EP3954947B1 - Ausseneinheit, kältekreislaufvorrichtung und kältemaschine - Google Patents

Ausseneinheit, kältekreislaufvorrichtung und kältemaschine Download PDF

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Publication number
EP3954947B1
EP3954947B1 EP19923884.1A EP19923884A EP3954947B1 EP 3954947 B1 EP3954947 B1 EP 3954947B1 EP 19923884 A EP19923884 A EP 19923884A EP 3954947 B1 EP3954947 B1 EP 3954947B1
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EP
European Patent Office
Prior art keywords
refrigerant
flow path
passage
expansion valve
temperature
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EP19923884.1A
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English (en)
French (fr)
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EP3954947A4 (de
EP3954947A1 (de
Inventor
Tomotaka Ishikawa
Yusuke Arii
Motoshi HAYASAKA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • 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
    • F25B2400/16—Receivers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2103—Temperatures near a heat exchanger
    • 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

Definitions

  • the present invention relates to an outdoor unit of a refrigeration cycle apparatus, a refrigeration cycle apparatus, and a refrigerating machine.
  • Japanese Patent Laying-Open No. 2017-187189 discloses a refrigeration apparatus that prevents refrigerant discharged from a compressor from having an excessively high temperature by controlling a torque for a motor embedded in the compressor.
  • Patent US 2015/096321 A1 discloses a refrigeration apparatus which uses R32 as a refrigerant, and includes a compressor, a condenser, an expansion mechanism, an evaporator, an intermediate injection channel and a suction injection channel.
  • the intermediate injection channel guides a part of the refrigerant flowing from the condenser toward the evaporator to the compressor, causing the refrigerant to merge with intermediate-pressure refrigerant of the compressor.
  • the suction injection channel guides a part of the refrigerant flowing from the condenser toward the evaporator to the suction passage, causing the refrigerant to merge with low-pressure refrigerant sucked into the compressor.
  • Patent JP 2010 127531 A discloses a refrigeration air conditioner which has a compressor, a condenser, a plurality of capillary tubes, an evaporator equipped with heat transfer tubes of the same number as that of the capillary tubes, and a main circuit forming a refrigerating cycle connecting them to circulate the refrigerant.
  • the air conditioner also has a bypass circuit making branch points communicate with each other provided between the condenser and the capillary tubes with a junction provided between the evaporator and the compressor.
  • a bypass electromagnetically operated valve, a bypass receiver, a bypass decompressing means are sequentially installed in the bypass circuit.
  • a controller when the pressure of a delivered refrigerant of the compressor measured by a pressure sensor reaches control upper limit pressure, the bypass electromagnetically operated valve is opened, the refrigerants are sent into the capillary tubes and the bypass circuit, and the high pressure is lowered.
  • an intermediate pressure injection circuit in which an internal heat exchanger is provided to increase a subcool, and refrigerant on a cooling side is returned to an intermediate pressure port of a compressor, in order to improve performance.
  • an intermediate pressure is also high, and thus it becomes difficult to ensure a subcool by the internal heat exchanger. Accordingly, the capability of the refrigeration cycle apparatus may be degraded.
  • An object of the present disclosure is to provide an outdoor unit, a refrigeration cycle apparatus, and a refrigerating machine capable of ensuring a subcool of refrigerant at an inlet portion of a load device even when an evaporation temperature is high.
  • An outdoor unit in accordance with the present invention is an outdoor unit of a refrigeration cycle apparatus, the outdoor unit being connectable to a load device including a first expansion valve and an evaporator.
  • the outdoor unit includes, among other things: a compressor having a suction port, a discharge port, and an intermediate pressure port; a condenser; a heat exchanger; and a second expansion valve.
  • the heat exchanger has a first passage and a second passage, and is configured to exchange heat between refrigerant flowing in the first passage and the refrigerant flowing in the second passage.
