbon dioxide refrigerant becomes supercritical in part of the refrigeration cycle 300, and the change in density of the refrigerant associated with the change in refrigerant pressure is greater than when the refrigerant is not in a supercritical state. Therefore, a larger refrigeration capacity can be ensured for the compression work of the compressors 12 and 13 than when the refrigerant does not go through a supercritical state. This is also true for the refrigerant circuits of the second to fourth embodiments described below.
  • Table 1 shows the capacities and coefficients of performance (COP) of the compressors 12, 13/12', 13' in the air conditioner 1 using the refrigerant circuit 10 according to the first embodiment and in an air conditioner using a conventional refrigerant circuit 10'.
  • the COP is a value obtained by dividing the cooling effect of the cooler 17/17' of the refrigerant circuit 10/10' by the power consumption related to the operation of the refrigerant circuit 10/10', and corresponds to the efficiency of the cooling effect relative to the power consumption.
  • control unit 50 (see FIG. 1) of the air conditioning apparatus 1 may control the circulation of the refrigerant based on the temperature of the refrigerant measured by the temperature sensors 501, 502 (see FIG. 2). For example, when the refrigerant temperature measured by the temperature sensor 501 is higher than the refrigerant temperature measured by the temperature sensor 502, the control unit 50 may control the motor-operated valve 16 to decrease the opening degree so as to increase the flow resistance. Also, when the refrigerant temperature measured by the temperature sensor 501 is higher than the refrigerant temperature measured by the temperature sensor 502, the control unit 50 may control the amount of refrigerant sucked into the compressor 13 to increase the flow rate of the refrigerant in the compressor 13.
  • the enthalpy difference between the refrigerant compressed by the compressor 12 (position 10b in FIG. 2) and the refrigerant compressed by the compressor 13 (position 10i in FIG. 2) is reduced.
  • the compression ratio in the compressor 13 can be set to a large value.
  • the positions at which the temperature sensors 501, 502 used for control are provided are not limited to the positions illustrated in FIG. 2 , and it is sufficient that the temperature sensor 501 is provided at a position before the first flow path 101 passes through the heat sink 14 and before the third flow path 103 joins at the junction 20, and the temperature sensor 502 is provided at a position before the first flow path 101 joins at the junction 20.
  • FIG. 4 is a schematic diagram of a refrigerant circuit 10-2 according to the second embodiment.
  • the refrigerant circuit 10-2 according to the second embodiment differs from the refrigerant circuit 10 according to the first embodiment only in that a radiator 21 is provided in the third flow path 103, and that the junction 20 merges the third flow path 103 at a position after the first flow path 101 has passed through the radiator 14. Therefore, configurations common to the refrigerant circuit 10 and the refrigerant circuit 10-2 are denoted by the same names and symbols, and detailed descriptions thereof will be omitted.
  • the radiator 21 is provided in the third flow path 103 and is a device that extracts heat from the refrigerant and radiates the heat by heat exchange between the refrigerant passing through and a fluid such as air or water.
  • the radiator 21 removes heat from the refrigerant compressed by the compressor 13 by heat exchange between the refrigerant compressed by the compressor 13 and the fluid.
  • the radiator 21 may be a heat exchanger similar to the radiator 14. Similarly to the radiator 14, the radiator 21 may also be used as a heater that heats a fluid.
  • the heat sink 21 is an example of a second heat sink.
  • the refrigerant which has passed through the cooler 19 to cool the air, is compressed by the compressor 12 and discharged to the first flow path 101.
  • the refrigerant discharged to the first flow path 101 passes through the radiator 14 to radiate heat, and after the third flow path 103 is merged at the junction 20, the refrigerant branches into the first branch 151 and the second branch 152 at the branching section 15.
  • the refrigerant branched to the first branch 151 is depressurized by the motor-operated valve 16 and flows into the second flow path 102, and exchanges heat with the refrigerant branched to the first branch 151 in the refrigerant-refrigerant heat exchanger 17.
