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WO2017038161A1 - Dispositif à cycle de réfrigération et procédé de commande de dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération et procédé de commande de dispositif à cycle de réfrigération Download PDF

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Publication number
WO2017038161A1
WO2017038161A1 PCT/JP2016/063963 JP2016063963W WO2017038161A1 WO 2017038161 A1 WO2017038161 A1 WO 2017038161A1 JP 2016063963 W JP2016063963 W JP 2016063963W WO 2017038161 A1 WO2017038161 A1 WO 2017038161A1
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WIPO (PCT)
Prior art keywords
stage compressor
refrigerant
compressor
expansion valve
predetermined value
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.)
Ceased
Application number
PCT/JP2016/063963
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English (en)
Japanese (ja)
Inventor
峰正 大村
岡田　拓也
正広 寺岡
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 Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to KR1020177037231A priority Critical patent/KR102098164B1/ko
Priority to EP16841193.2A priority patent/EP3301380B1/fr
Priority to CN201680035531.1A priority patent/CN107709895A/zh
Publication of WO2017038161A1 publication Critical patent/WO2017038161A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion 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
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/0409—Refrigeration circuit bypassing means for the 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0415—Refrigeration circuit bypassing means for the receiver
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/022—Compressor control for multi-stage operation
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/027—Compressor control by controlling pressure
    • F25B2600/0271—Compressor control by controlling pressure the discharge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction 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
    • F25B2700/2115—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 a refrigeration cycle apparatus and a control method of the refrigeration cycle apparatus.
  • Some heat pump systems using a refrigeration cycle in which a refrigerant circulates have an object of enabling high-temperature tapping even under a low outside air temperature environment.
  • the lower the outside air temperature the lower the temperature and pressure of the refrigerant at the evaporator inlet of the refrigerant, and the lower the suction pressure of the compressor inlet.
  • the discharge pressure of the compressor is increased to a predetermined value, the temperature of the refrigerant discharged from the compressor increases as the outside air temperature decreases.
  • the discharge pressure of the compressor is set higher as the tapping temperature is higher, the temperature of the refrigerant discharged from the compressor is increased.
  • the refrigerant supplied to the suction pipe of the compressor is a supercooling liquid medium, and when the amount of the liquid medium supplied is large, the refrigerant at the inlet of the compressor is in a gas-liquid two-phase state. As a result, since the compressor compresses the liquid, the compressor may be damaged. Therefore, the method of supplying the supercooled liquid medium to the suction pipe of the compressor can not always be performed, and can only intermittently prevent the temperature rise of the compressor.
  • Patent Document 1 it is described that the liquid refrigerant is supplied between the low stage side compression mechanism and the high stage side compression mechanism to reduce the temperature of the suction refrigerant of the high stage side compressor.
  • the temperature of the refrigerant discharged from the high pressure side compression mechanism decreases, but when the amount of liquid refrigerant supplied to the high pressure side compression mechanism is large, the refrigerant at the high pressure side compression mechanism inlet is in the gas-liquid two-phase state It becomes. Therefore, the high stage compressor needs to be supplied with an appropriate amount of liquid medium.
  • the present invention has been made in view of such circumstances, and it is intended to reduce the temperature of the refrigerant sucked by the high stage compressor and to prevent the high stage compressor from sucking the liquid medium. And a control method of the refrigeration cycle apparatus.
  • a compression unit having a low-stage compressor and a high-stage compressor, a condenser, an expansion unit, and an evaporator are connected by piping, and refrigerant is circulated.
  • the refrigerant delivered from the condenser is branched before being supplied to the expansion unit through the bypass piping, and is supplied between the low-stage compressor and the high-stage compressor.
  • the flow rate adjustment unit adjusts the flow rate of the refrigerant while starting or stopping the flow of the refrigerant in the bypass pipe.