  • the load device and a flow path from the compressor to the second expansion valve via the condenser and the first passage of the heat exchanger form a circulation flow path through which the refrigerant circulates.
  • the outdoor unit further includes: a first refrigerant flow path configured to cause the refrigerant to flow from a portion of the circulation flow path between an outlet of the first passage and the second expansion valve to an inlet of the second passage; a third expansion valve disposed on the first refrigerant flow path; a second refrigerant flow path configured to cause the refrigerant to flow from an outlet of the second passage to the suction port or the intermediate pressure port of the compressor; and a flow path switching unit disposed on the second refrigerant flow path and configured to switch, to one of the suction port and the intermediate pressure port, a destination of the refrigerant flowing out from the outlet of the second passage.
  • the flow path switching unit is controlled by a controller configured as specified by appended independent claim 1.
  • a subcool of liquid refrigerant delivered from the outdoor unit to the load device can be ensured even when an evaporation temperature changes, and thereby degradation of refrigeration capability can be prevented.
  • Fig. 1 is an overall configuration diagram of a refrigeration cycle apparatus. It should be noted that Fig. 1 functionally shows the connection relation and the arrangement configuration of devices in the refrigeration cycle apparatus, and does not necessarily show an arrangement in a physical space.
  • a refrigeration cycle apparatus 1 includes an outdoor unit 2, a load device 3, and extension pipes 84 and 88.
  • Outdoor unit 2 is an outdoor unit of refrigeration cycle apparatus 1, the outdoor unit being connectable to load device 3.
  • Outdoor unit 2 includes a compressor 10 having a suction port G1, a discharge port G2, and an intermediate pressure port G3, a condenser 20, a fan 22, a heat exchanger 30, a second expansion valve 40, and pipes 80 to 83 and 89.
  • Heat exchanger 30 has a first passage H1 and a second passage H2, and is configured to exchange heat between refrigerant flowing in first passage H1 and the refrigerant flowing in second passage H2.
  • Load device 3 includes a first expansion valve 50, an evaporator 60, and pipes 85, 86, and 87.
  • First expansion valve 50 is, for example, a temperature expansion valve controlled independently of outdoor unit 2.
  • Compressor 10 compresses the refrigerant suctioned from pipes 89 and 97, and discharges the compressed refrigerant to pipe 80.
  • Compressor 10 is configured to adjust a rotation speed according to a control signal from a controller 100. By adjusting the rotation speed of compressor 10, a circulation amount of the refrigerant is adjusted, and the capability of refrigeration cycle apparatus 1 can be adjusted.
  • various types of compressors can be adopted, and for example, a compressor of scroll type, rotary type, screw type, or the like can be adopted.
  • Condenser 20 condenses the refrigerant discharged from compressor 10 to pipe 80, and delivers the condensed refrigerant to pipe 81.
  • Condenser 20 is configured such that the high-temperature, high-pressure gas refrigerant discharged from compressor 10 performs heat exchange with outside air (heat dissipation). By this heat exchange, the refrigerant is condensed and transforms into a liquid phase.
  • Fan 22 supplies the outside air with which the refrigerant performs heat exchange in condenser 20, to condenser 20. By adjusting the number of revolutions of fan 22, a refrigerant pressure on a discharge side of compressor 10 (a high pressure-side pressure) can be adjusted.
  • condenser 20 when a device cools the refrigerant in a supercritical state, the device will also be referred to as condenser 20. Further, in the present specification, for ease of description, an amount of decrease from a reference temperature of the refrigerant in the supercritical state will also be referred to as a subcool.
  • a flow path from compressor 10 to second expansion valve 40 via condenser 20 and first passage H1 of heat exchanger 30 and a flow path on which first expansion valve 50 and evaporator 60 of load device 3 are disposed form a circulation flow path through which the refrigerant circulates.
  • this circulation flow path will also be referred to as a "main circuit" of a refrigeration cycle.
