EP3367021B1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP3367021B1
EP3367021B1 EP15906648.9A EP15906648A EP3367021B1 EP 3367021 B1 EP3367021 B1 EP 3367021B1 EP 15906648 A EP15906648 A EP 15906648A EP 3367021 B1 EP3367021 B1 EP 3367021B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
adjustment tank
amount adjustment
expansion valve
heat exchanger
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.)
Active
Application number
EP15906648.9A
Other languages
English (en)
French (fr)
Other versions
EP3367021A4 (de
EP3367021A1 (de
Inventor
Takuya Ito
Kazuyuki Ishida
Takahito HIKONE
Yasushi Okoshi
Masahiro Ito
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to EP19152449.5A priority Critical patent/EP3508802B1/de
Publication of EP3367021A1 publication Critical patent/EP3367021A1/de
Publication of EP3367021A4 publication Critical patent/EP3367021A4/de
Application granted granted Critical
Publication of EP3367021B1 publication Critical patent/EP3367021B1/de
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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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/003—Indoor unit with water as a heat sink or heat source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/004—Outdoor unit with water as a heat sink or heat source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • 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
    • F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B2600/2523—Receiver valves

Definitions

  • the present invention relates to a refrigeration cycle apparatus including a refrigerant circuit in which refrigerant circulates.
  • a water-side heat exchanger is superior in condensing efficiency of refrigerant than an air-side heat exchanger, thereby being capable of reducing a volume of the water-side heat exchanger. Further, in cooling operation and in heating operation, an amount of refrigerant required to a refrigeration cycle apparatus is smaller in the heating operation.
  • the amount of required refrigerant is smaller than that in the cooling operation, surplus refrigerant is required to be stored.
  • Patent Literature 2 describes an air conditioner including a control device which controls the amount of a refrigerant by controlling a high pressure-side flow control device and a low pressure-side flow control device when starting the operation of a compressor.
  • the control device makes the opening of the high pressure-side flow control device larger than the opening of the low pressure-side flow control device so as to reserve the refrigerant in a receiver in air-conditioning operation in which a suitable refrigerant amount is small, for example, in a heating operation.
  • the opening of the low pressure-side flow control device is made larger than the opening of the high pressure-side flow control device so that the refrigerant is not reserved in the receiver.
  • Patent Literature 3 describes a refrigeration cycle apparatus constituted by a main compressor, an expander, a sub compressor independently placed in an upstream side of the main compressor, a use side heat exchanger, and a heat source side heat exchanger.
  • Patent Literature 4 describes an air conditioner provided to improve performance by preventing the loss or decrease of refrigerant pressure by a refrigerant storing element.
  • a storing element is connected to a refrigerant path in parallel and stores refrigerant.
  • Patent Literature 5 describes an air conditioner refrigerant circuit, in which the refrigerant circuit includes an outdoor unit refrigerant circuit that includes an accumulator, a compressor, a four way directional control valve and an outdoor heat exchanger disposed inside an outdoor unit, and an indoor heat exchanger disposed inside an indoor heat exchanger.
  • the present invention has been made in view of the problem of the related art described above, and has an object to provide a refrigeration cycle apparatus capable of reducing stagnation of the refrigerant in a refrigerant amount adjustment tank even in a case in which an ambient temperature of the refrigerant amount adjustment tank is lower than an evaporating temperature of the refrigerant.
  • a refrigeration cycle apparatus including a refrigerant circuit sequentially connecting, with pipes, a compressor, a refrigerant-flow switching device, an air-side heat exchanger, a main expansion valve, and a water-side heat exchanger, and configured to allow refrigerant to circulate in the refrigerant circuit
  • the refrigeration cycle apparatus including a refrigerant amount adjustment tank arranged in parallel with the main expansion valve, and configured to store the refrigerant, a first refrigerant flow control valve provided to a pipe connected to one end of the refrigerant amount adjustment tank, the pipe being branched from a pipe connecting the air-side heat exchanger and the main expansion valve, the first refrigerant flow control valve being configured to adjust a flow rate of the refrigerant flowing into and out of the refrigerant amount adjustment tank on the basis of an opening degree of the first refrigerant flow control valve, and a second refriger
  • the refrigerant is allowed to flow into the refrigerant amount adjustment tank to prevent liquefaction of the refrigerant in the refrigerant amount adjustment tank, and thereby stagnation of the refrigerant in the refrigerant amount adjustment tank can be reduced.