  • the refrigerant is compressed by the compressor 13 and discharged to the third flow path 103, passes through the radiator 21 to radiate heat, and then merges with the first flow path 101 at the junction 20.
  • the refrigerant which branches into the second branch 152 and exchanges heat in the refrigerant-refrigerant heat exchanger 17 is decompressed by the motor-operated valve 18, and then passes through the cooler 19 to cool the air.
  • the refrigerant circuit 10-2 establishes a refrigeration cycle of the refrigerant.
  • the total capacity of the compressors is reduced compared to the case where the conventional refrigerant circuit 10 is used, in which refrigeration capacity is secured by increasing the amount of refrigerant circulating.
  • the confluence section 20 merges the third flow path 103 at a position after passing through the radiator 14 in the first flow path 101, so that the heat dissipation from the radiator 14 can be increased compared to when the third flow path 103 is merged at a position before passing through the radiator 14.
  • the capacity of the compressor 12 is larger than the capacity of the compressor 13. With this configuration, it is possible to increase the heat dissipation from the radiator 14 compared to when the capacity of the compressor 12 is smaller than the capacity of the compressor 13.
  • FIG. 5 is a schematic diagram of a refrigerant circuit 10-3 according to the third embodiment.
  • the refrigerant circuit 10-3 according to the third embodiment differs from the refrigerant circuit 10-2 according to the second embodiment only in that it includes a motor-operated valve 22 that reduces the pressure of the refrigerant after passing through a radiator 21. Therefore, the same names and symbols are used for components common to the refrigerant circuits 10-2 and 10-3, and detailed descriptions thereof will be omitted.
  • the motor-operated valve 22 is provided at a position after the radiator 21 in the third flow path 103, and reduces the pressure of the refrigerant passing therethrough.
  • the motor-operated valve 22 may have a similar configuration to the motor-operated valves 16 and 18 , and the opening degree of the motor-operated valve 22 may be adjusted by the control unit 50 .
  • the motor-operated valve 22 is an example of a third pressure reducing element.
  • the refrigerant which has passed through the cooler 19 to cool the air, is compressed by the compressor 12 and discharged to the first flow path 101.
  • the refrigerant discharged to the first flow path 101 passes through the radiator 14 to radiate heat, and after the third flow path 103 is joined at the junction 20, the refrigerant is branched into the first branch 151 and the second branch 152 at the branching section 15.
  • the refrigerant branched to the first branch 151 is depressurized by the motor-operated valve 16 and flows into the second flow path 102, and exchanges heat with the refrigerant branched to the first branch 151 in the refrigerant-refrigerant heat exchanger 17.
  • the refrigerant is compressed by the compressor 13 and discharged to the third flow path 103, passes through the radiator 21 to radiate heat, and then is further depressurized by the motor-operated valve 22 and merges with the first flow path 101 at the junction 20.
  • the refrigerant which branches into the second branch 152 and exchanges heat in the refrigerant-refrigerant heat exchanger 17 is decompressed by the motor-operated valve 18, and then passes through the cooler 19 to cool the air.
  • the refrigerant circuit 10-3 establishes a refrigeration cycle of the refrigerant.
  • the total capacity of the compressors is reduced compared to the case where the conventional refrigerant circuit 10 is used, in which refrigeration capacity is secured by increasing the amount of refrigerant circulating. Furthermore, in the refrigerant circuit 10-3, the refrigerant compressed by the compressor 13 is decompressed by the motor-operated valve 22, so that the compression ratio in the compressor 13 can be made larger than in the case where the motor-operated valve 22 is not provided.
  • FIG. 6 is a schematic diagram of a refrigerant circuit 10-4 according to the fourth embodiment.
  • the refrigerant circuit 10-4 according to the fourth embodiment differs from the refrigerant circuit 10-2 according to the second embodiment only in that it includes a motor-operated valve 23 that reduces the pressure of the refrigerant after passing through the radiator 14. Therefore, the same names and symbols are used for components common to the refrigerant circuits 10-2 and 10-4, and detailed descriptions thereof will be omitted.