  • Outdoor unit 2 further includes a first refrigerant flow path (91 to 94) configured to cause the refrigerant to flow from a portion of the circulation flow path between an outlet of first passage H1 and second expansion valve 40 to an inlet of second passage H2, a second refrigerant flow path (96 to 98) configured to cause the refrigerant to flow from an outlet of second passage H2 to suction port G1 or intermediate pressure port G3 of compressor 10, and a flow path switching unit 74 disposed on the second refrigerant flow path and configured to switch, to one of suction port G1 and intermediate pressure port G3, a destination of the refrigerant flowing out from the outlet of second passage H2.
  • this flow path that branches from the main circuit and delivers the refrigerant to compressor 10 via second passage H2 will be referred to as an "injection flow path".
  • Outdoor unit 2 further includes a receiver 73 disposed on the first refrigerant flow path and configured to store the refrigerant, a third expansion valve 71 disposed on a pipe 91 between an inlet of receiver 73 and the portion of the circulation flow path between the outlet of first passage H1 and second expansion valve 40, a degassing passage 93 provided between a pipe 94 at an outlet of receiver 73 and a gas exhaust outlet of receiver 73 and configured to exhaust a refrigerant gas within receiver 73, and a fourth expansion valve 72 disposed on degassing passage 93.
  • receiver 73 By providing receiver 73 on the injection flow path as described above, it becomes easy to ensure a subcool in pipes 82 and 83 which are liquid pipes. This is because, since receiver 73 generally includes the gas refrigerant therein and a refrigerant temperature reaches a saturation temperature, it is not possible to ensure a subcool if receiver 73 is disposed on pipe 82.
  • receiver 73 is provided at an intermediate pressure portion, it becomes possible to store intermediate pressure liquid refrigerant within receiver 73 even when a high pressure portion of the main circuit is in the supercritical state.
  • a design pressure of a container of receiver 73 can be set to be lower than that of the high pressure portion, and cost reduction by thinning the container can also be achieved.
  • Outdoor unit 2 further includes pressure sensors 110, 111, and 112, temperature sensors 120, 121, and 122, and controller 100 configured to control flow path switching unit 74.
  • Pressure sensor 110 detects a suction pressure PL of compressor 10, and outputs a detection value thereof to controller 100.
  • Pressure sensor 111 detects a discharge pressure PH of compressor 10, and outputs a detection value thereof to controller 100.
  • Pressure sensor 112 detects a pressure P1 in pipe 83 at an outlet of second expansion valve 40, and outputs a detection value thereof to controller 100.
  • outdoor unit 2 can decompress the refrigerant pressure to be lower than or equal to a design pressure of load device 3 (for example, 4 MPa), and then deliver the refrigerant to load device 3.
  • a design pressure of load device 3 for example, 4 MPa
  • load device 3 for example, 4 MPa
  • Temperature sensor 120 detects a discharge temperature TH of compressor 10, and outputs a detection value thereof to controller 100.
  • Temperature sensor 121 detects a refrigerant temperature T1 in pipe 81 at an outlet of condenser 20, and outputs a detection value thereof to controller 100.
  • Temperature sensor 122 detects a refrigerant temperature T2 at the outlet of first passage H1 on a cooled side of heat exchanger 30, and outputs a detection value thereof to controller 100.
  • the second refrigerant flow path includes a pipe 96 connecting between the outlet of second passage H2 of heat exchanger 30 and flow path switching unit 74, and flow path switching unit 74.
  • Flow path switching unit 74 includes pipes 97 and 98 branching from pipe 96, and on-off valves 75 and 76 disposed on pipes 97 and 98, respectively.
  • Pipe 97 is connected between pipe 96 and intermediate pressure port G3.
  • Pipe 98 is connected between pipe 96 and suction port G1.
  • Controller 100 includes a CPU (Central Processing Unit) 102, a memory 104 (a ROM (Read Only Memory) and a RAM (Random Access Memory)), input/output buffers (not shown) for inputting/outputting various signals, and the like.
