EP3301380B1 - 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
EP3301380B1
EP3301380B1 EP16841193.2A EP16841193A EP3301380B1 EP 3301380 B1 EP3301380 B1 EP 3301380B1 EP 16841193 A EP16841193 A EP 16841193A EP 3301380 B1 EP3301380 B1 EP 3301380B1
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EP
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Prior art keywords
stage compressor
refrigerant
degree
temperature
predetermined value
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EP16841193.2A
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German (de)
English (en)
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EP3301380A1 (fr
EP3301380A4 (fr
Inventor
Minemasa Omura
Takuya Okada
Masahiro Teraoka
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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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 device and a refrigeration cycle device control method.
  • the lower the outside air temperature, the lower the refrigerant temperature and pressure at an inlet of an evaporator of a refrigerant become, and a suction pressure at an inlet of a compressor is also lowered.
  • the discharge pressure of the compressor is raised to a predetermined value, the lower the outside air temperature, the higher the temperature of the refrigerant which is discharged from the compressor rises.
  • JP 2009 192164 A discloses another example of refrigeration cycle device.
  • JP 2009 192164 A discloses a refrigeration cycle device according to the preamble of claim 1 and a method according to the preamble of claim 6 of controlling a refrigeration cycle device.
  • the refrigerant which is supplied to the suction pipe of the compressor is a supercooled liquid medium, and if the amount of the supplied liquid medium is large, the refrigerant at the inlet of the compressor enters a gas-liquid two-phase state. As a result, the compressor compresses liquid, and therefore, there is a concern that the compressor may be broken. Therefore, a method of supplying the supercooled liquid medium to the suction pipe of the compressor cannot be constantly performed, and thus the temperature rise of the compressor can be merely prevented intermittently.
  • the above-mentioned PTL 1 discloses a technique in which a liquid refrigerant is supplied between a low-stage compression mechanism and a high-stage compression mechanism to lower the temperature of the refrigerant which is sucked into the high-stage compressor. In this way, the discharge refrigerant temperature of the high-stage compression mechanism is lowered.
  • the amount of the liquid refrigerant which is supplied to the high-stage compression mechanism is large, the refrigerant at the inlet of the high-stage compression mechanism enters a gas-liquid two-phase state. Therefore, an appropriate amount of liquid medium needs to be supplied to the high-stage compressor.
  • the present invention has been made in view of such circumstances and has an object to provide a refrigeration cycle device and a refrigeration cycle device control method, in which it is possible to lower the temperature of a refrigerant which is sucked into a high-stage compressor and to prevent the high-stage compressor from sucking in a liquid medium.
  • the refrigeration cycle device has a refrigerant cycle in which a compression section having a low-stage compressor and a high-stage compressor, a condenser, an expansion section, and an evaporator are connected with one another by piping and a refrigerant is circulated, the refrigeration cycle device including: a bypass pipe which branches off from a pipe connecting the condenser and the expansion section with each other and joins a pipe connecting the low-stage compressor and the high-stage compressor with each other; a flow rate adjustment section which is provided in the bypass pipe and adjusts the amount of a refrigerant flowing through the bypass pipe; and a controller which controls the flow rate adjustment section to increase the amount of the refrigerant flowing through the bypass pipe, when a discharge temperature of the high-stage compressor is higher than a predetermined value, and controls the flow rate adjustment section to adjust the amount of the refrigerant flowing through the bypass pipe, based on a suction superheat
  • the refrigerant sent out from the condenser is branched through the bypass pipe before it is supplied to the expansion section, and is supplied between the low-stage compressor and the high-stage compressor.
  • the flow rate adjustment section adjusts the flow rate of the refrigerant while starting or stopping the flow of the refrigerant in the bypass pipe.