  • Fig. 1 is a schematic diagram for illustrating an example of a circuit structure of a refrigeration cycle apparatus 1 according to Embodiment 1 of the present invention.
  • a refrigeration cycle apparatus 1 includes a compressor 11, a refrigerant-flow switching device 12, such as a four-way valve, an air-side heat exchanger 13, a main expansion valve 14, a water-side heat exchanger 15, an accumulator 16, a refrigerant amount adjustment tank 17, a sub-expansion valve 18A and a sub-expansion valve 18B serving as two refrigerant flow control valves, a gas purge circuit 19, and a heat source device controller 10 serving as a controller.
  • the compressor 11, the refrigerant-flow switching device 12, the air-side heat exchanger 13, the main expansion valve 14, the water-side heat exchanger 15, and the accumulator 16 are connected annularly via refrigerant pipes 2, to thereby form a main circuit of a refrigerant circuit.
  • a sub-circuit of the refrigerant circuit is formed by the refrigerant amount adjustment tank 17, the sub-expansion valve 18A, the sub-expansion valve 18B, and the gas purge circuit 19.
  • the compressor 11 sucks low-temperature and low-pressure refrigerant, compresses the refrigerant into high-temperature and high-pressure gas refrigerant, and discharges the refrigerant.
  • the compressor 11 there may be used, for example, an inverter compressor capable of controlling a flow rate, which is an amount of refrigerant delivered per unit time, in accordance with arbitral change in a drive frequency.
  • a low-pressure pressure sensor 22 is provided to measure a pressure of the refrigerant to be sucked into the compressor 11. Information indicating the measured pressure is supplied to a heat source device controller 10 described later.
  • the refrigerant-flow switching device 12 switches between cooling operation and heating operation by switching a flow direction of the refrigerant.
  • the refrigerant-flow switching device 12 for example, the four-way valve may be used, and other valves may be used in combination.
  • the air-side heat exchanger 13 exchanges heat between air supplied by an air-side air sending device 21, such as a fan disposed in its vicinity, and the refrigerant.
  • the air-side heat exchanger 13 is configured to serve, in the cooling operation, as a condenser for condensing the refrigerant by radiating heat of the refrigerant to the air.
  • the air-side heat exchanger 13 also serves, in the heating operation, as an evaporator for evaporating the refrigerant and cooling outside air using a heat of evaporation at a time of evaporation.
  • the main expansion valve 14 has functions of reducing and expanding the pressure of the refrigerant flowing in the refrigerant circuit.
  • the main expansion valve 14 may be configured by, for example, an electronic expansion valve or other valve capable of controlling an opening degree of the valve.
  • the water-side heat exchanger 15 serves as a condenser or an evaporator, and exchanges heat between the refrigerant flowing in the refrigerant circuit and a heat medium, such as water, flowing in a heat medium circuit by use of a pump 40.
  • the accumulator 16 is provided on a suction side, which is a low pressure side of the compressor 11.
  • the accumulator 16 is configured to store surplus refrigerant caused by the difference between the operation conditions of the cooling operation and the heating operation, surplus refrigerant caused by change in transitional operation, and another surplus refrigerant.
  • the refrigerant amount adjustment tank 17 is provided in parallel with the main expansion valve 14, and is configured to store the surplus refrigerant caused by the difference between the operation conditions of the cooling operation and the heating operation.
  • the refrigerant amount adjustment tank 17 has one end connected to a pipe branched from the refrigerant pipe 2 connecting the air-side heat exchanger 13 and the main expansion valve 14. Further, the refrigerant amount adjustment tank 17 has the other end connected to a pipe branched from the refrigerant pipe 2 connecting the main expansion valve 14 and the water-side heat exchanger 15.
  • the amount of refrigerant required for the refrigerant circuit becomes surplus, and hence the surplus refrigerant liquid is caused to flow into the refrigerant amount adjustment tank 17 to be stored in the refrigerant amount adjustment tank 17.
  • the sub-expansion valves 18A and 18B each serve as a refrigerant flow control valve for controlling the flow rate of refrigerant flowing into and out of the refrigerant amount adjustment tank 17 depending on the opening degree of the valve.
  • the sub-expansion valve 18A is provided on one end side of the refrigerant amount adjustment tank 17, specifically, on an upstream side of the refrigerant amount adjustment tank 17 in the cooling operation. Further, the sub-expansion valve 18B is provided on the other end side of the refrigerant amount adjustment tank 17, specifically, on a downstream side of the refrigerant amount adjustment tank 17 in the cooling operation.
