WO2018110185A1 - Système de circuit de fluide frigorigène et procédé de commande d'un tel système - Google Patents

Système de circuit de fluide frigorigène et procédé de commande d'un tel système Download PDF

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Publication number
WO2018110185A1
WO2018110185A1 PCT/JP2017/040965 JP2017040965W WO2018110185A1 WO 2018110185 A1 WO2018110185 A1 WO 2018110185A1 JP 2017040965 W JP2017040965 W JP 2017040965W WO 2018110185 A1 WO2018110185 A1 WO 2018110185A1
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Prior art keywords
refrigerant
enthalpy
temperature
heat exchanger
gas
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PCT/JP2017/040965
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English (en)
Japanese (ja)
Inventor
道明 中西
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三菱重工サーマルシステムズ株式会社
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Priority to EP17881376.2A priority Critical patent/EP3460357A4/fr
Publication of WO2018110185A1 publication Critical patent/WO2018110185A1/fr

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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using 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
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/08—Exceeding a certain temperature value in a refrigeration component or 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
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2103—Temperatures near a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to a refrigerant circuit system including a gas-liquid heat exchanger and a method for controlling the refrigerant circuit system.
  • Patent Document 1 In order to suppress the temperature of the compressor to an allowable temperature, there is an example in which only a part of the low-pressure refrigerant that has passed through the evaporator is passed through the gas-liquid heat exchanger and the rest is bypassed (Patent Document 1). That is, the flow rate of the low-pressure refrigerant radiated from the high-pressure refrigerant is adjusted by bypass.
  • Patent Document 1 a bypass path and a bypass valve are provided on the outlet side of the evaporator, and low-pressure refrigerant is sucked into the compressor from the bypass path.
  • an object of the present invention is to provide a refrigerant circuit system and a refrigerant circuit system control method that can promote supercooling while appropriately controlling the temperature of the compressor.
  • the present invention is a refrigerant circuit system including a compressor, a condenser, a decompression unit, and an evaporator.
  • the refrigerant circuit system further includes a high-pressure refrigerant that has passed through the condenser and a low-pressure refrigerant that has passed through the evaporator.
  • a gas-liquid heat exchanger that exchanges heat, a bypass path that accepts at least a portion of the high-pressure refrigerant that goes from the condenser to the gas-liquid heat exchanger, and bypasses it upstream from the decompression section, and a high pressure that flows into the bypass path
  • a flow rate adjustment unit capable of adjusting the flow rate of the refrigerant
  • a control unit that gives a command according to the flow rate to the flow rate adjustment unit, the control unit corresponding to the detected temperature of the discharged refrigerant discharged from the compressor
  • the discharge enthalpy which is the enthalpy, is h1, the difference between the enthalpy corresponding to the detected temperature of the refrigerant at the inlet of the gas-liquid heat exchanger and the enthalpy corresponding to the detected temperature of the refrigerant at the outlet of the gas-liquid heat exchanger En Based on hv, h1 and ⁇ h, the target discharge enthalpy corresponding to the target discharge
  • the increase / decrease ratio from the current flow rate of the high-pressure refrigerant flowing into the bypass path is determined on the assumption that the difference in compatible enthalpy, which is the difference, is ⁇ h ′.
  • the target temperature range including the target temperature Tv and having the upper limit temperature and the lower limit temperature is set, and the control unit sets the upper limit discharge corresponding to the upper limit temperature from the lower limit discharge enthalpy corresponding to the lower limit temperature. It is preferable to obtain a suitable enthalpy difference ⁇ h ′ that can accommodate the target discharge enthalpy hv by the enthalpy.
  • the refrigerant circuit system of the present invention is an outdoor unit that functions as a condenser during cooling operation and functions as an evaporator during heating operation, by switching between cooling operation and heating operation by changing the direction of refrigerant flow.
  • the indoor heat exchanger Positioned between the heat exchanger, the indoor heat exchanger that functions as an evaporator during cooling operation, and functions as a condenser during heating operation, and the gas-liquid heat exchanger and evaporator during cooling operation, and functions as a decompression unit
  • the air conditioner includes a cooling decompression unit, and a heating decompression unit that is located between the gas-liquid heat exchanger and the evaporator during heating operation and functions as a decompression unit.