  • the flow rate adjustment section is controlled to increase the amount of the refrigerant flowing through the bypass pipe, so that the temperature of the refrigerant which is sucked into the high-stage compressor is lowered. Further, the flow rate adjustment section is controlled to adjust the amount of the refrigerant flowing through the bypass pipe, based on the suction superheat degree of the high-stage compressor. Therefore, control can be performed such that the refrigerant which is sucked into the high-stage compressor becomes superheated gas, and the compressor can be prevented from sucking a liquid refrigerant. Further, the degree of superheat of the refrigerant which is sucked into the high-stage compressor can be made to be constant, and therefore, the compressor can be prevented from becoming higher in temperature and being broken.
  • the controller may control the flow rate adjustment section to reduce the amount of the refrigerant flowing through the bypass pipe, when the suction superheat degree of the high-stage compressor is equal to or lower than a predetermined value.
  • the flow rate adjustment section is controlled to reduce the amount of the refrigerant flowing through the bypass pipe, and therefore, a decrease in the degree of superheat of the refrigerant which is sucked into the high-stage compressor can be suppressed.
  • the controller may control the flow rate adjustment section to increase the amount of the refrigerant flowing through the bypass pipe, 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 is higher than the predetermined value.
  • the flow rate adjustment section is controlled to increase the amount of the refrigerant flowing through the bypass pipe, and therefore, an increase in the degree of superheat of the refrigerant which is sucked into the high-stage compressor can be suppressed.
  • the controller may cause the flow rate adjustment section to maintain the amount of the refrigerant flowing through the bypass pipe, 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 is equal to or lower than the predetermined value.
  • the controller increases a discharge pressure of the refrigerant which is discharged from the low-stage compressor by controlling a rotational frequency of the low-stage compressor or 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 a discharge pressure of the high-stage compressor is higher than a predetermined value.
  • the rotational frequency of the high-stage compressor is decreased or the rotational frequency of the low-stage compressor is increased.
  • the flow rate adjustment section may be an expansion valve
  • the controller may control the rotational frequency of the low-stage compressor or the high-stage compressor when a degree of opening of the expansion valve has reached a maximum opening degree, when the discharge temperature of the high-stage compressor or the discharge pressure of the high-stage compressor is higher than a predetermined value.
  • the discharge temperature of the high-stage compressor can be reliably lowered by controlling the rotational frequency of the low-stage compressor or the high-stage compressor.
  • a method of controlling a refrigeration cycle device having a refrigerant cycle in which a compression section having a low-stage compressor and a high-stage compressor, a condenser, an expansion section, and an evaporator are connected by piping and a refrigerant is circulated, the refrigeration cycle device including a bypass pipe which branches off from a pipe connecting the condenser and the expansion section and joins a pipe connecting the low-stage compressor and the high-stage compressor, and a flow rate adjustment section which is provided in the bypass pipe and adjusts the amount of a refrigerant flowing through the bypass pipe, the method including: a step of increasing the amount of the refrigerant flowing through the bypass pipe by controlling the flow rate adjustment section when a discharge temperature of the high-stage compressor is higher than a predetermined value; a step of adjusting the amount of the refrigerant flowing through the bypass pipe by controlling the flow rate adjustment section, based on a suction superheat degree of
  • the present invention it is possible to lower the temperature of the refrigerant which is sucked into the high-stage compressor and to prevent the high-stage compressor from sucking in a liquid medium.
  • the heat pump water heater 1 is provided with a heat pump system (hereinafter simply referred to as a heat pump) 2, and a water circulation line 3 connected to a hot water storage tank unit (not shown), as shown in Fig. 1 .
  • a refrigeration cycle device is the heat pump 2
  • the refrigeration cycle device according to the present invention is not limited to this example.
  • the refrigeration cycle device according to the present invention can also be applied to an air conditioner or the like having a refrigerant cycle.
  • the water circulation line 3 on the hot water storage tank unit side is provided with a water supply-side line 3A connected to a water-side flow path of a condenser (a refrigerant/water heat exchanger) 11 in the heat pump 2, and a hot water extraction-side line 3B for extracting hot water produced in the condenser 11, and the water supply-side line 3A is provided with a water pump and a flow rate control valve.