  • the gas purge circuit 19 has one end connected to the refrigerant amount adjustment tank 17 and the other end connected to the refrigerant pipe 2 connecting the main expansion valve 14 and the water-side heat exchanger 15.
  • the gas purge circuit 19 is configured to prevent, even when the sub-expansion valves 18A and 18B provided on both end sides of the refrigerant amount adjustment tank 17 are fully closed, the refrigerant in the refrigerant amount adjustment tank 17 from being liquid-sealed.
  • the low-pressure pressure sensor 22 measures a pressure of the refrigerant flowing into the compressor 11, and supplies pressure information of a measurement result to the heat source device controller 10.
  • the low-pressure pressure sensor 22 is connected to the refrigerant pipe 2 on the suction side of the compressor 11.
  • An outside-air temperature sensor 23 measures an ambient temperature of the refrigerant amount adjustment tank 17, and supplies temperature information of a measurement result to the heat source device controller 10.
  • the outside-air temperature sensor 23 is provided in a vicinity of the refrigerant amount adjustment tank 17, but an area in which the outside-air temperature sensor 23 is provided is not limited to the vicinity of the refrigerant amount adjustment tank 17.
  • the outside-air temperature sensor 23 may be provided, for example, at a position far from the refrigerant amount adjustment tank 17. Further, for example, a temperature sensor (not shown) provided to an air suction position of the air-side heat exchanger 13 may be used as the outside-air temperature sensor 23.
  • the heat source device controller 10 is configured by a microcomputer, for example, and controls an entire of the refrigeration cycle apparatus 1.
  • the heat source device controller 10 receives information indicating measurement results from various measurement units, such as the low-pressure pressure sensor 22 and the outside-air temperature sensor 23. Then, the heat source device controller 10 controls a drive frequency of the compressor 11, a number of revolution of the air-side air sending device 21 (including activation and deactivation of the air-side air sending device 21), switching of the refrigerant-flow switching device 12, the opening degree of the main expansion valve 14, the opening degrees of sub-expansion valves 18Aand 18B, and other operations, on the basis of operation information of the refrigeration cycle apparatus 1 based on the measurement results, and in accordance with an operation content instructed by a user.
  • FIG. 2 is a schematic diagram for illustrating a mounting according to invention of the refrigerant amount adjustment tank 17 illustrated in the refrigeration cycle apparatus 1 of Fig. 1 .
  • various devices of the refrigeration cycle apparatus 1 are housed in the machine chamber 30, and the air-side heat exchanger 13 is disposed on top of the machine chamber 30. Further, the air-side air sending device 21 is disposed on top of the air-side heat exchanger 13.
  • various devices housed in the machine chamber 30 include the compressor 11, the refrigerant-flow switching device 12, the main expansion valve 14, the water-side heat exchanger 15, and the accumulator 16, which form the main circuit of the refrigerant circuit, and the heat source device controller 10.
  • the machine chamber 30 also houses the refrigerant amount adjustment tank 17 and the sub-expansion valves 18A and 18B, which form the sub-circuit of the refrigerant circuit.
  • the refrigerant is heated so that a temperature in the refrigerant amount adjustment tank is constantly higher than an evaporating temperature of the refrigerant, and hence such a configuration has been suggested in which the refrigerant amount adjustment tank is disposed downstream of an air flow of the air-side heat exchanger, namely, on top of the machine chamber.
  • the refrigerant amount adjustment tank is heavy, and hence the strength of the machine chamber is required to be enhanced to dispose the refrigerant amount adjustment tank on top of the machine chamber. Consequently, there is a fear that the total weight of the refrigeration cycle apparatus increases, resulting in increasing a manufacturing cost.
  • the refrigerant amount adjustment tank 17 is housed in the machine chamber 30.
  • the refrigerant amount adjustment tank 17 When the refrigerant amount adjustment tank 17 is housed in the machine chamber 30, the refrigerant amount adjustment tank 17 is connected via the refrigerant pipes 2 by the substantially shortest distance to devices, such as the water-side heat exchanger 15, which are required to be connected in the refrigerant circuit.
  • the structure of the refrigeration cycle apparatus 1 may be simplified.
  • the refrigerant amount adjustment tank 17 is housed in the machine chamber 30, and hence the refrigerant pipes 2 connected to the refrigerant amount adjustment tank 17 may be connected by the substantially shortest distance.