  • the present invention is also a control method for a refrigerant circuit system including a compressor, a condenser, a decompression unit, and an evaporator, wherein the refrigerant circuit system further passes through the high-pressure refrigerant that has passed through the condenser and the evaporator.
  • a gas-liquid heat exchanger for exchanging heat with the low-pressure refrigerant, a bypass path for accepting at least a part of the high-pressure refrigerant from the condenser to the gas-liquid heat exchanger, and bypassing upstream of the decompression unit, and a bypass path
  • a flow rate adjustment unit capable of adjusting the flow rate of the high-pressure refrigerant flowing into the compressor, and detecting the temperature of the refrigerant discharged from the compressor; and the temperature of the refrigerant at the inlet of the gas-liquid heat exchanger
  • the step of detecting, the step of detecting the temperature of the refrigerant at the outlet of the gas-liquid heat exchanger, and the discharge enthalpy corresponding to the detected temperature of the discharged refrigerant is h1, the detected temperature of the refrigerant at the inlet Assuming that the enthalpy difference that is the difference between the corresponding enthalpy and the enthalpy corresponding to the detected temperature of the refrigerant
  • the target temperature range including the target temperature Tv and having the upper limit temperature and the lower limit temperature is set, and in the step of obtaining ⁇ h ′, from the lower limit discharge enthalpy corresponding to the lower limit temperature It is preferable to obtain a suitable enthalpy difference ⁇ h ′ that can accommodate the target discharge enthalpy hv by the upper limit discharge enthalpy corresponding to the upper limit temperature.
  • the temperature of the discharged refrigerant is derived so as to be within the target temperature Tv ( ⁇ h ′).
  • the refrigerant flowing through the gas-liquid heat exchanger and the refrigerant flowing through the bypass path based on the present and future ratio ( ⁇ h ′ / ⁇ h) of the magnitude of the effect of the heat exchange amount by the gas-liquid heat exchanger.
  • a refrigerant circuit system 1 shown in FIG. 1 includes a refrigerant circuit through which refrigerant circulates.
  • the refrigerant circuit system 1 is an air conditioner that uses a refrigeration cycle, and exchanges heat between an outdoor unit (not shown) having an outdoor heat exchanger 11 that exchanges heat between outdoor air and refrigerant, and indoor air and refrigerant. And an indoor unit (not shown) having the indoor heat exchanger 12.
  • the refrigerant circuit system 1 includes a four-way valve 13 capable of switching the direction of the circulating refrigerant flow, and is configured to be switched between a cooling operation and a heating operation by operating the four-way valve 13.
  • the refrigerant flow during cooling is indicated by solid arrows.
  • the path B shown by a broken line is opened, so that the refrigerant flows in the direction opposite to that during cooling (broken arrow in FIG. 1).
  • the outdoor heat exchanger 11 functions as a condenser during the cooling operation, and functions as an evaporator during the heating operation.
  • the indoor heat exchanger 12 functions as an evaporator during cooling operation, and functions as a condenser during heating operation.
  • the refrigerant circuit system 1 includes a fan 11 ⁇ / b> F that blows air to the outdoor heat exchanger 11 and a fan 12 ⁇ / b> F that blows air toward the indoor heat exchanger 12.
  • the outdoor heat exchanger 11 and the indoor heat exchanger 12 shown in FIG. 1 are denoted as a condenser and an evaporator, respectively, as functions during cooling operation.
  • the outdoor heat exchanger 11 is referred to as a condenser 11 and the indoor heat exchanger 12 is referred to as an evaporator 12 on the basis of cooling.
  • the refrigerant circuit system 1 includes a compressor 14, a condenser 11, a decompression unit 15 (151, 152), and an evaporator 12 as basic elements.
  • a decompression unit 15 As the decompression unit 15, two decompression units 151 for cooling operation and decompression unit 152 for heating operation are prepared.
  • the decompression unit 151 for cooling operation does not function during heating operation.
  • the decompression unit 152 for heating operation does not function during the cooling operation.
  • the refrigerant circuit system 1 includes a gas-liquid heat exchanger 20 that exchanges heat between the low-pressure refrigerant that has passed through the evaporator 12 and the high-pressure refrigerant that has passed through the condenser 11, and gas-liquid heat.