  • a condenser a refrigerant/water heat exchanger
  • the heat pump 2 is configured with a closed cycle refrigerant circuit in which a compression section having a low-stage compressor 7 and a high-stage compressor 8, the condenser 11 dissipating the heat of a refrigerant gas, a first expansion valve 12 reducing the pressure of a refrigerant to an intermediate pressure, an intermediate pressure receiver 13 having a gas-liquid separation function, a second expansion valve 16 reducing the pressure of an intermediate pressure refrigerant such that the intermediate pressure refrigerant becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant, and an evaporator (an air heat exchanger) 17 performing heat exchange between the refrigerant and the outside air which is blown from a blower 18 are connected in this order through a refrigerant pipe.
  • a compression section having a low-stage compressor 7 and a high-stage compressor 8
  • the condenser 11 dissipating the heat of a refrigerant gas
  • a first expansion valve 12 reducing the pressure of
  • the condenser 11 of the heat pump 2 is a refrigerant/water heat exchanger, in which heat exchange between water and the refrigerant gas is performed by circulating a high-temperature and high-pressure refrigerant gas discharged from the compression section in a refrigerant-side flow path on one side and circulating water in a water-side flow path on the other side through the water circulation line 3. Then, the condenser 11 is configured so as to produce hot water by heating the water with the high-temperature and high-pressure refrigerant gas.
  • the refrigerant circuit is provided with a gas injection circuit 31 which supplies an intermediate pressure refrigerant gas separated in the intermediate pressure receiver 13 having a gas-liquid separation function to the high-stage compressor 8.
  • the gas injection circuit 31 may be provided with an electromagnetic valve and a check valve so as to be able to open and close the gas injection circuit 31 as necessary. Due to the economizer effect by gas injection, the heating capacity and the coefficient of performance (COP) by the heat pump 2 is improved, and thus the hot water supply capacity can be increased.
  • the refrigerant circuit is provided with a liquid bypass circuit 32 which supplies the refrigerant cooled by heat exchange with water in the condenser 11 to the high-stage compressor 8.
  • a third expansion valve 33 is provided in the liquid bypass circuit 32.
  • the heat pump water heater 1 if the heat pump 2 is operated, the high-temperature and high-pressure refrigerant gas compressed in two stages in the compression section is introduced into the condenser 11, where the high-temperature and high-pressure refrigerant gas is subjected to heat exchange with water which flows from the water supply-side line 3A of the water circulation line 3 to the water-side flow path.
  • the water is heated and increased in temperature by heat dissipation from the high-temperature and high-pressure refrigerant gas and then returned to a hot water storage tank (not shown) through the hot water extraction-side line 3B, and the heat exchange between the refrigerant and the water is continuously performed in the condenser 11 until the amount of hot water stored in the hot water storage tank reaches a predetermined amount. If the amount of stored hot water reaches the predetermined amount, the hot water storage operation is ended.
  • the refrigerant cooled by heat exchange with water in the condenser 11 is reduced in pressure by the first expansion valve 12 and reaches the intermediate pressure receiver 13 where the refrigerant is subjected to gas-liquid separation.
  • the intermediate pressure gas refrigerant separated in the intermediate pressure receiver 13 is supplied to the high-stage compressor 8 by the gas injection circuit 31, sucked into the high-stage compressor 8, and recompressed. Due to the economizer effect by the gas injection, the heating capacity and the coefficient of performance (COP) is improved, and thus the hot water supply capacity can be increased.
  • a liquid refrigerant separated in the intermediate pressure receiver 13 is reduced in pressure by the second expansion valve 16, becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant, and flows into the evaporator (an air heat exchanger) 17.
  • the refrigerant flowing into the evaporator 17 is subjected to heat exchange with the outside air which is blown by the blower, absorbs heat from the outside air, and is evaporated and gasified.