  • the flow rate adjusting unit When the high-stage compressor discharge temperature is higher than a predetermined value, the flow rate adjusting unit is controlled to increase the amount of refrigerant flowing through the bypass pipe, so the temperature of the refrigerant drawn by the high-stage compressor decreases. . Further, based on the high stage compressor suction superheat degree, the flow rate adjusting unit is controlled to adjust the amount of refrigerant flowing through the bypass pipe. Therefore, control can be performed such that the refrigerant sucked by the high-stage side compressor becomes the superheated gas, and the compressor can be prevented from sucking the liquid refrigerant. In addition, since the degree of superheat of the refrigerant sucked by the high-stage compressor can be made constant, it is possible to prevent the temperature rise and breakage of the compressor.
  • control unit controls the flow rate adjusting unit to reduce the amount of refrigerant flowing through the bypass pipe when the suction superheat degree of the high-stage compressor is equal to or less than a predetermined value.
  • the flow rate adjusting unit is controlled to reduce the amount of refrigerant flowing through the bypass pipe. It is possible to suppress a decrease in the degree of superheat of the refrigerant to be sucked.
  • the control unit The flow rate adjuster may be controlled to increase the amount of refrigerant flowing through the bypass pipe.
  • the flow rate adjusting unit is controlled to bypass the bypass pipe. Since the amount of the refrigerant flowing through increases, it is possible to suppress an increase in the degree of superheat of the refrigerant sucked by the high stage compressor.
  • the control unit when the suction superheat degree of the high pressure side compressor is higher than a predetermined value and the discharge temperature of the high pressure side compressor is not more than the predetermined value, the control unit The amount of the refrigerant flowing through the bypass pipe may be maintained by the flow rate adjusting unit.
  • the flow rate adjusting unit is not controlled. Since the amount of the refrigerant flowing through is maintained, it is possible to suppress a decrease and an increase in the degree of superheat of the refrigerant sucked by the high-stage-side compressor and maintain the refrigerant constant.
  • the controller is configured such that the degree of suction superheat of the high-stage compressor is higher than a predetermined value, and the discharge temperature of the high-stage compressor or the discharge of the high-stage compressor When the pressure is higher than a predetermined value, the rotational speed of the low-stage compressor or the high-stage compressor may be controlled to increase the discharge pressure of the refrigerant discharged from the low-stage compressor.
  • the suction superheat degree of the high-stage compressor when the suction superheat degree of the high-stage compressor is higher than a predetermined value and the discharge temperature of the high-stage compressor or the discharge pressure of the high-stage compressor is higher than a predetermined value Since the rotation speed of the stage side compressor or the high stage side compressor is controlled and the discharge pressure of the refrigerant discharged from the low stage side compressor is increased, the suction pressure of the high stage side compressor is also increased. The difference between the suction pressure and the discharge pressure of the stage-side compressor can be reduced. As a result, the high stage compressor discharge temperature can be reduced. In order to increase the discharge pressure of the refrigerant discharged from the low-stage compressor, the number of revolutions of the high-stage compressor is decreased or the number of revolutions of the low-stage compressor is increased.
  • the flow rate adjustment unit is an expansion valve
  • the control unit is configured to set a discharge temperature of the high stage compressor or a discharge pressure of the high stage compressor higher than a predetermined value.
  • the discharge temperature of the high-stage compressor or the discharge pressure of the high-stage compressor is higher than a predetermined value, so the opening degree of the expansion valve can not be increased, and an increase in the degree of superheat can not be suppressed. Even in this case, by controlling the rotational speed of the low-stage compressor or the high-stage compressor, it is possible to reliably lower the high-stage compressor discharge temperature.
  • a compression unit having a low-stage compressor and a high-stage compressor, a condenser, an expansion unit, and an evaporator are connected by piping and refrigerant And a bypass pipe that branches off in a pipe that connects the condenser and the expansion unit and that joins with a pipe that connects the low-stage compressor and the high-stage compressor;
  • a control method of a refrigeration cycle apparatus including a flow rate adjusting unit provided in a pipe and adjusting the amount of refrigerant flowing through the bypass pipe, wherein the discharge temperature of the high-stage compressor is higher than a predetermined value. Controlling the flow rate adjusting unit to increase the amount of refrigerant flowing through the bypass pipe; controlling the flow rate adjusting unit based on the degree of suction superheat of the high-stage compressor; Step to adjust the amount And, with a.
