EP4332466A1 - Klimatisierungsvorrichtung - Google Patents

Klimatisierungsvorrichtung Download PDF

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Publication number
EP4332466A1
EP4332466A1 EP21939196.8A EP21939196A EP4332466A1 EP 4332466 A1 EP4332466 A1 EP 4332466A1 EP 21939196 A EP21939196 A EP 21939196A EP 4332466 A1 EP4332466 A1 EP 4332466A1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
temperature
flow path
air conditioner
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.)
Pending
Application number
EP21939196.8A
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English (en)
French (fr)
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EP4332466A4 (de
Inventor
Masanori Sato
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP4332466A1 publication Critical patent/EP4332466A1/de
Publication of EP4332466A4 publication Critical patent/EP4332466A4/de
Pending 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the 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
    • 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21162—Temperatures of a condenser of the refrigerant at the inlet of the condenser
    • 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits

Definitions

  • the present disclosure relates to an air conditioner.
  • Japanese Patent Laying-Open No. 2009-162403 discloses an air conditioner that uses HC refrigerant having a low GWP, that is, propane (R290) or isobutane, as refrigerant for a refrigerant circuit. This air conditioner uses an internal heat exchanger in order to increase efficiency.
  • the present disclosure has been made in order to solve the aforementioned problem, and an object thereof is to disclose an air conditioner capable of achieving further improved performance of a refrigeration cycle that uses an internal heat exchanger, while keeping the internal heat exchanger to have a small size.
  • the present disclosure relates to an air conditioner.
  • the air conditioner includes: a refrigerant circuit including at least a compressor, a condenser, an expansion valve, and an evaporator, the refrigerant circuit being configured to circulate refrigerant; a heat exchanger configured to exchange heat between the refrigerant that has passed through the condenser and the refrigerant that is suctioned into the compressor; a flow rate adjusting device configured to adjust an amount of heat medium supplied to the heat exchanger to cool the heat exchanger; a temperature sensor configured to detect a temperature of the heat medium; and a controller configured to control the flow rate adjusting device in accordance with an output of the temperature sensor.
  • the air conditioner according to the present disclosure can obtain an effect caused by an increase in enthalpy difference in the evaporator without reducing the density of the refrigerant suctioned into the compressor. This enables further improved performance of a refrigeration cycle that uses an internal heat exchanger.
  • Fig. 1 is a view showing a configuration of an air conditioner 1000 according to a first embodiment.
  • Air conditioner 1000 shown in Fig. 1 includes a refrigerant circuit 500, an internal heat exchanger 250, a flow rate adjusting device 420, and a controller 100.
  • Refrigerant circuit 500 includes at least a compressor 200, an outdoor heat exchanger 210, an expansion valve 230, and an indoor heat exchanger 110, and is configured to circulate refrigerant.
  • refrigerant R290 is used, for example.
  • refrigerant circuit 500 is constituted by compressor 200, outdoor heat exchanger 210, an outdoor blower 220, expansion valve 230, a four-way valve 240, indoor heat exchanger 110, and an indoor blower 120.
  • Four-way valve 240 has ports P1 to P4.
  • expansion valve 230 an electronic expansion valve (LEV: Linear Expansion Valve) can be used, for example.
  • Compressor 200 is configured to change its operating frequency, in accordance with a control signal received from controller 100.
  • compressor 200 includes therein a drive motor variable in rotational speed under inverter control and, when the operating frequency is changed, the rotational speed of the drive motor is changed. By changing the operating frequency of compressor 200, an output of compressor 200 is adjusted.
  • Compressor 200 of any of various types such as rotary type, reciprocating type, scroll type, and screw type, for example, may be employed.
  • Four-way valve 240 is controlled into one of a cooling operation state and a heating operation state, by a control signal received from controller 100.
  • the cooling operation state refers to a state in which port P1 and port P4 communicate with each other and port P2 and port P3 communicate with each other, as indicated by broken lines.