  • CPU 102 expands programs stored in the ROM onto the RAM or the like and executes the programs.
  • the programs stored in the ROM are programs describing processing procedures of controller 100. According to these programs, controller 100 performs control of the devices in outdoor unit 2. This control can be processed not only by software but also by dedicated hardware (electronic circuitry).
  • Fig. 2 is a flowchart for illustrating control of flow path switching unit 74.
  • controller 100 determines whether or not on-off valve 75 is opened and on-off valve 76 is closed.
  • on-off valve 75 is opened and on-off valve 76 is closed (YES in S1)
  • intermediate pressure port G3 is selected as the destination of the refrigerant flowing through the injection flow path.
  • suction port G1 is selected as the destination of the refrigerant flowing through the injection flow path
  • on-off valve 75 is closed and on-off valve 76 is opened.
  • step S2 controller 100 determines whether or not refrigerant temperature T2 at the outlet of first passage H1 of heat exchanger 30 is higher than or equal to a first temperature Tth1.
  • controller 100 controls flow path switching unit 74 to switch the destination of the refrigerant to suction port G1 in the processing in steps S3 to S7. Also when refrigerant temperature T2 at the outlet of first passage H1 of heat exchanger 30 is equal to first temperature Tth1 (YES in S2), controller 100 controls flow path switching unit 74 to switch the destination of the refrigerant to suction port G1 in the processing in steps S3 to S7.
  • controller 100 controls flow path switching unit 74 to switch the destination of the refrigerant to suction port G1 by sequentially performing the processing in steps S4 to S7.
  • suction air temperature TL of compressor 10 can be obtained by converting suction pressure PL detected by pressure sensor 110.
  • step S4 operation of compressor 10 is stopped.
  • step S5 on-off valve 75 is closed.
  • step S6 on-off valve 76 is opened.
  • step S7 operation of compressor 10 is resumed.
  • controller 100 does not perform switching of flow path switching unit 74 in steps S4 to S7.
  • controller 100 controls flow path switching unit 74 to switch the destination of the refrigerant to intermediate pressure port G3 in the processing in steps S9 to S13. Also when refrigerant temperature T2 is equal to second temperature Tth2 (YES in S8), controller 100 controls flow path switching unit 74 to switch the destination of the refrigerant to intermediate pressure port G3. It should be noted that Tth1 is higher than Tth2.
  • controller 100 controls flow path switching unit 74 to switch the destination of the refrigerant to intermediate pressure port G3 by sequentially performing the processing in steps S10 to S13. It should be noted that TLth1 is higher than TLth2.
  • step S10 operation of compressor 10 is stopped.
  • step S11 on-off valve 76 is closed.
  • step S12 on-off valve 75 is opened.
  • step S13 operation of compressor 10 is resumed.
  • controller 100 maintains flow path switching unit 74 with the destination of the refrigerant being set to suction port G1, and does not perform flow path switching.
  • controller 100 controls flow path switching unit 74 to increase the pressure difference, to switch the destination of the refrigerant from intermediate pressure port G3 to suction port G1. Accordingly, the amount of decompression in third expansion valve 71 can be ensured, and thus the amount of temperature decrease in third expansion valve 71 increases. Thereby, a temperature difference between a refrigerant temperature in first passage H1 and a refrigerant temperature in second passage H2 of heat exchanger 30 can be ensured. Therefore, the amount of heat exchange in heat exchanger 30 increases, and thus refrigerant temperature T2 can be decreased.
  • the flowchart may be modified to perform flow path switching during operation, without performing the processing in steps S4 and S7 of the processing in steps S4 to S7.
  • the flowchart may be modified to perform flow path switching during operation, without performing the processing in steps S10 and S13 of the processing in steps S10 to S13.
  • Fig. 3 is a flowchart for illustrating control of third expansion valve 71.