  • the refrigerant pipes 2 in the refrigeration cycle apparatus 1 may be reduced in length, and thereby the structure of the refrigeration cycle apparatus 1 can be simplified.
  • the center of gravity of the refrigeration cycle apparatus 1 is located at a lower part, and hence it is possible to improve the stability when the refrigeration cycle apparatus 1 is disposed.
  • the refrigerant amount adjustment tank 17 when the evaporating temperature of the refrigerant is higher than an outside-air temperature, the refrigerant is cooled by an outside air via container walls of the refrigerant amount adjustment tank 17. As a result, the refrigerant in the refrigerant amount adjustment tank 17 is liquefied, the refrigerant liquid may stagnate in the refrigerant amount adjustment tank 17.
  • the sub-expansion valves 18A and 18B are provided at both ends of the refrigerant amount adjustment tank 17 to appropriately adjust the flow rate of the refrigerant flowing into the refrigerant amount adjustment tank 17 in the cooling operation.
  • the refrigerant amount adjustment tank 17 may be housed in the machine chamber 30, and the stagnation of the refrigerant in the refrigerant amount adjustment tank 17 may be reduced when the evaporating temperature of the refrigerant is higher than the outside-air temperature.
  • Fig. 3 is a flow chart for illustrating an example of a process for controlling a flow rate of refrigerant flowing into the refrigerant amount adjustment tank 17 illustrated in the refrigeration cycle apparatus 1 of Fig. 1 .
  • Step S1 the heat source device controller 10 determines whether a unit operation is performed. It should be noted that a state "in which the unit operation is performed,” represents a state in which the compressor 11 is in an operation state, the refrigerant circulates in the refrigerant circuit, and an operation mode is the cooling operation.
  • Step S1 When the determination is made that the unit operation is performed (Step S1, YES), the process proceeds to Step S2. Meanwhile, when the determination is made that the unit operation is not performed (Step S1, NO), the process proceeds to Step S4.
  • Step S2 the heat source device controller 10 converts pressure information obtained by the low-pressure pressure sensor 22 into an evaporating temperature, which is a saturation temperature of the refrigerant. Then, the heat source device controller 10 compares the obtained evaporating temperature of the refrigerant and the outside-air temperature that is based on temperature information obtained by the outside-air temperature sensor 23 to determine whether the evaporating temperature of the refrigerant is higher than the outside-air temperature.
  • the evaporating temperature of the refrigerant is obtained, but the basis is not limited to this example.
  • a temperature sensor may be provided on a refrigerant exit side of the of the air-side heat exchanger 13 in the cooling operation, and the evaporating temperature of the refrigerant may be obtained from the measurement results of the temperature sensor.
  • the evaporating temperature of the refrigerant is a temperature obtained on the basis of a pressure of the refrigerant at the low pressure, which is measured by the low-pressure pressure sensor 22, but the pressure of the refrigerant of this case differs from a pressure of the refrigerant flowing into the refrigerant amount adjustment tank 17. For this reason, an error lies between the evaporating temperature of the refrigerant at the low pressure, which is based on the measurement results of the low-pressure pressure sensor 22 and the evaporating temperature of the refrigerant based on the pressure of the refrigerant flowing into the refrigerant amount adjustment tank 17.
  • the outside-air temperature is a temperature, which is obtained on the basis of the temperature measured by the outside-air temperature sensor 23, but an error lies between the outside-air temperature and an actual temperature of the refrigerant amount adjustment tank 17.
  • Embodiment 1 of the present invention a set temperature to correct these errors is preset, and a comparison is made between the evaporating temperature of the refrigerant at the low pressure and a temperature obtained by adding the set temperature to the outside-air temperature.
  • the temperature obtained by adding the set temperature to the outside-air temperature is simply referred to as the "outside-air temperature" for the description below.
  • Step S2 When determination is made that the evaporating temperature of the refrigerant is equal to or lower than the outside-air temperature (Step S2, NO), the process proceeds to Step S4.
  • the refrigerant in the refrigerant amount adjustment tank 17 is heated by an ambient outside air.
  • the refrigerant is heated to be brought into a gas state, even when the sub-expansion valve 18B is opened to release pipes connecting the refrigerant amount adjustment tank 17 and the water-side heat exchanger 15, the refrigerant liquid does not stagnate in the refrigerant amount adjustment tank 17.