  • the present invention it is possible to reduce the temperature of the refrigerant drawn by the high-stage compressor and to prevent the high-stage compressor from drawing the liquid medium.
  • the heat pump water heater 1 includes a heat pump system (hereinafter simply referred to as a heat pump) 2 and a water circulation system 3 connected to a hot water storage tank unit (not shown).
  • a heat pump heat pump
  • a water circulation system 3 connected to a hot water storage tank unit (not shown).
  • a refrigerating cycle apparatus is the heat pump 2
  • the refrigerating cycle apparatus of this invention is not limited to this example.
  • the refrigeration cycle apparatus according to the present invention is also applicable to those having a refrigerant cycle such as an air conditioner.
  • the water circulation system path 3 on the hot water storage tank unit side is a water supply side system path 3A connected to the water side flow path of the condenser (refrigerant / water heat exchanger) 11 in the heat pump 2 and the hot water manufactured by the condenser 11 And a hot water extraction side system path 3B for taking out the water, and a water pump and a flow control valve are provided in the water supply side system path 3A.
  • the heat pump 2 includes a compression unit having a low-stage compressor 7 and a high-stage compressor 8, a condenser 11 for radiating the refrigerant gas, a first expansion valve 12 for decompressing the refrigerant to an intermediate pressure, and a gas-liquid separation.
  • the exchanger 17) is constituted by a closed cycle refrigerant circuit connected in this order via a refrigerant pipe.
  • the condenser 11 of the heat pump 2 is a refrigerant / water heat exchanger, and a high temperature / high pressure refrigerant gas discharged from the compression section is circulated in one refrigerant side flow path, and a water circulation system is generated in the other water side flow path The water is circulated through the passage 3 to exchange heat between the water and the refrigerant gas. And this condenser 11 is comprised so that warm water may be produced
  • the refrigerant circuit is provided with a gas injection circuit 31 for supplying the high pressure side compressor 8 with the intermediate pressure refrigerant gas separated by the intermediate pressure receiver 13 having a gas-liquid separation function.
  • the gas injection circuit 31 may be provided with a solenoid valve and a check valve so that the gas injection circuit 31 can be opened and closed as needed.
  • the refrigerant circuit is provided with a liquid bypass circuit 32 which supplies the high-stage compressor 8 with the refrigerant cooled by heat exchange with water in the condenser 11.
  • the liquid bypass circuit 32 is provided with a third expansion valve 33.
  • the heat pump water heater 1 when the heat pump 2 is operated, the high temperature / high pressure refrigerant gas compressed in two stages in the compression section is introduced into the condenser 11, where water is supplied from the water supply system 3A of the water circulation system 3 It exchanges heat with the water flowing through the side flow path. This water is heated and raised by heat release from the high temperature / high pressure refrigerant gas, and then returns to the hot water storage tank (not shown) through the hot water extraction side system path 3B until the amount of hot water storage in the hot water storage tank reaches a predetermined amount, The heat exchange between the refrigerant and the water is continuously continued by the condenser 11, and when the amount of stored hot water reaches a predetermined amount, the stored hot water operation is ended.
  • the refrigerant cooled by heat exchange with water in the condenser 11 is decompressed by the first expansion valve 12 and reaches the intermediate pressure receiver 13, where it is separated into gas and liquid.
  • the gas refrigerant of intermediate pressure separated by the intermediate pressure receiver 13 is supplied to the high pressure side compressor 8 by the gas injection circuit 31, and is sucked into the high pressure side compressor 8 and recompressed.