  • third expansion valve 71 is feedback-controlled such that discharge temperature TH of compressor 10 matches a target temperature. Specifically, when discharge temperature TH of compressor 10 is higher than the target temperature in step S21 (YES in S21), controller 100 increases a degree of opening of third expansion valve 71 in step S22. Thereby, the refrigerant flowing into intermediate pressure port G3 or suction port G1 via receiver 73 increases, and thus discharge temperature TH decreases.
  • controller 100 decreases the degree of opening of third expansion valve 71 in step S24. Thereby, the refrigerant flowing into intermediate pressure port G3 or suction port G1 via receiver 73 decreases, and thus discharge temperature TH increases.
  • controller 100 controls the degree of opening of third expansion valve 71 such that discharge temperature TH of compressor 10 approaches the target temperature.
  • the frequency of changing the degree of opening of third expansion valve 71 may be decreased by setting the target temperature in step S21 to be higher than the target temperature in step S23.
  • Fig. 4 is a flowchart for illustrating control of fourth expansion valve 72.
  • fourth expansion valve 72 is feedback-controlled such that refrigerant temperature T1 at the outlet of condenser 20 matches a target temperature, to ensure the subcool of the refrigerant at the outlet of condenser 20.
  • controller 100 increases a degree of opening of fourth expansion valve 72 in step S32.
  • the gas refrigerant flows out of receiver 73 and the amount of the liquid refrigerant increases, and thus the amount of the refrigerant circulating through the main circuit decreases. Accordingly, the refrigerant temperature increases on the whole and refrigerant temperature T1 increases, and thus subcool SC decreases.
  • controller 100 decreases the degree of opening of fourth expansion valve 72 in step S34.
  • the amount of the gas refrigerant increases and the amount of the liquid refrigerant decreases in receiver 73, and thus the amount of the refrigerant circulating through the main circuit increases. Accordingly, the refrigerant temperature decreases on the whole and refrigerant temperature T1 decreases, and thus subcool SC increases.
  • controller 100 controls the degree of opening of fourth expansion valve 72 such that refrigerant temperature T1 at the outlet of condenser 20 approaches the target temperature.
  • the frequency of changing the degree of opening of fourth expansion valve 72 may be decreased by setting the target value in step S31 to be larger than the target value in step S33.
  • Controller 100 performs control of compressor 10 and second expansion valve 40 to use a supercritical region of the refrigerant. For example, when an outside air temperature is higher than a supercritical temperature of the refrigerant as in summer, controller 100 increases the rotation speed of compressor 10 to be higher than that for spring or autumn, to increase the pressure of the high pressure portion. In this case, the pressure of the high pressure portion of the main circuit increases. In order to allow load device 3 to be used in common with a device used with an ordinary refrigerant, decompression is performed in second expansion valve 40. On this occasion, second expansion valve 40 is controlled as described below.
  • Fig. 5 is a flowchart for illustrating control of second expansion valve 40.
  • second expansion valve 40 is feedback-controlled such that pressure P1 matches a target pressure. Specifically, when pressure P1 is higher than the target pressure in step S41 (YES in S41), controller 100 decreases a degree of opening of second expansion valve 40 in step S42. Thereby, the amount of decompression by second expansion valve 40 increases, and thus pressure P1 decreases.
  • controller 100 increases the degree of opening of second expansion valve 40 in step S44. Thereby, the amount of decompression by second expansion valve 40 decreases, and thus pressure P1 increases.
  • load device 3 can be set to be lower than or equal to a design pressure of the device used with an ordinary refrigerant, and load device 3 can be used in common with a load device for a conventional machine which uses refrigerant such as R410A.
  • refrigeration cycle apparatus 1 may be utilized in an air conditioner or the like.