  • the heating operation state refers to a state in which port P1 and port P3 communicate with each other and port P2 and port P4 communicate with each other, as indicated by solid lines.
  • Internal heat exchanger 250 is configured to exchange heat between high-pressure and high-temperature refrigerant that has passed through a condenser (outdoor heat exchanger 210) and low-pressure and low-temperature refrigerant that is suctioned by compressor 200 during cooling.
  • internal heat exchanger 250 is also configured to perform heat exchange with external heat medium for cooling conveyed through a flow path 410.
  • water is used as the heat medium for cooling. The water may be circulated such that it passes through internal heat exchanger 250, then is cooled at a cooling tower or the like, and thereafter is supplied again through flow path 410, for example. Further, drain water from an evaporator, tap water, groundwater, or the like may flow without circulation. It is sufficient as long as the heat medium can cool the internal heat exchanger, and a flow path through which the heat medium passes may not necessarily be provided inside. For example, internal heat exchanger 250 may be cooled by spraying water from outside.
  • Flow rate adjusting device 420 adjusts the amount of the heat medium such as water supplied to internal heat exchanger 250 to cool internal heat exchanger 250.
  • a control valve having an opening degree that changes from 0 to 100% in accordance with a control signal, or the like can be used, for example.
  • Air conditioner 1000 further includes temperature sensors 260 to 263 and 411. Temperature sensor 260 is arranged on a suction pipe of compressor 200 to measure a suction temperature T260 of the refrigerant. Temperature sensor 261 is arranged on a pipe that connects outdoor heat exchanger 210 and internal heat exchanger 250 to measure a refrigerant temperature T261. Temperature sensor 262 is arranged in indoor heat exchanger 110 to measure a refrigerant temperature T262, which serves as an evaporation temperature during cooling and as a condensation temperature during heating. Temperature sensor 263 is arranged on a pipe that connects indoor heat exchanger 110 and port P3 of four-way valve 240 to measure a refrigerant temperature T263.
  • Temperature sensor 411 detects a temperature T411 of the heat medium such as water. If the water temperature is lower than the temperature of the high-pressure refrigerant at an inlet of internal heat exchanger 250 obtained by temperature sensor 261, the water can cool internal heat exchanger 250, and thus the temperature of the high-pressure refrigerant at an outlet of internal heat exchanger 250 can be reduced.
  • Controller 100 is configured to control flow rate adjusting device 420 in accordance with an output of temperature sensor 411. Further, controller 100 controls the opening degree of expansion valve 230 to adjust an SH (superheat) of the refrigerant at an outlet portion of the evaporator.
  • SH superheat
  • Controller 100 has a configuration including a CPU (Central Processing Unit) 101, a memory 102 (ROM (Read Only Memory) and a RAM (Random Access Memory)), input/output buffers (not shown), and the like.
  • CPU 101 expands programs stored in the ROM onto the RAM or the like and executes the programs.
  • the programs stored in the ROM are programs describing processing procedures of controller 100.
  • controller 100 performs control of devices in air conditioner 1000. This control can be processed not only by software but also by dedicated hardware (electronic circuitry).
  • Fig. 2 is a view showing a configuration of an air conditioner 2000 in a study example.
  • Air conditioner 1000 in Fig. 1 includes internal heat exchanger 250 that can be cooled with water, whereas air conditioner 2000 includes an ordinary internal heat exchanger 550 instead.
  • Internal heat exchanger 550 shown in Fig. 2 is configured to exchange heat between high-temperature and high-pressure refrigerant that has flowed out of an outlet of outdoor heat exchanger 210 and low-temperature and low-pressure refrigerant that is suctioned into compressor 200 during cooling.
  • Fig. 3 is a PH diagram of a refrigeration cycle that uses R290 refrigerant and has no internal heat exchanger, in the configuration in the study example.