  • the motor-operated valve 23 is provided at a position in the first flow path 101 after the first flow path 101 has passed through the radiator 14 and before the first flow path 101 joins with the third flow path 103 at the joining portion 20, and reduces the pressure of the refrigerant passing therethrough.
  • the motor-operated valve 23 may have a similar configuration to the motor-operated valves 16 , 18 , and 22 , and the opening degree of the motor-operated valve 23 may be adjusted by the control unit 50 .
  • the motor-operated valve 23 is an example of a fourth pressure reducing element.
  • the refrigerant which has passed through the cooler 19 to cool the air, is compressed by the compressor 12 and discharged to the first flow path 101.
  • the refrigerant discharged to the first flow path 101 passes through the radiator 14 to radiate heat, and is depressurized by the motor-operated valve 23. Then, after the third flow path 103 joins at the confluence 20, the refrigerant branches into the first branch 151 and the second branch 152 at the branching section 15.
  • the refrigerant branched into the first branch 151 is depressurized by the motor-operated valve 16 and flows into the second flow path 102, and exchanges heat with the refrigerant branched into the second branch 152 in the refrigerant-refrigerant heat exchanger 17. Then, the refrigerant is compressed by the compressor 13 and discharged to the third flow path 103, passes through the radiator 21 to radiate heat, and then joins the first flow path 101 at the confluence 20.
  • the refrigerant which branches into the second branch 152 and exchanges heat in the refrigerant-refrigerant heat exchanger 17 is decompressed by the motor-operated valve 18, and then passes through the cooler 19 to cool the air. By circulating the refrigerant in this manner, the refrigerant circuit 10-4 establishes a refrigeration cycle of the refrigerant.
  • the total capacity of the compressors is reduced compared to the case where the conventional refrigerant circuit 10 is used, in which refrigeration capacity is ensured by increasing the amount of refrigerant circulating. Furthermore, in the refrigerant circuit 10-4, the refrigerant compressed by the compressor 12 is decompressed by the motor-operated valve 23, so that the compression ratio in the compressor 12 can be made larger than in the case where the motor-operated valve 23 is not provided.
  • the air conditioning device 1 may switch between a cooling function that supplies cold air to a space to cool the space, and a heating function that supplies warm air to the space to heat the space.
  • a cooling function that supplies cold air to a space to cool the space
  • a heating function that supplies warm air to the space to heat the space.
  • the refrigerant circuit of the application example includes a switching means for switching the cooler 19 (see Figures 2, 4 to 6) in the above-described embodiment between a state in which it functions as a heat exchanger that cools air in the cooling function and a state in which it functions as a heat exchanger that heats air in the heating function.
  • FIG. 7 is a diagram for explaining a refrigerant circuit 10-5 of an application example.
  • the refrigerant circuit 10-5 of the application example differs from the refrigerant circuit 10 according to the first embodiment only in that it includes a four-way switching valve 60 that switches the connection relationship of the four flow paths. Therefore, the same names and symbols are used for components common to the refrigerant circuit 10 and the refrigerant circuit 10-5, and detailed descriptions thereof will be omitted.
  • the four-way switching valve 60 is provided to connect a flow path from the cooler 19 to the compressor 12 and a flow path from the junction 20 to the radiator 14. Then, under the control of the control unit 50, the connection relationship of the flow paths is switched between a first state in which the cooler 19 and the compressor 12 are connected and the junction 20 and the radiator 14 are connected, and a second state in which the cooler 19 and the junction 20 are connected and the compressor 12 and the radiator 14 are connected.
  • the four-way switching valve 60 is an example of a switching means, and switching may be performed using other configurations.
  • the refrigerant circuit 10-5 in the first state the refrigerant circulates in the same manner as in the refrigerant circuit 10 described using Fig. 2, and the air that is the counterpart of the heat exchange in the cooler 19 is cooled. In this way, the cooling function of the air conditioner 1 is realized.