  • 1 refrigeration cycle apparatus; 2: outdoor unit; 3: load device; 10: compressor; 20: condenser; 22: fan; 30: heat exchanger; 40: second expansion valve; 50: first expansion valve; 60: evaporator; 71: third expansion valve; 72: fourth expansion valve; 73: receiver; 74: flow path switching unit; 75, 76: on-off valve; 80, 81, 82, 83, 85, 89, 91, 94, 96, 97, 98: pipe; 84, 88: extension pipe; 93: degassing passage; 100: controller; 102: CPU; 104: memory; 110, 111, 112: pressure sensor; 120, 121, 122: temperature sensor; G1: suction port; G2: discharge port; G3: intermediate pressure port; H1: first passage; H2: second passage.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Claims (7)

  1. Außeneinheit (2) einer Kältekreislaufvorrichtung (1), wobei die Außeneinheit (2) mit einer Lasteinrichtung (3) verbindbar ist, aufweisend ein erstes Expansionsventil (50) und einen Verdampfer (60), wobei die Außeneinheit (2) umfasst:
    einen Verdichter (10), aufweisend einen Ansauganschluss (G1), einen Auslassanschluss (G2) und einen Zwischendruckanschluss (G3);
    einen Kondensator (20);
    einen Wärmetauscher (30), aufweisend einen ersten Durchgang (H1) und einen zweiten Durchgang (H2), der eingerichtet ist, Wärme zwischen in dem ersten Durchgang (H1) strömendem Kältemittel und in dem zweiten Durchgang (H2) strömendem Kältemittel auszutauschen; und
    ein zweites Expansionsventil (40), wobei die Lasteinrichtung (3) und ein Strömungspfad vom Verdichter (10) zum zweiten Expansionsventil (40) über den Kondensator (20) und den ersten Durchgang (H1) des Wärmetauschers (30) einen Zirkulationsströmungspfad bilden, durch den das Kältemittel zirkuliert,
    die Außeneinheit (2) ferner umfasst:
    einen ersten Kältemittelströmungspfad (91 bis 94), der eingerichtet ist, das Kältemittel zu veranlassen, von einem Abschnitt des Zirkulationsströmungspfads zwischen einem Auslass des ersten Durchgangs (H1) und dem zweiten Expansionsventil (40) zu einem Einlass des zweiten Durchgangs (H2) zu strömen;
    ein drittes Expansionsventil (71), das im ersten Kältemittelströmungspfad angeordnet ist;
    einen zweiten Kältemittelströmungspfad (96 bis 98), der eingerichtet ist, das Kältemittel zu veranlassen, von einem Auslass des zweiten Durchgangs (H2) zu dem Ansauganschluss (G1) oder dem Zwischendruckanschluss (G3) des Verdichters (10) zu strömen;
    eine Strömungspfad-Umschalteinheit (74), die auf dem zweiten Kältemittelströmungspfad angeordnet und eingerichtet ist, ein Ziel des aus dem Auslass des zweiten Durchgangs (H2) ausströmenden Kältemittels auf einen des Ansauganschlusses (G1) und des Zwischendruckanschlusses (G3) umzuschalten; und
    eine Steuereinheit (100), die eingerichtet ist, die Strömungspfad-Umschalteinheit (74) zu steuern;
    dadurch gekennzeichnet, dass
    die Außeneinheit (2) ferner umfasst:
    einen Sammler (73), der auf dem ersten Kältemittelströmungspfad angeordnet und eingerichtet ist das Kältemittel zu speichern;
    einen Entgasungsdurchgang (93), der zwischen einem Auslass des Sammlers (73) und einem Gasausstoßauslass des Sammlers (73) vorgesehen und eingerichtet ist, ein Kältemittelgas innerhalb des Sammlers auszustoßen;
    ein viertes Expansionsventil (72), das in dem Entgasungsdurchgang (93) angeordnet ist,
    wobei
    das dritte Expansionsventil (71) zwischen einem Einlass des Sammlers (73) und dem Abschnitt des Zirkulationsströmungspfades zwischen dem Auslass des ersten Durchgangs (H1) und dem zweiten Expansionsventil (40) angeordnet ist, und
    die Steuereinheit (100) eingerichtet ist, die Strömungspfad-Umschalteinheit (74) so zu steuern, dass sie das Ziel des Kältemittels auf den Ansauganschluss (G1) umschaltet, wenn eine Temperatur am Auslass des ersten Durchgangs (H1) des Wärmetauschers (30) höher als eine erste Temperatur ist.