  • a bypass path 21 that bypasses part of the high-pressure refrigerant that goes to the exchanger 20 to the upstream side of the decompression unit 151, a bypass valve 22 that can adjust the flow rate of the high-pressure refrigerant that flows into the bypass path 21, and the bypass valve 22
  • a control unit 25 for giving an opening degree.
  • the gas-liquid heat exchanger 20 includes a high-pressure path 201 through which a high-pressure refrigerant flows and a low-pressure path 202 through which a low-pressure refrigerant flows.
  • the high-pressure refrigerant flowing through the high-pressure path 201 and the low-pressure refrigerant flowing through the low-pressure path 202 can exchange heat.
  • the bypass path 21 receives a part of the high-pressure refrigerant from the upstream side of the high-pressure path 201 and makes a bypass downstream of the high-pressure path 201 and upstream of the decompression unit 151.
  • the high-pressure refrigerant that has flowed into the gas-liquid heat exchanger 20 through the condenser 11 is supercooled by radiating heat to the low-pressure refrigerant, as indicated by 100 in FIG. 2, and the enthalpy is lowered. Thereafter, the pressure is reduced by the pressure reducing unit 151 and flows to the evaporator 12. While the high-pressure refrigerant is supercooled by the gas-liquid heat exchanger 20, the low-temperature and low-pressure refrigerant that has passed through the evaporator 12 absorbs heat from the high-pressure refrigerant and is overheated as indicated by 101 in FIG. If it does so, the temperature of the refrigerant
  • the predetermined target temperature Tv allowed for the compressor 14 is determined in consideration of the performance of the lubricating oil used for the sliding portion of the compressor 14 and the performance of the motor when the motor is built in the compressor 14. be able to.
  • a target temperature Tv that is the temperature of the refrigerant flowing through the discharge pipe that discharges the refrigerant compressed by the compressor 14 to the outside of the compressor 14 is determined.
  • a target temperature range including the target temperature Tv and including the upper limit temperature X and the lower limit temperature X- ⁇ is set.
  • the temperature of the compressor 14 is kept from the lower limit temperature X- ⁇ to the upper limit temperature X while obtaining the supercooling effect as much as possible by the gas-liquid heat exchanger 20.
  • 22 is used to adjust the flow rate of the high-pressure refrigerant flowing through the bypass path 21.
  • an opening degree command according to the flow rate is given from the control unit 25 to the bypass valve 22
  • the opening amount of the bypass valve 22 is changed according to the opening degree command, so that the flow rate of the refrigerant flowing through the bypass path 21 is adjusted.
  • the control unit 25 performs a calculation.
  • the refrigerant circuit system 1 of the present embodiment includes a condenser temperature sensor 11A, a discharge temperature sensor 14A, an inlet temperature sensor 20A, and an outlet temperature sensor 20B.
  • the condenser temperature sensor 11 ⁇ / b> A detects the temperature of the gas-liquid two-phase refrigerant flowing through the condenser 11.
  • the temperature detected by the condenser temperature sensor 11A is regarded as the temperature of the saturated vapor, and the pressure of the high-pressure refrigerant can be obtained as the corresponding saturated vapor pressure.
  • the outdoor unit is provided with a pressure gauge indicating the pressure of the high-pressure refrigerant
  • the value measured by the pressure gauge can be used as the pressure of the high-pressure refrigerant.
  • the refrigerant circuit system 1 is also provided with a temperature sensor 12A for detecting the temperature of the gas-liquid two-phase refrigerant flowing through the indoor heat exchanger 12 that functions as a condenser during the heating operation for control during the heating operation. Yes.
  • the pressure of the high-pressure refrigerant can be obtained using the temperature detected by the temperature sensor 12A.
  • the discharge temperature sensor 14 ⁇ / b> A detects the temperature of refrigerant (hereinafter referred to as discharge refrigerant) flowing through the discharge pipe of the compressor 14.
  • the inlet temperature sensor 20 ⁇ / b> A detects the temperature of the high-pressure refrigerant that flows into the inlet of the gas-liquid heat exchanger 20.
  • the outlet temperature sensor 20 ⁇ / b> B detects the temperature of the high-pressure refrigerant that flows out from the outlet of the gas-liquid heat exchanger 20.