  • Fig. 4 is a PH diagram of a refrigeration cycle that uses the R290 refrigerant and has an internal heat exchanger, in the configuration in the study example.
  • Fig. 5 is a PH diagram of a refrigeration cycle that uses the R290 refrigerant and has an internal heat exchanger, in the configuration in the first embodiment.
  • the increased amount of evaporator enthalpy difference ⁇ he acts more greatly than the decreased amount of suction density ⁇ s as described above, and thus it is possible to improve the COP of the air conditioning equipment by using an internal heat exchanger.
  • the PH diagram of the refrigerant circuit in the present embodiment is calculated under the same conditions as those in Fig. 4 (an evaporation temperature of 17°C, a condensation temperature of 40°C, an evaporator superheat of 5 deg, a supercool of 5 deg, and a compressor efficiency of 1), the PH diagram as shown in Fig. 5 is obtained. It should be noted that the calculation was made assuming that the temperature of the water as an external cooling source was 22°C.
  • the enthalpy at the high-pressure side refrigerant outlet of internal heat exchanger 250 becomes smaller than that in the case of using ordinary internal heat exchanger 550, and the evaporator enthalpy difference increases to h(D3)-h(A3).
  • the reason for the increase is that the temperature of the refrigerant at the high-pressure outlet of ordinary internal heat exchanger 550 is 28.2°C, whereas in the present embodiment, the temperature of the external cooling source is 22°C, and thus the temperature of the refrigerant at the high-pressure outlet of internal heat exchanger 250 decreases to that temperature (22°C).
  • Fig. 6 is a perspective view showing an external appearance of internal heat exchanger 250.
  • Fig. 7 is a cross sectional view of internal heat exchanger 250 in a cross section F in Fig. 6 .
  • Internal heat exchanger 250 shown in Figs. 6 and 7 has a triple-tube structure including an inner tube 251, a middle tube 252, and an outer tube 253.
  • Inner tube 251 serves as a flow path R1 through which the low-pressure refrigerant returning to a suction portion of compressor 200 flows.
  • Middle tube 252 serves as a flow path R2 through which the high-pressure refrigerant that has flowed out of the outlet of outdoor heat exchanger 210 flows.
  • Outer tube 253 serves as a flow path R3 through which the water externally conveyed through flow path 410 flows.
  • the refrigerant that flows through flow path R1 and the refrigerant that flows through flow path R2 have a relation of counterflows
  • the refrigerant that flows through flow path R2 and the water that flows through flow path R3 also have a relation of counterflows.
  • a crack appears in the outer circumference of outer tube 253, it is the water that may leak to the outside of internal heat exchanger 250, which is less problematic than the case where the refrigerant flows through outer tube 253.
  • the refrigerant can be prevented from being discharged to the outside.
  • a chlorofluorocarbon-based refrigerant is used, the refrigerant is less likely to leak to the outside, which can suppress influence on global warming.
  • internal heat exchanger 250 includes flow path 410, the cooling medium that flows through flow path 410 is water, and internal heat exchanger 250 is of a triple-tube type. It should be noted that the cooling medium may not be water. Further, internal heat exchanger 250 may not be of a triple-tube type, and it is not necessary to form therein a flow path through which the cooling medium such as water flows. For example, internal heat exchanger 250 may be of a double-tube type, and internal heat exchanger 250 may be cooled by spraying water from above. Furthermore, although internal heat exchanger 250 is installed to act during cooling, no problem occurs when it is installed to act during heating.
  • controller 100 changes the frequency of compressor 200 such that a room temperature reaches a target (setting) temperature. Further, controller 100 controls flow rate adjusting device 420 during cooling, as described below.
  • Fig. 8 is a flowchart for illustrating control of flow rate adjusting device 420 during cooling.
  • controller 100 obtains refrigerant temperature T261 at the outlet of outdoor heat exchanger 210 from temperature sensor 261, and obtains temperature T411 of the water from temperature sensor 411.