  • the refrigerant circuit 10-5 in the second state the refrigerant circulates in a manner different from that in the first state, and the pressure and specific enthalpy of the refrigerant change in a path opposite to that of the refrigeration cycle 300 described with reference to Fig. 3. More specifically, the refrigerant compressed by the compressors 12 and 13 merges at the merger section 20 and then passes through the cooler 19.
  • the refrigerant passing through the cooler 19 is in a state in which it has been pressurized and heated by the compressors 12 and 13, and is at a sufficiently high temperature relative to the air with which it exchanges heat. Therefore, the air with which it exchanges heat in the cooler 19 is heated by removing heat from the refrigerant. This realizes the heating function of the air-conditioning device 1.
  • a switching means is applied to the refrigerant circuit 10 according to the first embodiment, and is shown as an application example refrigerant circuit 10-5, but a similar switching means can also be applied to the refrigerant circuits 10-2, 10-3, and 10-4 according to the second, third, and fourth embodiments.
  • the control unit 50 may control the circulation of the refrigerant based on the temperature of the refrigerant measured by temperature sensors 501, 502 (see Figures 2, 4 to 7).
  • the refrigeration cycle device is applied to the air conditioner 1, but the scope of application is not limited.
  • the refrigeration cycle device may be applied to various devices that cool objects, such as a freezer, a refrigerator, or an ice maker.
  • the refrigeration cycle device may be applied to various devices that heat objects, such as a heater, a water heater, or a water heater, by utilizing heat dissipation from the radiator 14.
  • carbon dioxide refrigerant has been given as an example of the refrigerant circulating through each refrigerant circuit, the type of refrigerant is not limited.
  • a mixed refrigerant in which carbon dioxide is mixed with other components may be used, or a single refrigerant or mixed refrigerant that does not contain carbon dioxide may be used.
  • the heat dissipation in the radiators 14, 21 is greater than when a non-azeotropic mixed refrigerant that does not contain carbon dioxide is used.
  • first compression element and the second compression element may be integrated into one device, and the operation for compression in each compression element may be realized by a common motor or the like.
  • each compression element can be individually controlled according to the state of the refrigerant being sucked in, etc.
  • a plurality of compressors connected in parallel may be used in place of the compressor 12, and a plurality of compressors connected in parallel may be used in place of the compressor 13. In this case, too, the total capacity can be made smaller than in the case where the refrigerant circulation amount is increased in the conventional refrigerant circuit 10' to ensure refrigeration capacity.
  • motorized valves or solenoid valves are used as pressure reducing elements to enable the control unit 50 to control the opening degree. If control by the control unit 50 is not performed, capillary tubes, orifice plates, etc. may be used for each pressure reducing element.
  • the refrigerant is illustrated as being split into two branches, the first branch 151 and the second branch 152, but it may be split into three or more branches including the first branch 151 and the second branch 152.
  • a plurality of flow paths including the third flow path 103 may merge into the first flow path 101. Note that when branching into three or more branches, the branching may occur at a plurality of branching parts including the branching part 15, and the merging may occur at a plurality of merging parts including the merging part 20.
  • the air-conditioning apparatus 1 of the above-described embodiment includes a compressor 12 that compresses the sucked refrigerant and discharges it to a first flow path 101, a radiator 14 that is provided in the first flow path 101 and passes the refrigerant through and radiates heat extracted from the passing refrigerant, a branching section 15 that branches the refrigerant after passing through the radiator 14 in the first flow path 101 into a first branch 151 and a second branch 152, an electric valve 16 that reduces the pressure of the refrigerant branched into the first branch 151 and flows it into the second flow path 102, and a refrigerant-refrigerant heat exchanger 17 that exchanges heat between the refrigerant flowing through the second flow path 102 and the refrigerant branched into the second branch 152.
  • the refrigerant circuits 10, 10-2, 10-3, 10-4, and 10-5 include a refrigerant exchanger 17, an electric valve 18 that reduces the pressure of the refrigerant after heat exchange in the refrigerant-refrigerant heat exchanger 17 in the second branch 152, a cooler 19 that cools the air by heat exchange between the refrigerant after pressure reduction by the electric valve 18 and the air and causes the refrigerant after heat exchange to be drawn into the compressor 12, a compressor 13 that draws in the refrigerant after heat exchange in the refrigerant-refrigerant heat exchanger 17 in the second flow path 102, compresses it, and discharges it into the third flow path 103, and a junction section 20 that merges the third flow path 103 with the first flow path 101.