  • the refrigerant gasified in the evaporator 17 is sucked into the compression section and recompressed. Hereinafter, the same operation is repeated, whereby the production of hot water is performed.
  • a first temperature sensor 21 is provided in a discharge pipe of the high-stage compressor 8. The temperature of the refrigerant discharged from the high-stage compressor 8 (the discharge temperature of the high-stage compressor 8) is measured by the first temperature sensor 21.
  • a second temperature sensor 22 is provided in a portion after joining the liquid bypass circuit 32, of a suction pipe of the high-stage compressor 8. The temperature of the refrigerant which is sucked into the high-stage compressor 8 is measured by the second temperature sensor 22. Further, a pressure sensor 23 is provided in the suction pipe of the high-stage compressor 8. The pressure in the suction pipe of the high-stage compressor 8 is measured by the pressure sensor 23.
  • a controller 40 calculates the degree of superheat of the refrigerant which is sucked into the high-stage compressor 8, based on the temperature and pressure of the refrigerant measured by the second temperature sensor 22 and the pressure sensor 23.
  • controller 40 adjusts the degree of opening 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.
  • the degree of opening of the third expansion valve 33 is controlled such that the degree of opening of the third expansion valve 33 is maintained.
  • the degree of opening of the third expansion valve 33 is controlled such that the degree of opening of the third expansion valve 33 is set to a predetermined initial value.
  • the degree of opening of the third expansion valve 33 is controlled such that the degree of opening of the third expansion valve 33 is reduced.
  • the degree of opening of the third expansion valve 33 is maintained or increased according to the discharge temperature of the high-stage compressor 8.
  • the degree of opening of the third expansion valve 33 is controlled such that the degree of opening of the third expansion valve 33 is maintained, and when the discharge temperature of the high-stage compressor 8 becomes higher than the predetermined first threshold value, the degree of opening of the third expansion valve 33 is controlled such that the degree of opening of the third expansion valve 33 is increased.
  • any one of the third temperature sensor 24A which is provided in a refrigerant pipe 20 connecting the intermediate pressure receiver 13 and the evaporator (an air heat exchanger) 17, the third temperature sensor 24B which is provided in the gas injection circuit 31 connecting the intermediate pressure receiver 13 and the suction pipe of the high-stage compressor 8, and the third temperature sensor 24C which is 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 which is supplied from the intermediate pressure receiver 13 to the evaporator 17, the third temperature sensor 24B can measure the temperature of the refrigerant that is a saturated gas which is supplied from the intermediate pressure receiver 13 to the suction pipe of the high-stage compressor 8, and the third temperature sensor 24C can measure the temperature of the gas-liquid two-phase refrigerant which is supplied to the intermediate pressure receiver 13.
  • the controller 40 calculates the degree of superheat of the refrigerant which is sucked into the high-stage compressor 8, based on the difference between the temperatures of the refrigerant measured by at least one of the third temperature sensors 24A, 24B, and 24C and the first temperature sensor 21.
  • the third temperature sensors 24A, 24B, and 24C are provided instead of the pressure sensor 23, as compared with a case where the pressure sensor 23 is provided in the suction pipe of the high-stage compressor 8, a configuration can be simplified and the cost can also be reduced.
  • step S1 the discharge temperature (hereinafter also referred to as a "first temperature") of the high-stage compressor 8 is detected (step S1), and whether or not the first temperature is higher than a predetermined first threshold value is determined (step S2).
  • a third expansion valve opening degree initial value setting command is sent to the third expansion valve 33 (step S3), and a state is created where the degree of opening of the third expansion valve 33 is opened to a predetermined initial value.
  • the refrigerant cooled in the condenser 11 is supplied to the high-stage compressor 8 through the liquid bypass circuit 32.
  • a high-stage compressor suction superheat degree (hereinafter also referred to as a "first degree of superheat") is calculated (step S4), and whether or not the first degree of superheat is higher than a predetermined second threshold value is determined (step S5).