  • controller 100 determines whether or not temperature T261 obtained from temperature sensor 261 is higher than temperature T411 obtained from temperature sensor 411.
  • controller 100 controls flow rate adjusting device 420 to be fully closed, to prevent the water from flowing to internal heat exchanger 250.
  • controller 100 controls flow rate adjusting device 420 to be fully opened.
  • controller 100 determines whether a superheat of the suctioned refrigerant (hereinafter referred to as a suction SH) is smaller than a determination value ⁇ (> 0).
  • the suction SH is calculated by subtracting the evaporation temperature obtained by temperature sensor 262 from the suction temperature obtained by temperature sensor 260.
  • determination value ⁇ is set to a value at which it is possible to determine that the refrigerant suctioned into compressor 200 is sufficiently gasified, for example, 5K.
  • step S16 controller 100 closes flow rate adjusting device 420 by a certain opening degree. By decreasing the flow rate of the water in this manner to reduce the amount of heat exchange, the value of the suction SH can be increased. Thereafter, the processing in step S15 is performed again.
  • the flow rate of the water to internal heat exchanger 250 is adjusted using flow rate adjusting device 420 in the present embodiment, the flow rate of the water may be controlled using a pump.
  • FIG. 9 is a flowchart for illustrating control of expansion valve 230 during cooling.
  • controller 100 determines whether or not a superheat of the refrigerant at the outlet portion of the evaporator (hereinafter referred to as an evaporator outlet SH) is smaller than a determination value ⁇ ( ⁇ 0).
  • the evaporator outlet SH is calculated by subtracting evaporation temperature T262 obtained by temperature sensor 262 from evaporator outlet temperature T263 obtained by temperature sensor 263.
  • determination value ⁇ is set to a value smaller than determination value ⁇ . For example, when determination value ⁇ is 5K, determination value ⁇ is set to 2K.
  • determination value ⁇ is set to be smaller than determination value ⁇ .
  • step S22 controller 100 opens the opening degree of expansion valve 230 by a certain value. Thereby, the value of the evaporator outlet SH can be decreased. Thereafter, the processing in step S21 is performed again.
  • controller 100 determines whether flow rate adjusting device 420 is fully closed.
  • step S24 controller 100 closes the opening degree of expansion valve 230 by a certain value to increase the value of the suction SH, and thereafter performs determination processing in step S25.
  • step S25 controller 100 determines whether or not the suction SH is smaller than determination value ⁇ (> 0).
  • the suction SH ⁇ ⁇ is satisfied (NO in S25)
  • the suction SH ⁇ ⁇ is satisfied (YES in S25)
  • controller 100 closes the opening degree of expansion valve 230 by a certain value. By controlling the opening degree of expansion valve 230 in this manner, the value of the suction SH can be increased. Thereafter, the processing in step S25 is performed again.
  • flow rate adjusting device 420 may be fully closed and controlled as in an ordinary air conditioner, or flow rate adjusting device 420 may be controlled as described below.
  • Fig. 10 is a view showing a configuration of an air conditioner 1001 having sensors used during heating added thereto.
  • Fig. 11 is a flowchart for illustrating control of flow rate adjusting device 420 during heating.
  • controller 100 obtains a refrigerant temperature T264 at an inlet of internal heat exchanger 250 from a temperature sensor 264, and obtains temperature T411 of the water from temperature sensor 411.
  • controller 100 determines whether or not temperature T264 obtained from temperature sensor 264 is higher than temperature T411 obtained from temperature sensor 411.
  • step S33 controller 100 controls flow rate adjusting device 420 to be fully closed, to prevent the water from flowing to internal heat exchanger 250.
  • step S34 controller 100 controls flow rate adjusting device 420 to be fully opened.
  • step S35 controller 100 determines whether the superheat of the suctioned refrigerant (suction SH) is smaller than determination value ⁇ (> 0).