  • the total capacity of the compressors 12 and 13 is suppressed compared to an air conditioner equipped with a conventional refrigerant circuit 10' that ensures refrigeration capacity by increasing the amount of refrigerant circulating.
  • the confluence 15 merges the third flow path 103 at a position in the first flow path 101 after it has passed through the radiator 14.
  • the third flow path 103 is also provided with a radiator 21 that radiates heat extracted by passing refrigerant compressed by the compressor 13 through it.
  • the amount of heat dissipated from the radiator 14 can be increased compared to when the confluence 15 merges the third flow path 103 at a position in the first flow path 101 before it has passed through the radiator 14.
  • the capacity of the compressor 12 is larger than the capacity of the compressor 13. In this case, the amount of heat dissipated from the radiator 14 can be increased compared to when the capacity of the compressor 12 is smaller than the capacity of the compressor 13.
  • a motor-operated valve 22 that reduces the pressure of the refrigerant after passing through the radiator 21 is provided in the third flow path 103.
  • the compression ratio of the compressor 13 can be set to a large value.
  • a motor-operated valve 23 that reduces the pressure of the refrigerant after passing through the radiator 14 is provided in the first flow path 101 at a position after the refrigerant has passed through the radiator 14 and before the junction 20 joins with the third flow path 103.
  • the compression ratio of the compressor 12 can be set to a large value.
  • the air conditioning device 1 of the above-mentioned embodiment a carbon dioxide refrigerant is used.
  • the amount of heat dissipated in the radiator 14 is greater than when a non-azeotropic refrigerant that does not contain carbon dioxide is used.
  • temperature sensors 501, 502 for measuring the temperature of the refrigerant are provided at a position in the first flow path 101 before passing through the radiator 14 and before the third flow path 103 merges at the junction 15, and at a position in the third flow path 103 before the refrigerant merges with the first flow path 101 at the junction 15.
  • the control unit 50 of the air conditioning device 1 may control the flow resistance of the motor-operated valve 16 to increase when the temperature of the refrigerant measured by the temperature sensor 501 is higher than the temperature of the refrigerant measured in the third flow path 103. In this case, the enthalpy difference between the refrigerant compressed by the compressor 12 and the refrigerant compressed by the compressor 13 becomes smaller.
  • control unit 50 may control the flow rate of the compressor 13 to increase when the temperature of the refrigerant measured in the first flow path 101 is higher than the temperature of the refrigerant measured in the third flow path 103.
  • the enthalpy difference between the refrigerant compressed by the compressor 12 and the refrigerant compressed by the compressor 13 becomes smaller.

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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)

Abstract

Le problème décrit par la présente invention est de limiter la capacité totale d'un compresseur par rapport à un cas dans lequel la capacité de réfrigération est maintenue en augmentant une quantité de circulation de fluide frigorigène. La solution selon l'invention porte sur un dispositif à cycle de réfrigération qui comprend : un premier élément de compression pour comprimer un fluide frigorigène aspiré et le décharger vers un premier trajet d'écoulement ; un dissipateur thermique disposé dans le premier trajet d'écoulement et à travers lequel passe un fluide frigorigène pour dissiper la chaleur extraite du fluide frigorigène passant ; une partie de ramification pour amener le fluide frigorigène qui a traversé le dissipateur thermique dans le premier trajet d'écoulement à se ramifier à une première branche et à une seconde branche ; un premier élément de réduction de pression pour réduire la pression du fluide frigorigène ramifié à la première branche et amener le fluide frigorigène à s'écouler vers le deuxième trajet d'écoulement ; un échangeur thermique pour provoquer l'échange de chaleur entre le fluide frigorigène s'écoulant à travers le deuxième trajet d'écoulement et le fluide frigorigène ramifié vers la seconde branche ; un second élément de réduction de pression pour réduire la pression du fluide frigorigène après échange de chaleur au moyen de l'échangeur thermique dans la seconde branche ; un refroidisseur pour refroidir un objet au moyen d'un échange de chaleur entre le fluide frigorigène après réduction de pression au moyen du second élément de réduction de pression et de l'objet et amener le fluide frigorigène après échange de chaleur à être aspiré dans le premier élément de réduction de pression ; un second élément de compression pour aspirer le fluide frigorigène après échange de chaleur au moyen de l'échangeur thermique dans le deuxième trajet d'écoulement, comprimer le fluide frigorigène et évacuer le fluide frigorigène vers un troisième trajet d'écoulement ; et une partie de fusion pour fusionner le troisième trajet d'écoulement avec le premier.