  2. Außeneinheit nach Anspruch 1, wobei die Steuereinheit (100) eingerichtet ist, dass, wenn die Temperatur am Auslass des ersten Durchgangs (H1) des Wärmetauschers (30) niedriger als eine zweite Temperatur ist, die Steuereinheit (100) die Strömungspfad-Umschalteinheit (74) steuert, um das Ziel des Kältemittels auf den Zwischendruckanschluss (G3) umzuschalten.
  3. Außeneinheit nach Anspruch 1, wobei die Steuereinheit (100) eingerichtet ist, einen Öffnungsgrad des dritten Expansionsventils (71) so zu steuern, dass sich eine Kältemitteltemperatur an der Auslassöffnung (G2) des Verdichters (10) einer Zieltemperatur nähert.
  4. Außeneinheit nach Anspruch 1, wobei die Steuereinheit (100) eingerichtet, einen Öffnungsgrad des vierten Expansionsventils (72) so zu steuern, dass sich eine Kältemitteltemperatur an einem Auslass des Kondensators (20) einer Zieltemperatur nähert.
  5. Außeneinheit nach einem der Ansprüche 1 bis 4, wobei die Steuereinheit (100) eingerichtet ist, eine Steuerung des Verdichters (10) und des zweiten Expansionsventils (40) durchzuführen, so dass ein überkritischer Bereich des Kältemittels verwendet wird.
  6. Kältekreislaufvorrichtung, umfassend:
    die Außeneinheit (2) nach einem der Ansprüche 1 bis 5; und
    die Lasteinrichtung (3).
  7. Kältemaschine, umfassend die Kältekreislaufvorrichtung (1) nach Anspruch 6.
EP19923884.1A 2019-04-10 2019-04-10 Ausseneinheit, kältekreislaufvorrichtung und kältemaschine Active EP3954947B1 (de)

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EP4286774A4 (de) 2021-01-27 2024-03-27 Mitsubishi Electric Corporation Kältekreislaufvorrichtung
EP4350246A4 (de) * 2021-05-25 2024-07-10 Mitsubishi Electric Corp Kältekreislaufvorrichtung
WO2022249288A1 (ja) * 2021-05-25 2022-12-01 三菱電機株式会社 冷凍サイクル装置
CN115682332A (zh) * 2021-07-30 2023-02-03 美的集团股份有限公司 空调器控制方法、装置、空调器及存储介质

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WO2008140454A1 (en) * 2007-05-14 2008-11-20 Carrier Corporation Refrigerant vapor compression system with flash tank economizer
EP2286162A4 (de) * 2007-12-20 2012-09-12 Carrier Corp Kältemittelsystem und betriebsverfahren dafür
JP2010127531A (ja) * 2008-11-27 2010-06-10 Mitsubishi Electric Corp 冷凍空調装置
JP5500240B2 (ja) * 2012-05-23 2014-05-21 ダイキン工業株式会社 冷凍装置
JP5516712B2 (ja) * 2012-05-28 2014-06-11 ダイキン工業株式会社 冷凍装置
WO2015063838A1 (ja) * 2013-10-28 2015-05-07 三菱電機株式会社 冷凍サイクル装置
JP6420686B2 (ja) * 2015-02-24 2018-11-07 日立ジョンソンコントロールズ空調株式会社 冷凍サイクル装置
JP6288146B2 (ja) 2016-04-01 2018-03-07 ダイキン工業株式会社 冷凍装置
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