  • the suction SH is calculated by subtracting an evaporation temperature obtained by a temperature sensor 265 from the suction temperature obtained by temperature sensor 260.
  • determination value ⁇ is set to a value at which it is possible to determine that the refrigerant suctioned into compressor 200 is sufficiently gasified, for example, 5K.
  • step S35 controller 100 closes flow rate adjusting device 420 by a certain opening degree. By decreasing the flow rate of the water in this manner to reduce the amount of heat exchange, the value of the suction SH can be increased. Thereafter, the processing in step S35 is performed again.
  • the flow rate of the water may be controlled using a pump instead of flow rate adjusting device 420.
  • the evaporator outlet SH is calculated by subtracting the value of temperature sensor 265 from the value of a temperature sensor 266.
  • the coefficient of performance, COP, of the air conditioner that uses R290 as the refrigerant and uses an internal heat exchanger can be improved. Further, while using R290 as the refrigerant is most effective, even when R32 or R410 is used as the refrigerant, the effect caused by an internal heat exchanger can be obtained and COP can be improved, because the suction density changes from that in the case shown in Fig. 2 .
  • an air heat exchanger is employed as outdoor heat exchanger 210, considering the case that the cooling source for the refrigeration cycle is not in a situation where it can always be used. For example, when tap water is employed, there may be a case where it cannot be used due to suspension of water supply or the like. Therefore, in order to cause the refrigeration cycle to always function, it is appropriate to employ outdoor air, which can always be utilized, as a target of heat exchange of outdoor heat exchanger 210. Further, when a water-refrigerant heat exchanger is employed as outdoor heat exchanger 210, it is also necessary to draw a water pipe. Accordingly, the configuration as in Fig. 1 is employed to achieve a simple configuration.
  • Fig. 12 is a view showing a configuration of an air conditioner 1002 according to a second embodiment.
  • outdoor heat exchanger 210 in Fig. 1 is changed to a heat exchanger 270.
  • heat exchanger 270 is configured to exchange heat with the water as the external cooling source. The water is circulated and cooled at a cooling tower or the like, and then is supplied again through a water supply pipe.
  • Heat exchanger 270 is a plate heat exchanger, for example. Further, the water used by heat exchanger 270 and internal heat exchanger 250 is supplied through the same water supply pipe.
  • air conditioner 1002 in the second embodiment the same effect as that in the first embodiment is obtained.
  • the amount of heat exchange by the water increases when compared with the configuration shown in the first embodiment, the returned water has a higher temperature and can be used for hot-water supply or the like.
  • plate heat exchanger 270 is employed as the outdoor heat exchanger and thereby heat exchange performance is improved, the heat exchanger can be downsized when compared with the first embodiment.
  • internal heat exchanger 250 may be used for an air conditioner for cooling only that does not include a four-way valve.
  • the first and second embodiments have provided the description based on an example where the R290 refrigerant is used as refrigerant circulating through the refrigerant circuit
  • another refrigerant such as R32 or R410 may be used.
  • R32 refrigerant since influence of the increase in enthalpy difference in the evaporator and influence of the decrease in the density of the suctioned refrigerant offset each other in internal heat exchanger 550 shown in the study example in Fig. 2 , there is no merit in introducing the R32 refrigerant.
  • internal heat exchanger 250 shown in Fig. 1 can suppress the decrease in the density of the suctioned refrigerant using the external cooling source, the performance of the air conditioner can be improved even in the case of using the R32 refrigerant.
  • Air conditioner 1000 shown in Fig. 1 includes: refrigerant circuit 500 including at least compressor 200, a condenser (outdoor heat exchanger 210), expansion valve 230, and an evaporator (indoor heat exchanger 110), the refrigerant circuit being configured to circulate refrigerant; internal heat exchanger 250 configured to exchange heat between the refrigerant that has passed through the condenser (outdoor heat exchanger 210) and the refrigerant that is suctioned into compressor 200; flow rate adjusting device 420 configured to adjust an amount of heat medium supplied to the internal heat exchanger to cool internal heat exchanger 250; temperature sensor 411 configured to detect a temperature of the heat medium; and controller 100 configured to control flow rate adjusting device 420 in accordance with an output of temperature sensor 411.