  • the economizer effect by the gas injection can improve the heating capacity and coefficient of performance (COP) and increase the hot water supply capacity.
  • the liquid refrigerant separated by the intermediate pressure receiver 13 is depressurized by the second expansion valve 16 and flows into the evaporator (air heat exchanger) 17 as a low-temperature low-pressure gas-liquid two-phase refrigerant.
  • the refrigerant flowing into the evaporator 17 exchanges heat with the outside air blown by the blower, absorbs heat from the outside air, and is vaporized and gasified.
  • the refrigerant gasified by the evaporator 17 is sucked into the compressor and recompressed.
  • generation of warm water is performed by repeating the same operation.
  • a first temperature sensor 21 is provided in the discharge pipe of the high-stage compressor 8. The temperature of the refrigerant discharged from the high pressure side compressor 8 (the discharge temperature of the high pressure side compressor 8) is measured by the first temperature sensor 21.
  • a second temperature sensor 22 is provided in a portion of the suction pipe of the high-stage compressor 8 after joining with the liquid bypass circuit 32. The temperature of the refrigerant drawn into the high pressure side compressor 8 is measured by the second temperature sensor 22. Further, a pressure sensor 23 is provided in a suction pipe of the high-stage compressor 8. The pressure sensor 23 measures the pressure in the suction pipe of the high-stage compressor 8.
  • the control unit 40 calculates the degree of superheat of the refrigerant drawn into the high pressure side compressor 8 based on the temperature and pressure of the refrigerant measured by the second temperature sensor 22 and the pressure sensor 23.
  • control unit 40 adjusts the opening degree of the third expansion valve 33 according to the calculated degree of superheat of the refrigerant and the discharge temperature of the high-stage compressor 8. Specifically, when the discharge temperature of the high-stage compressor 8 is equal to or less than the predetermined first threshold value, the opening degree of the third expansion valve 33 is controlled to maintain the opening degree of the third expansion valve 33 . On the other hand, when the discharge temperature of the high-stage compressor 8 becomes higher than the predetermined first threshold, the third expansion valve 33 is set to set the opening degree of the third expansion valve 33 to the predetermined initial value. Is controlled.
  • the degree of opening of the third expansion valve 33 is reduced so as to decrease the degree of opening of the third expansion valve 33. It is controlled.
  • the degree of superheat of the refrigerant drawn into the high pressure side compressor 8 becomes higher than a predetermined second threshold value, the temperature of the third expansion valve 33 is adjusted according to the discharge temperature of the high pressure side compressor 8. The opening degree is maintained or the opening degree of the third expansion valve 33 is increased.
  • the third The opening degree of the third expansion valve 33 is controlled to maintain the opening degree of the expansion valve 33, and the opening degree of the third expansion valve 33 is increased when the opening degree of the third expansion valve 33 becomes higher than the first threshold.
  • the opening degree of 33 is controlled.
  • the pressure sensor 23 provided in the suction pipe of the high-stage compressor 8 is used to calculate the degree of superheat of the refrigerant drawn into the high-stage compressor 8.
  • third temperature sensors 24A, 24B, 24C provided in a pipe connected to the intermediate pressure receiver 13 may be used.
  • a third temperature sensor 24A provided in the refrigerant pipe 20 connecting the intermediate pressure receiver 13 and the evaporator (air heat exchanger) 17, a gas connecting the intermediate pressure receiver 13 and the suction pipe of the high stage compressor 8
  • At least one of the third temperature sensor 24B provided in the injection circuit 31 and the third temperature sensor 24C provided in a pipe connecting the condenser 11 and the intermediate pressure receiver 13 is used.
  • the third temperature sensor 24A can measure the temperature of the refrigerant that is a saturated liquid supplied from the intermediate pressure receiver 13 to the evaporator 17, and the third temperature sensor 24B receives the suction of the high-stage compressor 8 from the intermediate pressure receiver 13.