  • the control unit 25 uses the pressure of the high-pressure refrigerant based on the measurement value by the condenser temperature sensor 11A or obtained by the pressure gauge and the temperature Td of the discharge refrigerant detected by the discharge temperature sensor 14A to Get h1 which is enthalpy. Further, the enthalpy h2 of the refrigerant at the inlet of the gas-liquid heat exchanger 20 is obtained using the temperature detected by the inlet temperature sensor 20A and the pressure of the high-pressure refrigerant, and further, the temperature and high pressure detected by the outlet temperature sensor 20B.
  • the refrigerant enthalpy h3 at the outlet of the gas-liquid heat exchanger 20 is acquired using the refrigerant pressure.
  • the enthalpy difference ⁇ h is obtained by the calculation of h2 ⁇ h3. This corresponds to the effect of supercooling of the high-pressure refrigerant by the gas-liquid heat exchanger 20, in other words, the effect of overheating of the low-pressure refrigerant.
  • the case where the high-pressure refrigerant does not flow through the gas-liquid heat exchanger 20 corresponds to the case where the opening degree of the bypass valve 22 is fully opened in the present embodiment.
  • ⁇ h ′ is a suitable enthalpy difference that matches the target discharge enthalpy hv.
  • the control unit 25 can calculate ⁇ h ′ by calculating hv ⁇ h1 ′. From the ratio between this ⁇ h ′ and the current enthalpy difference ⁇ h based on the detected temperature, the control unit 25 obtains a control amount of the refrigerant flow rate to be bypassed through the bypass path 21 and gives it to the bypass valve 22 as an opening degree.
  • the control unit 25 presents the current flow rate of the high-pressure refrigerant that flows into the bypass path 21 based on the current ratio ( ⁇ h ′ / ⁇ h). An opening / closing command corresponding to the flow rate multiplied by the increasing / decreasing ratio is given to the bypass valve 22.
  • the target discharge enthalpy hv is widened so that the temperature of the discharged refrigerant falls within a predetermined temperature range including the target temperature Tv, and ⁇ h ′ is calculated so as to fit from the upper limit to the lower limit of the enthalpy. It is preferable.
  • the operation by the control unit 25 has been described by taking the cooling operation as an example, but the same applies to the heating operation.
  • the switching operation of the four-way valve 13 causes the refrigerant to flow in the order of the compressor 14, the indoor heat exchanger 12 as a condenser, the decompression unit 152, the gas-liquid heat exchanger 20, and the outdoor heat exchanger 11 as an evaporator. Circulate. Since the inlet and outlet of the gas-liquid heat exchanger 20 are opposite to those during cooling operation, the enthalpy difference ⁇ h due to heat exchange in the gas-liquid heat exchanger 20 is determined from the enthalpy h3 corresponding to the temperature detected by the temperature sensor 20B.
  • h3-h2 obtained by subtracting enthalpy h2 corresponding to the temperature detected by sensor 20A. Except that the enthalpy difference ⁇ h corresponds to h3 ⁇ h2, and the discharge enthalpy h1 is obtained using the pressure of the high-pressure refrigerant corresponding to the condenser temperature detected by the temperature sensor 12A of the indoor heat exchanger 12. The same processing as in the cooling operation can be performed.
  • ⁇ Gr corresponds to an increase / decrease magnification of the heat exchange amount by the gas-liquid heat exchanger 20.
  • the control unit 25 calculates according to the procedure shown in FIG. 3 and changes the opening degree of the bypass valve 22 based on the calculated ⁇ Gr. Under the restriction of the temperature of the compressor 14, it is preferable to promote supercooling by flowing a high-pressure refrigerant through the gas-liquid heat exchanger 20 as much as possible. In the present embodiment, the operation is started with the bypass valve 22 fully closed.
  • the cooling operation first, as described above, the pressure of the high-pressure refrigerant obtained by using the condenser temperature sensor 11A or the pressure gauge and the temperature Td of the discharged refrigerant detected by the discharge temperature sensor 14A are used. A discharge enthalpy h1 is acquired (step S1).
  • step S2 using the temperatures detected by the temperature sensors 20A and 20B, the enthalpy h2 of the refrigerant at the inlet of the gas-liquid heat exchanger 20 and the enthalpy h3 of the refrigerant at the outlet are acquired, and enthalpy by gas-liquid heat exchange is obtained.