  • Step S4 the heat source device controller 10 sets the opening degree of the sub-expansion valve 18A to “full close”, and sets the opening degree of the sub-expansion valve 18B to “full open”.
  • Step S2 when the evaporating temperature of the refrigerant is determined to be higher than the outside-air temperature (Step S2, YES), the process proceeds to Step S3.
  • the refrigerant in the refrigerant amount adjustment tank 17 is cooled by the ambient outside air.
  • the refrigerant in the refrigerant amount adjustment tank 17 is liquefied by condensation, and even when the sub-expansion valve 18B is opened to release the pipes connecting the refrigerant amount adjustment tank 17 and the water-side heat exchanger 15, the refrigerant liquid stagnates in the refrigerant amount adjustment tank 17. Then, the refrigerant liquid stagnates in the refrigerant amount adjustment tank 17, and hence the refrigerant in the refrigerant circuit is insufficient for the refrigerant required in the cooling operation. As a result, there is a fear that a stable operation cannot be made.
  • Step S3 the heat source device controller 10 sets the opening degree of the sub-expansion valve 18A to a “set opening degree” that is preset, and the opening degree of the sub-expansion valve 18B is set to "full open”.
  • the refrigerant in the refrigerant amount adjustment tank 17 is brought into a gas state as described above, the refrigerant does not stagnate in the refrigerant amount adjustment tank 17, and most of the refrigerant filled in the refrigerant circuit circulates in the refrigerant circuit. For this reason, the required amount of refrigerant in the cooling operation may be smaller than that in a case in which the refrigerant is constantly continuously flowing into the refrigerant amount adjustment tank 17.
  • the required amount of refrigerant in the heating operation is smaller than the required amount in the cooling operation, surplus refrigerant is required to be stored in the refrigerant amount adjustment tank 17. Consequently, in this case, the sub-expansion valve 18B is set to "full open” to release the pipes connecting the refrigerant amount adjustment tank 17 and the water-side heat exchanger 15, and the surplus refrigerant is stored in the refrigerant amount adjustment tank 17.
  • the sub-expansion valve 18A is set to a minimum opening degree. With this configuration, a minimum circulation amount of the refrigerant circuit may be circulated.
  • the refrigerant amount adjustment tank 17 to store the surplus refrigerant is provided in parallel with the main expansion valve 14, and the sub-expansion valves 18A and 18B are provided on both ends of the refrigerant amount adjustment tank 17. Then, on the basis of the evaporating temperature of the refrigerant in the refrigerant amount adjustment tank 17 and the outside-air temperature, the opening degrees of the sub-expansion valves 18A and 18B are controlled to control the flow rate of the refrigerant flowing into and out of the refrigerant amount adjustment tank 17.
  • the refrigerant in the cooling operation, to prevent the refrigerant stagnating in the refrigerant amount adjustment tank 17 from being liquefied by the outside-air temperature, the refrigerant may be caused to flow in the refrigerant amount adjustment tank 17 to reduce the stagnation of the refrigerant in the refrigerant amount adjustment tank 17.
  • Embodiment 1 of the present invention by reducing the stagnation of the refrigerant in the refrigerant amount adjustment tank 17 as described above, the refrigerant amount adjustment tank is not required to be disposed, as in the related art, downstream of the flow of the air of the air-side heat exchanger. As a result, the refrigerant amount adjustment tank 17 may be housed in the machine chamber, and the structure of the refrigeration cycle apparatus 1 may be simplified.
  • the opening degree of the sub-expansion valve 18B is always set to, in the cooling operation and in the heating operation, "full open,” and hence the sub-expansion valve 18B may be omitted.
  • the refrigerant amount adjustment tank 17 may be cooled. Consequently, for a predetermined period of time from a start-up of the compressor 11, a heat quantity for cooling the refrigerant is larger than that for the stable operation time period. Consequently, for the predetermined period of time from the start-up of the compressor 11, it is required that the flow rate of the refrigerant flowing into the refrigerant amount adjustment tank 17 is larger than that for the stable operation time period, and the refrigerant amount adjustment tank 17 is heated by the flowing refrigerant.
  • Embodiment 2 which is not claimed, depending on an elapsed time period since the start-up of the compressor 11, the opening degree of the sub-expansion valve 18A is changed to control the flow rate of the refrigerant flowing into the refrigerant amount adjustment tank 17.