  • the temperature of the refrigerant that is a saturated gas supplied to the pipe can be measured, and the third temperature sensor 24C can measure the temperature of the gas-liquid two-phase refrigerant supplied to the intermediate pressure receiver 13.
  • the control unit 40 sets the temperature of the refrigerant drawn into the high-stage compressor 8 based on the temperature difference between the refrigerant measured by the first temperature sensor 21 and at least one of the third temperature sensors 24A, 24B, 24C. Calculate the degree of superheat.
  • the third temperature sensors 24A, 24B and 24C are provided instead of the pressure sensor 23, the configuration can be simplified and the cost can be reduced as compared with the case where the pressure sensor 23 is provided in the suction pipe of the high stage compressor 8.
  • step S1 the discharge temperature (hereinafter also referred to as “first temperature”) of the high-stage compressor 8 is detected (step S1). It is determined whether it is higher than one threshold (step S2).
  • the third expansion valve 33 continues to be closed.
  • the third expansion valve opening initial value setting command is sent to the third expansion valve 33 (step S3), and the opening degree of the third expansion valve 33 is predetermined. It is in the open state up to the initial value of. Thereby, the refrigerant cooled by the condenser 11 is supplied to the high stage compressor 8 through the liquid bypass circuit 32.
  • first superheat degree the high-stage compressor suction superheat degree (hereinafter also referred to as "first superheat degree") is calculated (step S4), and it is determined whether the first superheat degree is higher than a predetermined second threshold value. (Step S5). If the first degree of superheat is equal to or less than the second threshold, the third degree of expansion valve opening degree reduction command is sent to the third expansion valve 33 because the degree of suction superheat of the high-stage compressor 8 is low (step S6), the opening degree of the third expansion valve 33 is reduced. Thereafter, the detection of the first degree of superheat is continued (step S4), and the adjustment of the opening degree of the third expansion valve 33 is continuously performed.
  • the discharge temperature (first temperature) of the high-stage compressor 8 is detected (step S7), and the first temperature is higher than the predetermined first threshold. Is also determined (step S8).
  • the current opening degree of the third expansion valve 33 is continued. Thereafter, the detection of the first degree of superheat is continued (step S4), and the adjustment of the opening degree of the third expansion valve 33 is continuously performed.
  • step S9 when the first temperature becomes higher than the first threshold, the third expansion valve opening degree increase command is sent to the third expansion valve 33 (step S9), and the opening degree of the third expansion valve 33 is further opened. It will be As a result, the refrigerant cooled by the condenser 11 is more supplied to the high stage compressor 8 through the liquid bypass circuit 32. Thereafter, the detection of the first degree of superheat is continued (step S4), and the adjustment of the opening degree of the third expansion valve 33 is continuously performed.
  • the refrigerant cooled by the condenser 11 is continuously supplied to the high-stage compressor 8 through the liquid bypass circuit 32.
  • the degree of opening of the third expansion valve 33 is further opened, and the refrigerant cooled by the condenser 11 in the high-stage compressor 8 is more It can be supplied to suppress an increase in the first temperature and the first degree of superheat.
  • the heat pump water heater 1 according to the present embodiment is different from the heat pump water heater 1 according to the first embodiment only in the control unit 40, and the other configuration is the same (see FIG. 1 or FIG. 2). Therefore, in the following, in particular, the control unit 40 of the second embodiment will be described, and detailed description of overlapping components will be omitted.
  • the control unit 40 calculates the degree of superheat of the refrigerant drawn into the high pressure side compressor 8 based on the temperature and pressure of the refrigerant measured by the second temperature sensor 22 and the pressure sensor 23.
  • the temperature of the refrigerant measured by at least one of the third temperature sensors 24A, 24B, 24C may be used as in the first embodiment.
  • the control unit 40 adjusts the opening degree of the third expansion valve 33 in accordance with the calculated degree of superheat of the refrigerant and the discharge temperature of the high stage compressor 8. Further, the control unit 40 controls the number of rotations of the high pressure side compressor 8 in accordance with the discharge temperature of the high pressure side compressor 8.