  • the difference ⁇ h is calculated (step S2).
  • an enthalpy difference ⁇ h ′ corresponding to the heat exchange amount of the gas-liquid heat exchanger 20 necessary for keeping the temperature of the discharged refrigerant at the target temperature Tv is calculated (step S3).
  • the target temperature range is set using a threshold value.
  • This target temperature range includes the target temperature Tv, and has an upper limit temperature X and a lower limit temperature (X ⁇ ).
  • An enthalpy range including the target discharge enthalpy hv is set by the upper limit discharge enthalpy corresponding to the upper limit temperature X and the lower limit discharge enthalpy corresponding to the lower limit temperature (X ⁇ ).
  • the control unit 25 makes the target discharge enthalpy hv fall within the upper limit enthalpy corresponding to the temperature (X ⁇ ) and lower than the upper limit enthalpy corresponding to the temperature X. ⁇ h ′ allowed to be added to the discharge enthalpy h1 ′ is calculated.
  • the ratio ( ⁇ h ′ / ⁇ h) between ⁇ h ′ and ⁇ h is calculated as the increase / decrease magnification ⁇ Gr of the gas-liquid heat exchange amount (step S4). If ⁇ Gr is smaller than 1, it is necessary to reduce the flow rate of the high-pressure refrigerant flowing through the gas-liquid heat exchanger 20 in order to suppress the temperature of the discharged refrigerant. On the other hand, if ⁇ Gr is greater than 1, the temperature of the discharged refrigerant is lower than the allowable temperature of the compressor 14, so the flow rate of the high-pressure refrigerant flowing through the gas-liquid heat exchanger 20 is increased from the current level. There is room to promote liquefaction of
  • the opening degree of the bypass valve 22 can be changed according to the following procedure according to the calculated ⁇ Gr. For example, when ⁇ Gr is smaller than 1 (Y in step S5), the flow rate of the high-pressure refrigerant flowing through the gas-liquid heat exchanger 20 is reduced unless the opening degree of the bypass valve 22 is fully open (N in step S6). Then, an opening degree command for increasing the opening degree is given to the bypass valve 22 (step S7). Then, the bypass valve 22 is driven to an opening amount corresponding to the current (1 / ⁇ Gr) times based on the opening command. For example, the bypass valve 22 is driven by a driving pulse whose number of pulses per unit time is about (1 / ⁇ Gr) times the current time. For example, the minimum pulse number is set to 0.01 or the like so that the bypass valve 22 can be opened even if the current pulse number is 0 because the bypass valve 22 is fully closed.
  • step S8 When ⁇ Gr is greater than 1 (Y in step S8), the flow rate of the high-pressure refrigerant flowing through the gas-liquid heat exchanger 20 is increased unless the opening degree of the bypass valve 22 is fully closed (N in step S9). Therefore, an opening degree command for reducing the opening degree is given to the bypass valve 22 (step S10).
  • step S11 the heat exchange amount by the gas-liquid heat exchanger 20 is adapted to the target temperature Tv, so the opening degree of the bypass valve 22 is maintained as it is.
  • the temperature of the discharged refrigerant is determined from the relationship between the enthalpy difference ⁇ h corresponding to the effect of supercooling by the gas-liquid heat exchanger 20 and the discharge enthalpy h1 corresponding to the temperature Td of the discharged refrigerant. Is controlled to change the opening degree of the bypass valve 22 based on ⁇ Gr derived so as to be within the target temperature Tv, thereby suppressing the temperature of the discharged refrigerant and promoting supercooling to improve the performance of the air conditioner Can be achieved.
  • the evaporator 12 since the high-pressure refrigerant that has bypassed the bypass path 21 is caused to flow upstream from the decompression unit 151, unlike the case where the bypassed high-pressure refrigerant is caused to flow before the compressor 14, the evaporator 12.
  • the heat exchange performance of the evaporator 12 can be maintained without reducing the amount of refrigerant circulating to the evaporator.
  • the refrigerant flowing through the gas-liquid heat exchanger 20 and the bypass path 21 are changed.