  • a third expansion valve opening degree reduction command is sent to the third expansion valve 33 (step S6), and the degree of opening of the third expansion valve 33 is reduced.
  • the detection of the first degree of superheat is continued (step S4), and the adjustment of the degree of opening of the third expansion valve 33 is continuously performed.
  • the discharge temperature (the first temperature) of the high-stage compressor 8 is detected (step S7), and whether or not the first temperature is higher than the predetermined first threshold value is determined (step S8) .
  • the current degree of opening 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 degree of opening of the third expansion valve 33 is continuously performed.
  • a third expansion valve opening degree increase command is sent to the third expansion valve 33 (step S9), and a state is created where the degree of opening of the third expansion valve 33 is further opened.
  • a greater amount of refrigerant cooled in the condenser 11 is 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 degree of opening of the third expansion valve 33 is continuously performed.
  • the refrigerant cooled in the condenser 11 continues to be supplied to the high-stage compressor 8 through the liquid bypass circuit 32. Further, in a case where the first temperature becomes higher than the first threshold value, a state is created where the degree of opening of the third expansion valve 33 is further opened, and thus a greater amount of refrigerant cooled in the condenser 11 is supplied to the high-stage compressor 8, so that an increase in the first temperature and the first degree of superheat can be suppressed.
  • the heat pump water heater 1 according to this embodiment is different in only the controller 40 from that of the first embodiment, and other configurations are the same as those of the first embodiment (refer to Fig. 1 or Fig. 2 ). Therefore, in the following, in particular, a controller 40 of the second embodiment will be described, and detailed description of the overlapping components will be omitted.
  • the controller 40 calculates the degree of superheat of the refrigerant which is sucked into the high-stage 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, and 24C may be used.
  • the controller 40 adjusts the degree of opening 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. Further, the controller 40 controls the rotational frequency of the high-stage compressor 8 according to the discharge temperature of the high-stage compressor 8.
  • the degree of opening of the third expansion valve 33 is controlled such that the degree of opening of the third expansion valve 33 is maintained.
  • the degree of opening of the third expansion valve 33 is controlled such that the degree of opening of the third expansion valve 33 is set to a predetermined initial value.
  • the degree of opening of the third expansion valve 33 is controlled such that the degree of opening of the third expansion valve 33 is reduced.
  • the degree of opening of the third expansion valve 33 is maintained or increased according to the discharge temperature of the high-stage compressor 8.
  • the degree of opening of the third expansion valve 33 is controlled such that the degree of opening of the third expansion valve 33 is maintained, and when the discharge temperature of the high-stage compressor 8 becomes higher than the first threshold value, whether or not the degree of opening of the third expansion valve 33 has reached the maximum opening degree is determined.
  • the degree of opening of the third expansion valve 33 is controlled such that the degree of opening of the third expansion valve 33 is increased, and when the degree of opening of the third expansion valve 33 has reached the maximum opening degree, the rotational frequency of the high-stage compressor 8 is controlled such that the rotational frequency of the high-stage compressor 8 is reduced.
  • the rotational frequency of the low-stage compressor 7 may be controlled such that the rotational frequency of the low-stage compressor 7 is increased
  • Steps S1 to S8 are the same as those in the control of the third expansion valve 33 in the first embodiment described above, and therefore, description thereof is omitted.
  • step S8 In a state where the first degree of superheat is higher than the second threshold value, in step S8, whether or not the first temperature is higher than the predetermined first threshold value is determined, and thereafter, in a case where the first temperature is equal to or lower than the first threshold value, the current degree of opening 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 degree of opening of the third expansion valve 33 is continuously performed.
  • step S9 whether or not the degree of opening of the third expansion valve 33 has reached the maximum opening degree is determined.
  • step S10 a command to increase the degree of opening of the third expansion valve 33 is sent to the third expansion valve 33 (step S10), and a state is created where the degree of opening of the third expansion valve 33 is further opened. In this way, a greater amount of refrigerant cooled in the condenser 11 is 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 degree of opening of the third expansion valve 33 is continuously performed.