  • the opening degree of the third expansion valve 33 is controlled to maintain the opening degree of the third expansion valve 33 .
  • the third expansion valve 33 is set to set the opening degree of the third expansion valve 33 to the predetermined initial value. Is controlled.
  • the degree of opening of the third expansion valve 33 is reduced so as to decrease the degree of opening of the third expansion valve 33. It is controlled.
  • the degree of superheat of the refrigerant drawn into the high pressure side compressor 8 becomes higher than a predetermined second threshold value, the temperature of the third expansion valve 33 is adjusted according to the discharge temperature of the high pressure side compressor 8. The opening degree is maintained or the opening degree of the third expansion valve 33 is increased.
  • the third Is the opening degree of the third expansion valve 33 controlled so as to maintain the opening degree of the expansion valve 33, and when it becomes higher than the first threshold value, does the opening degree of the third expansion valve 33 reach the maximum opening degree? It is judged whether or not.
  • the opening degree of the third expansion valve 33 when the opening degree of the third expansion valve 33 does not reach the maximum opening degree, the opening degree of the third expansion valve 33 is controlled to increase the opening degree of the third expansion valve 33, and When the opening degree of the third expansion valve 33 reaches the maximum opening degree, the rotational speed of the high-stage compressor 8 is controlled so as to decrease the rotational speed of the high-stage compressor 8.
  • the rotational speed of the low-stage compressor 7 is increased instead of controlling the rotational speed of the high-stage compressor 8.
  • the rotation speed of the low-stage compressor 7 may be controlled.
  • Steps S ⁇ b> 1 to S ⁇ b> 8 are the same as the control of the third expansion valve 33 in the first embodiment described above, and the description is omitted.
  • step S8 In a state where the first degree of superheat is higher than the second threshold, and after it is determined in step S8 whether the first temperature is higher than the predetermined first threshold, the first temperature is equal to or lower than the first threshold , And the current opening degree of the third expansion valve 33 is continued. Thereafter, the detection of the first degree of superheat is continued (step S4), and the adjustment of the opening degree of the third expansion valve 33 is continuously performed.
  • step S9 it is determined whether the opening degree of the third expansion valve 33 has reached the maximum opening degree.
  • the third expansion valve 33 opening degree increase command is sent to the third expansion valve 33 (step S10), and the opening degree of the third expansion valve 33 Is further opened.
  • the refrigerant cooled by the condenser 11 is more supplied to the high stage compressor 8 through the liquid bypass circuit 32.
  • the detection of the first degree of superheat is continued (step S4), and the adjustment of the opening degree of the third expansion valve 33 is continuously performed.
  • step S11 when the opening degree of the third expansion valve 33 has reached the maximum opening degree, the rotational speed of the high-stage compressor 8 is decreased (step S11). As a result, the discharge pressure of the low-stage compressor 7 is increased, and the suction pressure of the high-stage compressor 8 is also increased. As a result, as shown in FIG. 5, the difference between the suction pressure and the discharge pressure of the high-stage compressor 8 becomes smaller, and the difference is higher than in the case where the discharge pressure of the low-stage compressor 7 is not increased. The gas temperature of the refrigerant discharged from the stage compressor 8 can be reduced.
  • the low-stage side The rotational speed of the compressor 7 may be increased.
  • the rotational speed of the high-stage compressor 8 or the low-stage compressor 7 is adjusted.
  • the invention is not limited to this example.
  • the discharge pressure of the high-stage compressor 8 may be detected.
  • the rotational speed of the high-stage compressor 8 or the low-stage compressor 7 Adjustments may be made.