  • the ratio of the flow rate to the flowing refrigerant an appropriate response of the compressor 14 can be obtained, and the temperature of the discharged refrigerant can be stabilized at the target temperature Tv at an early stage.
  • the alternate long and short dash line in FIG. 4 shows a case where the bypass flow rate is reduced by the bypass valve 22 at a time because the temperature of the discharged refrigerant exceeds the temperature Tv allowed for the compressor. In this case, overshoot and hunting are likely to occur due to excessive response of the temperature of the discharged refrigerant.
  • the broken line shown in FIG. 4 shows the case where the bypass flow rate is gradually reduced by the bypass valve 22 when the temperature of the discharged refrigerant exceeds the temperature Tv allowed for the compressor 14. In this case, there is a possibility that the bypass flow rate is insufficient and the discharge temperature cannot be lowered to the allowable temperature Tv. According to the control of the present embodiment, as shown by the thick solid line in FIG.
  • the temperature of the discharged refrigerant appropriately follows the change in the magnitude of the effect of gas-liquid heat exchange accompanying the change in ⁇ Gr.
  • the temperature of the refrigerant is quickly stabilized at the target temperature Tv. Since the bypassed refrigerant is allowed to flow upstream of the decompression unit 151 that is away from the compressor 14, it can be avoided that the temperature of the discharged refrigerant responds sensitively, which also contributes to the stability of the discharged temperature.
  • a flow rate adjusting unit 23 that can adjust the flow rate of the refrigerant flowing into the bypass path 21 can be used.
  • the flow rate adjustment unit 23 and the control unit 25 on the right side in FIG. 5 that function during the cooling operation and the left flow rate adjustment unit 23 and the control unit 25 in FIG. 5 that function during the heating operation are switched and used.
  • the flow rate adjusting unit 23 can cause the entire amount of the high-pressure refrigerant that passes through the condenser 11 and goes to the gas-liquid heat exchanger 20 to flow into the bypass path 21 as necessary.
  • the control unit 25 calculates the enthalpy difference ⁇ h ′ by the same method as in the above embodiment, and sends a command corresponding to the current ⁇ h ′ / ⁇ h times bypass flow rate to the flow rate adjusting unit. 23, the same effect as the above embodiment can be obtained.
  • the refrigerant circuit system of the present invention can be configured as a system exclusively for cooling operation or heating operation. In that case, the four-way valve 13 is not necessary and only one decompression unit 15 is sufficient. In addition, it is sufficient to prepare a condenser temperature sensor only for one of the two heat exchangers 11 and 12 that functions as a condenser.
  • the refrigerant circuit system of the present invention can be applied not only to an air conditioner but also to an appropriate device using a refrigeration cycle such as a freezer or a water heater.

Abstract

L'invention concerne un système de circuit de fluide frigorigène avec lequel il est possible de favoriser un surfusion tout en régulant de manière adéquate la température du compresseur. Le système de circuit de fluide frigorigène (1) comprend : un échangeur de chaleur gaz-liquide (20) pour échanger de la chaleur entre un fluide frigorigène haute pression et un fluide frigorigène basse pression; un trajet de dérivation (21) pour dévier le fluide frigorigène haute pression en amont d'une unité de décompression (151); une soupape de dérivation (22) apte à régler le débit; et une unité de commande (25) pour délivrer une commande correspondant au débit de la soupape de dérivation (22). L'unité de commande (25) détermine le rapport d'augmentation/diminution d'un moment actuel du débit du fluide frigorigène haute pression à canaliser dans le trajet de dérivation (21) sur la base de Δh'/Δh, étant donné que: h1 est l'enthalpie de décharge, qui est l'enthalpie correspondant à la température détectée du fluide frigorigène évacué; Δh est la différence d'enthalpie, qui est la différence d'enthalpie correspondant à la température de fluide frigorigène détectée au niveau de l'entrée et de la sortie de l'échangeur de chaleur gaz-liquide (20); hv est l'enthalpie de décharge cible correspondant à la température cible Tv admissible pour le compresseur (14); et Δh' est la différence d'enthalpie compatible avec l'enthalpie de décharge cible hv sur la base de h1 et Δh.