  • step S11 the rotational frequency of the high-stage compressor 8 is reduced (step S11).
  • the suction pressure of the high-stage compressor 8 also rises.
  • Fig. 5 compared to a case where the difference between the suction pressure and the discharge pressure of the high-stage compressor 8 becomes smaller, and thus the adjustment to raise the discharge pressure of the low-stage compressor 7 is not performed, it is possible to lower the gas temperature of the refrigerant which is discharged from the high-stage compressor 8.
  • step S11 the rotational frequency of the high-stage compressor 8 is reduced in a case where the degree of opening of the third expansion valve 33 has reached the maximum opening degree.
  • the rotational frequency of the low-stage compressor 7 may be increased.
  • the present invention is not limited to this example.
  • detection of the discharge pressure of the high-stage compressor 8 may be performed.
  • adjustment of the rotational frequency of the high-stage compressor 8 or the low-stage compressor 7 may be performed.

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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)

Claims (6)

  1. Dispositif à cycle de réfrigération (2) ayant un cycle de réfrigérant dans lequel une section de compression ayant un compresseur d'étage inférieur (7) et un compresseur d'étage supérieur (8), un condensateur (11), une section d'expansion et un évaporateur (17) sont raccordés entre eux par tuyauterie et un réfrigérant circule, le dispositif à cycle de réfrigération comprenant :
    un tuyau de dérivation qui se ramifie d'un tuyau raccordant le condensateur (11) et la section d'expansion entre eux et rejoint un tuyau raccordant le compresseur d'étage inférieur (7) et le compresseur d'étage supérieur (8) entre eux ;
    une section d'ajustement de débit qui est prévue dans le tuyau de dérivation et est configurée pour ajuster la quantité de réfrigérant s'écoulant par le tuyau de dérivation ; et
    un organe de commande (40) qui est configuré pour commander la section d'ajustement de débit afin d'augmenter la quantité de réfrigérant qui s'écoule dans le tuyau de dérivation, lorsqu'une température de décharge du compresseur d'étage supérieur (8) est supérieure à une valeur prédéterminée, et pour réguler la section d'ajustement de débit afin d'ajuster la quantité de réfrigérant qui s'écoule par le tuyau de dérivation, sur la base d'un degré de surchauffe d'aspiration du compresseur d'étage supérieur (8),
    dans lequel l'organe de commande (40) est configuré pour augmenter une pression de décharge du réfrigérant qui est déchargé par le compresseur d'étage inférieur (7) en contrôlant une fréquence de rotation du compresseur d'étage inférieur (7) ou du compresseur d'étage supérieur (8), lorsque le degré de surchauffe d'aspiration du compresseur d'étage supérieur (8) est supérieur à une valeur prédéterminée, et que la température de décharge du compresseur d'étage supérieur (8) ou une pression de décharge du compresseur d'étage supérieur (8) est supérieure à une valeur prédéterminée.
  2. Dispositif à cycle de réfrigération (2) selon la revendication 1, dans lequel l'organe de commande (40) est configuré pour commander la section d'ajustement de débit afin de réduire la quantité de réfrigérant qui s'écoule par le tuyau de dérivation, lorsque le degré de surchauffe d'aspiration du compresseur d'étage supérieur (8) est égal ou inférieur à une valeur prédéterminée.
  3. Dispositif à cycle de réfrigération (2) selon la revendication 1 ou 2, dans lequel l'organe de commande (40) est configuré pour commander la section d'ajustement de débit afin d'augmenter la quantité de réfrigérant qui s'écoule par le tuyau de dérivation, lorsque le degré de surchauffe d'aspiration du compresseur d'étage supérieur (8) est supérieur à une valeur prédéterminée et que la température de décharge du compresseur d'étage supérieur (8) est supérieure à la valeur prédéterminée.