  • Fig. 4 is a flow chart for illustrating an example of a process for controlling a flow rate of refrigerant flowing into the refrigerant amount adjustment tank 17 illustrated in a refrigeration cycle apparatus 1 according to Embodiment 2 of the present invention.
  • Step S11 the heat source device controller 10 determines whether a unit operation is performed.
  • Step S11, YES the process proceeds to Step S12.
  • Step S12 the heat source device controller 10 converts pressure information obtained by the low-pressure pressure sensor 22 into an evaporating temperature, which is a saturation temperature of the refrigerant. Then, the heat source device controller 10 compares the obtained evaporating temperature of the refrigerant and the outside-air temperature, which is based on temperature information obtained by the outside-air temperature sensor 23 to determine whether the evaporating temperature of the refrigerant is higher than the outside-air temperature.
  • Step S12 When the determination is made that the evaporating temperature of the refrigerant is higher than the outside-air temperature (Step S12, YES), the process proceeds to Step S13.
  • Step S13 the heat source device controller 10 determines whether four minutes have elapsed since the start-up of the compressor 11. This operation is to determine, as described above, whether the compressor 11 is in a stable operation state.
  • the time period to determine whether the compressor 11 is in the stable operation is not limited to four minutes.
  • the time period may be appropriately set.
  • Step S13 When the determination is made that four minutes have not yet elapsed (Step S13, NO), the process proceeds to Step S15.
  • Step S15 the heat source device controller 10 sets the opening degree of the sub-expansion valve 18A to a preset "first opening degree.” Specifically, the heat source device controller 10 sets, for example, the opening degree of the sub-expansion valve 18A, as the "first opening degree,” to about 20% of “full open.”
  • Step S13 when the heat source device controller 10 determines that four minutes have elapsed (Step S13, YES), the process proceeds to Step S14.
  • Step S14 the heat source device controller 10 sets the opening degree of the sub-expansion valve 18A to a "second opening degree” that is smaller than the opening degree set in Step S15. Specifically, the heat source device controller 10 sets the opening degree of the sub-expansion valve 18A as the "second opening degree” to about 10% of "full open.”
  • Step S11 determines that the unit operation is not performed
  • Step S12 determines that the evaporating temperature of the refrigerant is equal to or lower than the outside-air temperature
  • Step S16 the process proceeds to Step S16.
  • Step S16 the heat source device controller 10 sets the opening degree of the sub-expansion valve 18A to “full close” and sets the opening degree of the sub-expansion valve 18B to “full open.”
  • the opening degree of the sub-expansion valve 18A may be set to a larger opening degree that is the same opening degree as in Step S15.
  • the flow ratio of the refrigerant flowing into the refrigerant amount adjustment tank 17 may be made smaller than the flow rate of the refrigerant flowing into the main expansion valve 14.
  • influence of the refrigerant flow control to the main expansion valve 14 may be made smaller, and thereby a stable operation can be performed.
  • Embodiment 2 of the present invention depending on the elapsed time period since the start-up of the compressor 11, the opening degree of the sub-expansion valve 18A is changed. Then, from the start-up of the compressor 11 to the elapse of the predetermined time, the opening degree of the sub-expansion valve 18A is made larger than that in the stable operation, the flow rate of the refrigerant flowing into the refrigerant amount adjustment tank 17 can be made larger, and thereby the refrigerant stagnating in the refrigerant amount adjustment tank 17 can be more heated.
  • the opening degree of the sub-expansion valve 18A when the compressor 11 is in the stable operation is made smaller than the opening degree of the sub-expansion valve 18A at the time of start-up of the compressor 11, the influence to the refrigerant flow rate control of the main expansion valve 14 may be made smaller, and thereby the more stable operation may be performed.
  • Embodiment 1 and Embodiment 2 of the present invention are made of Embodiment 1 and Embodiment 2 of the present invention as described above, but the present invention is defined by the claims.
  • Embodiment 1 and Embodiment 2 described above description is made of a case in which the number of the refrigerant circuit is one, but the number of the refrigerant circuit is not limited to one.
  • a plurality of refrigerant circuits may be provided in the same refrigeration cycle apparatus 1.
  • Fig. 5 is a schematic diagram for illustrating an example in which a plurality of refrigerant circuits are provided in the refrigeration cycle apparatus according to Embodiment 1 and Embodiment 2 of the present invention.
  • a plurality of refrigerant circuits are provided in the refrigeration cycle apparatus according to Embodiment 1 and Embodiment 2 of the present invention.