PCT/JP2017/040965 2016-12-14 2017-11-14 Système de circuit de fluide frigorigène et procédé de commande d'un tel système WO2018110185A1 (fr)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111750574A (zh) * 2019-03-28 2020-10-09 东普雷股份有限公司 冷冻装置及冷冻装置的运转方法
CN114738934A (zh) * 2022-03-29 2022-07-12 青岛海尔空调电子有限公司 一种空调器故障检测方法、检测装置及空调器
WO2023040384A1 (fr) * 2021-09-18 2023-03-23 青岛海尔空调电子有限公司 Climatiseur

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110195925A (zh) * 2019-05-31 2019-09-03 宁波奥克斯电气股份有限公司 一种低温空气源热泵喷焓阀的控制方法及空调器
CN110486917B (zh) * 2019-08-23 2021-06-22 广东美的暖通设备有限公司 运行控制装置及方法、空调器和计算机可读存储介质
CN113091205B (zh) * 2020-08-19 2022-03-08 广州松下空调器有限公司 一种空调器异常检测方法及装置
WO2023100233A1 (fr) * 2021-11-30 2023-06-08 三菱電機株式会社 Dispositif de climatisation
CN115289604A (zh) * 2022-08-12 2022-11-04 珠海格力电器股份有限公司 制热过负荷保护方法和装置、空调器

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09105560A (ja) * 1995-08-04 1997-04-22 Mitsubishi Electric Corp 冷凍装置
JPH1068553A (ja) * 1996-08-27 1998-03-10 Daikin Ind Ltd 空気調和機
JP2002349977A (ja) * 2001-05-24 2002-12-04 Denso Corp ヒートポンプサイクル
JP2003214713A (ja) * 2002-01-23 2003-07-30 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
JP2008121977A (ja) * 2006-11-13 2008-05-29 Mitsubishi Electric Corp ヒートポンプ給湯機
JP2010002109A (ja) * 2008-06-19 2010-01-07 Mitsubishi Electric Corp 冷凍空調装置
JP2011043273A (ja) * 2009-08-20 2011-03-03 Panasonic Corp ヒートポンプ式加熱液体システム
JP2015152262A (ja) * 2014-02-17 2015-08-24 東芝キヤリア株式会社 冷凍サイクル装置
DE102014222849A1 (de) * 2014-11-10 2016-05-12 BSH Hausgeräte GmbH Haushaltskältegerät und Kältemaschine dafür

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003130481A (ja) * 2001-10-24 2003-05-08 Mitsubishi Heavy Ind Ltd 自動車用空調装置の蒸気圧縮式冷凍サイクル
CN105074351B (zh) * 2013-03-12 2017-03-22 三菱电机株式会社 空调装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09105560A (ja) * 1995-08-04 1997-04-22 Mitsubishi Electric Corp 冷凍装置
JPH1068553A (ja) * 1996-08-27 1998-03-10 Daikin Ind Ltd 空気調和機
JP2002349977A (ja) * 2001-05-24 2002-12-04 Denso Corp ヒートポンプサイクル
JP2003214713A (ja) * 2002-01-23 2003-07-30 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
JP2008121977A (ja) * 2006-11-13 2008-05-29 Mitsubishi Electric Corp ヒートポンプ給湯機
JP2010002109A (ja) * 2008-06-19 2010-01-07 Mitsubishi Electric Corp 冷凍空調装置
JP2011043273A (ja) * 2009-08-20 2011-03-03 Panasonic Corp ヒートポンプ式加熱液体システム
JP2015152262A (ja) * 2014-02-17 2015-08-24 東芝キヤリア株式会社 冷凍サイクル装置
DE102014222849A1 (de) * 2014-11-10 2016-05-12 BSH Hausgeräte GmbH Haushaltskältegerät und Kältemaschine dafür

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3460357A4 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111750574A (zh) * 2019-03-28 2020-10-09 东普雷股份有限公司 冷冻装置及冷冻装置的运转方法
CN111750574B (zh) * 2019-03-28 2023-09-15 东普雷股份有限公司 冷冻装置及冷冻装置的运转方法
WO2023040384A1 (fr) * 2021-09-18 2023-03-23 青岛海尔空调电子有限公司 Climatiseur
CN114738934A (zh) * 2022-03-29 2022-07-12 青岛海尔空调电子有限公司 一种空调器故障检测方法、检测装置及空调器

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