  4. Dispositif à cycle de réfrigération (2) selon la revendication 1 ou 2, dans lequel l'organe de commande (40) est configuré pour amener la section d'ajustement de débit à maintenir la quantité de réfrigérant qui s'écoule par le tuyau de dérivation, lorsque le degré de surchauffe d'aspiration du compresseur d'étage supérieur (8) est supérieur à une valeur prédéterminée et que la température de décharge du compresseur d'étage supérieur (8) est égale ou inférieure à la valeur prédéterminée.
  5. Dispositif à cycle de réfrigération (2) selon la revendication 1, dans lequel la section d'ajustement de débit est une valve d'expansion (33), et
    l'organe de commande (40) est configuré pour commander la fréquence de rotation du compresseur d'étape inférieur (7) ou du compresseur d'étage supérieur (8) lorsqu'un degré d'ouverture de la valve d'expansion (33) a atteint un degré d'ouverture maximum, lorsque la température de décharge du compresseur d'étage supérieur (8) ou la pression de décharge du compresseur d'étage supérieur (8) est supérieure à une valeur prédéterminée.
  6. Procédé pour commander un dispositif à cycle de réfrigération (2) ayant un cycle de réfrigérant dans lequel une section de compression ayant un compresseur d'étage inférieur (7) et un compresseur d'étage supérieur (8), un condensateur (11), une section d'expansion et un évaporateur (17) sont raccordés par tuyauterie et le réfrigérant circule, le dispositif à cycle de réfrigération (2) comprenant un tuyau de dérivation qui se ramifie à partir d'un tuyau raccordant le condensateur (11) et la section d'expansion et rejoint un tuyau raccordant le compresseur d'étage inférieur (7) et le compresseur d'étage supérieur (8), et une section d'ajustement de débit qui est prévue dans le tuyau de dérivation et ajuste la quantité d'un réfrigérant qui s'écoule par le tuyau de dérivation, le procédé comprenant :
    une étape d'augmentation de la quantité de réfrigérant qui s'écoule dans le tuyau de dérivation en commandant la section d'ajustement de débit lorsqu'une température de décharge du compresseur d'étage supérieur (8) est supérieure à une valeur prédéterminée ;
    une étape d'ajustement de la quantité du réfrigérant qui s'écoule dans le tuyau de dérivation en commandant la section d'ajustement de débit, sur la base d'un degré de surchauffe d'aspiration du compresseur d'étage supérieur (8) ; et
    une étape pour augmenter une pression de décharge d'un réfrigérant qui est déchargé du compresseur d'étage inférieur (7) en contrôlant une fréquence de rotation d'un compresseur d'étage inférieur (7) ou du compresseur d'étage supérieur (8), lorsque le degré de surchauffe d'aspiration du compresseur d'étage supérieur (8) est supérieur à une valeur prédéterminée, et que la température de décharge du compresseur d'étage supérieur (8) ou une pression de décharge du compresseur d'étage supérieur (8) est supérieure à une valeur prédéterminée.
EP16841193.2A 2015-08-28 2016-05-11 Dispositif à cycle de réfrigération et procédé de commande de dispositif à cycle de réfrigération Active EP3301380B1 (fr)

Applications Claiming Priority (2)

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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
PCT/JP2016/063963 WO2017038161A1 (fr) 2015-08-28 2016-05-11 Dispositif à cycle de réfrigération et procédé de commande de dispositif à cycle de réfrigération

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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***、控制方法及计算机可读存储介质
CN112714853B (zh) * 2018-09-28 2022-11-29 三菱电机株式会社 制冷循环装置的室外机、制冷循环装置以及空调装置
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***的控制方法及其控制***、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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WO2017038161A1 (fr) 2017-03-09
CN107709895A (zh) 2018-02-16
EP3301380A1 (fr) 2018-04-04
EP3301380A4 (fr) 2018-04-18
KR102098164B1 (ko) 2020-04-08
JP2017044454A (ja) 2017-03-02
KR20180011259A (ko) 2018-01-31

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