PCT/JP2024/011724 2023-03-31 2024-03-25 Dispositif à cycle de réfrigération Pending WO2024204077A1 (fr)

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JPS5941746A (ja) * 1982-08-31 1984-03-08 三菱電機株式会社 冷凍装置
JPH03294754A (ja) * 1990-04-11 1991-12-25 Daikin Ind Ltd 空気調和装置
JPH05346267A (ja) * 1992-06-16 1993-12-27 Daikin Ind Ltd 空気調和装置
JP2000329416A (ja) * 1999-03-15 2000-11-30 Denso Corp 冷凍サイクル
JP2005061784A (ja) * 2003-08-20 2005-03-10 Yanmar Co Ltd エンジンヒートポンプ
US20070017240A1 (en) * 2005-07-19 2007-01-25 Hussmann Corporation Refrigeration system with mechanical subcooling
JP2009539058A (ja) * 2006-06-01 2009-11-12 キャリア コーポレイション 冷凍システム用の多段圧縮機ユニット
WO2010137120A1 (fr) * 2009-05-26 2010-12-02 三菱電機株式会社 Dispositif d'alimentation en eau chaude du type pompe à chaleur
JP2013124820A (ja) * 2011-12-15 2013-06-24 Ryohei Iwatani ２段式暖房機及び２段式冷房機
JP5758818B2 (ja) 2012-02-15 2015-08-05 株式会社日立製作所 圧縮機システムおよびその運転制御方法

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JPS60226669A (ja) * 1984-04-24 1985-11-11 三洋電機株式会社 冷凍装置

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Publication number Priority date Publication date Assignee Title
JPS5941746A (ja) * 1982-08-31 1984-03-08 三菱電機株式会社 冷凍装置
JPH03294754A (ja) * 1990-04-11 1991-12-25 Daikin Ind Ltd 空気調和装置
JPH05346267A (ja) * 1992-06-16 1993-12-27 Daikin Ind Ltd 空気調和装置
JP2000329416A (ja) * 1999-03-15 2000-11-30 Denso Corp 冷凍サイクル
JP2005061784A (ja) * 2003-08-20 2005-03-10 Yanmar Co Ltd エンジンヒートポンプ
US20070017240A1 (en) * 2005-07-19 2007-01-25 Hussmann Corporation Refrigeration system with mechanical subcooling
JP2009539058A (ja) * 2006-06-01 2009-11-12 キャリア コーポレイション 冷凍システム用の多段圧縮機ユニット
WO2010137120A1 (fr) * 2009-05-26 2010-12-02 三菱電機株式会社 Dispositif d'alimentation en eau chaude du type pompe à chaleur
JP2013124820A (ja) * 2011-12-15 2013-06-24 Ryohei Iwatani ２段式暖房機及び２段式冷房機
JP5758818B2 (ja) 2012-02-15 2015-08-05 株式会社日立製作所 圧縮機システムおよびその運転制御方法

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Title
See also references of EP4462037A4

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CN120548445A (zh) 2025-08-26
JP2024145834A (ja) 2024-10-15
JP7698215B2 (ja) 2025-06-25
EP4462037A1 (fr) 2024-11-13

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