  • four refrigerant circuits are provided are illustrated.
  • refrigeration cycle apparatus refrigerant pipe 10 heat source device controller 11 compressor 12 refrigerant-flow switching device 13 air-side heat exchanger 14 main expansion valve 15 water-side heat exchanger 16 accumulator 17 refrigerant amount adjustment tank 18A, 18B sub-expansion valve 19 gas purge circuit 21 air-side air sending device 22 low-pressure pressure sensor 23 outside-air temperature sensor 30 machine chamber 40 pump

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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)

Claims (3)

  1. Kältekreislaufvorrichtung (1), aufweisend einen Kältemittelkreislauf, der mit Leitungen einen Verdichter (11), eine Kältemittelströmungsschalteinrichtung (12), einen luftseitigen Wärmetauscher (13), ein Hauptexpansionsventil (14) und einen wasserseitigen Wärmetauscher (15) sequentiell verbindet und eingerichtet ist, dem Kältemittel zu ermöglichen, in dem Kältemittelkreislauf zu zirkulieren, wobei die Kältekreislaufvorrichtung (1) umfasst:
    einen Kältemittelmengenanpassungsbehälter (17), der parallel zum Hauptexpansionsventil (14) angeordnet ist und eingerichtet ist, das Kältemittel zu speichern;
    ein erstes Kältemittelströmung-Steuerungsventil (18A), das an einer Leitung vorgesehen ist, die mit einem Ende des Kältemittelmengenanpassungsbehälters (17) verbunden ist, wobei die Leitung von einer Leitung abgezweigt ist, die den luftseitigen Wärmetauscher (13) und das Hauptexpansionsventil (14) verbindet, wobei das erste Kältemittelströmung-Steuerungsventil (18A) eingerichtet ist, eine Strömungsrate des Kältemittels, das in den und aus dem Kältemittelmengenanpassungsbehälter (17) strömt, auf Grundlage eines Öffnungsgrades des ersten Kältemittelströmung-Steuerungsventils (18A) anzupassen; und
    ein zweites Kältemittelströmung-Steuerungsventil (18B), das an einer Leitung vorgesehen ist, die mit einem Ende des Kältemittelmengenanpassungsbehälters (17) verbunden ist, wobei die Leitung von einer Leitung abgezweigt ist, die das Hauptexpansionsventil (14) und den wasserseitigen Wärmetauscher (15) verbindet, wobei das zweite Kältemittelströmung-Steuerungsventil (18B) eingerichtet ist, eine Strömungsrate des Kältemittels, das in den und aus dem Kältemittelmengenanpassungsbehälter (17) strömt, auf Grundlage eines Öffnungsgrades des zweiten Kältemittelströmung-Steuerungsventils (18B) anzupassen,
    wobei der Kältemittelmengenanpassungsbehälter (17) in einer Maschinenkammer (30) untergebracht ist, die zumindest den Verdichter (11) und das Hauptexpansionsventil (14) unterbringt, die den Kältemittelkreislauf bilden,
    wobei der Kältemittelmengenanpassungsbehälter (17) unter dem luftseitigen Wärmetauscher (13) angeordnet ist.
  2. Kältekreislaufvorrichtung (1) nach Anspruch 1, ferner umfassend einen Gasablasskreislauf (19), aufweisend ein Ende, das mit dem Kältemittelmengenanpassungsbehälter (17) verbunden ist, und ein anderes Ende, das mit einer Leitung verbunden ist, die das Hauptexpansionsventil (14) und den wasserseitigen Wärmetauscher (15) verbindet.
  3. Kältekreislaufvorrichtung (1) nach Anspruch 1 oder 2, umfassend eine Vielzahl von Kältemittelkreisläufen.
EP15906648.9A 2015-10-20 2015-10-20 Kältekreislaufvorrichtung Active EP3367021B1 (de)

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EP19152449.5A Division EP3508802B1 (de) 2015-10-20 2015-10-20 Kältekreislaufvorrichtung

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JPWO2021084743A1 (de) * 2019-11-01 2021-05-06

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EP3367021A4 (de) 2019-02-20
JP6479203B2 (ja) 2019-03-06
EP3508802B1 (de) 2020-04-22
EP3508802A1 (de) 2019-07-10
EP3367021A1 (de) 2018-08-29
WO2017068642A1 (ja) 2017-04-27
JPWO2017068642A1 (ja) 2018-05-10

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