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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)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

L'objectif de la présente invention consiste à réduire la température d'un fluide frigorigène aspiré par un compresseur d'étage supérieur et à empêcher le compresseur d'étage supérieur d'aspirer un milieu liquide. Ce dispositif à cycle de réfrigération comporte une unité de compression possédant un compresseur d'étage inférieur (7) et un compresseur d'étage supérieur (8), un condenseur (11), un premier détendeur (12) et un évaporateur (17). Le dispositif à cycle de réfrigération est équipé : d'un circuit de dérivation de liquide (32) qui bifurque d'un tuyau raccordant le condenseur (11) et le premier détenteur (12), et rejoint un tuyau raccordant le compresseur d'étage inférieur (7) et le compresseur d'étage supérieur (8) ; d'un troisième détenteur (33) qui est disposé sur le circuit de dérivation de liquide (32) et ajuste la quantité du fluide frigorigène s'écoulant dans le circuit de dérivation de liquide (32) ; et d'un dispositif de commande (40) qui commande le troisième détenteur (33) et augmente la quantité du fluide frigorigène s'écoulant dans le circuit de dérivation de liquide (32) lorsque la température d'évacuation du compresseur d'étage supérieur (8) est supérieure à une valeur prédéfinie, et qui commande le troisième détenteur (33) et ajuste la quantité du fluide frigorigène s'écoulant dans le circuit de dérivation du liquide (32) sur la base du degré de surchauffe d'aspiration du compresseur d'étage supérieur (8).
PCT/JP2016/063963 2015-08-28 2016-05-11 Dispositif à cycle de réfrigération et procédé de commande de dispositif à cycle de réfrigération Ceased WO2017038161A1 (fr)

Priority Applications (3)

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KR1020177037231A KR102098164B1 (ko) 2015-08-28 2016-05-11 냉동 사이클 장치 및 냉동 사이클 장치의 제어 방법
EP16841193.2A EP3301380B1 (fr) 2015-08-28 2016-05-11 Dispositif à cycle de réfrigération et procédé de commande de dispositif à cycle de réfrigération
CN201680035531.1A CN107709895A (zh) 2015-08-28 2016-05-11 制冷循环装置及制冷循环装置的控制方法

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JP2015169268A JP2017044454A (ja) 2015-08-28 2015-08-28 冷凍サイクル装置及び冷凍サイクル装置の制御方法
JP2015-169268 2015-08-28

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DE102017204222A1 (de) * 2017-03-14 2018-09-20 Siemens Aktiengesellschaft Wärmepumpe und Verfahren zum Betreiben einer Wärmepumpe
CN107255309B (zh) * 2017-06-30 2020-06-23 美的集团武汉制冷设备有限公司 空调系统、控制方法及计算机可读存储介质
WO2020065999A1 (fr) * 2018-09-28 2020-04-02 三菱電機株式会社 Unité extérieure pour dispositif à cycle frigorifique, dispositif à cycle frigorifique, et dispositif de climatisation
US11460224B2 (en) 2018-10-31 2022-10-04 Emerson Climate Technologies, Inc. Oil control for climate-control system
CN111023605A (zh) * 2019-12-20 2020-04-17 北京工业大学 一种高压比制冷压缩机分流气液共进补气口协同降温方法
CN113340031B (zh) * 2021-05-27 2023-04-07 广东芬尼克兹节能设备有限公司 一种co2热泵系统的控制方法及其控制系统、存储介质
CN113639485B (zh) * 2021-07-23 2023-03-28 青岛海尔空调电子有限公司 用于调节热泵设备排气过热度的方法、装置和热泵设备
GB2614564A (en) * 2022-01-07 2023-07-12 Carno Heat Ltd Multistage compression system
JP2024005797A (ja) * 2022-06-30 2024-01-17 株式会社前川製作所 冷凍装置及び冷凍装置の制御方法

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KR20180011259A (ko) 2018-01-31
CN107709895A (zh) 2018-02-16
EP3301380B1 (fr) 2019-05-01
KR102098164B1 (ko) 2020-04-08
JP2017044454A (ja) 2017-03-02
EP3301380A1 (fr) 2018-04-04
EP3301380A4 (fr) 2018-04-18

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