  • controller 100 is configured to control flow rate adjusting device 420 such that the heat medium is supplied to internal heat exchanger 250 when temperature T411 of the heat medium is lower than temperature T261 of the refrigerant that has passed through the condenser (outdoor heat exchanger 210).
  • controller 100 is configured to control flow rate adjusting device 420 such that the heat medium is supplied to internal heat exchanger 250 when temperature T411 of the heat medium is lower than temperature T260 of the refrigerant that is suctioned into compressor 200.
  • controller 100 is configured to control flow rate adjusting device 420 such that the heat medium is not supplied to internal heat exchanger 250 when temperature T411 of the heat medium is higher than temperature T261 of the refrigerant that has passed through the condenser (outdoor heat exchanger 210).
  • internal heat exchanger 250 includes first flow path R1 through which the refrigerant that is suctioned into compressor 200 passes, second flow path R2 through which the refrigerant that has passed through the condenser (outdoor heat exchanger 210) passes, and third flow path R3 through which the heat medium passes.
  • the refrigerant that passes through first flow path R1 and the refrigerant that passes through second flow path R2 have a relation of counterflows
  • the refrigerant that passes through second flow path R2 and the heat medium that passes through third flow path R3 have a relation of counterflows.
  • internal heat exchanger 250 includes first flow path R1 through which the refrigerant that is suctioned into compressor 200 passes, second flow path R2 through which the refrigerant that has passed through the condenser (outdoor heat exchanger 210) passes, and third flow path R3 through which the heat medium passes.
  • Second flow path R2 and third flow path R3 are arranged adjacently to exchange heat.
  • internal heat exchanger 250 is a triple-tube heat exchanger having inner tube 251, middle tube 252, and outer tube 253 arranged in order from inside toward outside.
  • Inner tube 251 is first flow path R1.
  • Second flow path R2 is formed between middle tube 252 and inner tube 251.
  • Third flow path R3 is formed between middle tube 252 and outer tube 253.
  • the condenser (heat exchanger 270) is configured such that the heat medium and the refrigerant exchange heat.
  • the refrigerant is propane.
  • 100 controller; 101: CPU; 102: memory; 110, 210, 250, 270, 550: heat exchanger; 120: indoor blower; 200: compressor; 220: outdoor blower; 230: expansion valve; 240: four-way valve; 251: inner tube; 252: middle tube; 253: outer tube; 260 to 266, 411: temperature sensor; 410, R1, R2, R3: flow path; 420: flow rate adjusting device; 500: refrigerant circuit; 1000, 1001, 1002, 2000: air conditioner; P1, P2, P3, P4: port.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
EP21939196.8A 2021-04-27 2021-04-27 Klimatisierungsvorrichtung Pending EP4332466A4 (de)

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PCT/JP2021/016709 WO2022230034A1 (ja) 2021-04-27 2021-04-27 空気調和装置

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US5797277A (en) * 1997-11-06 1998-08-25 Chrysler Corporation Condensate cooler for increasing refrigerant density
JP2003262397A (ja) * 2002-03-08 2003-09-19 Osaka Gas Co Ltd 給湯装置
KR100652888B1 (ko) * 2004-04-26 2006-12-06 금종관 삼중관구조의 응축기를 구비한 에어컨
JP2009162403A (ja) 2007-12-28 2009-07-23 Toshiba Carrier Corp 空気調和機
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WO2015056333A1 (ja) * 2013-10-17 2015-04-23 三菱電機株式会社 冷凍サイクル装置
JP2015081726A (ja) * 2013-10-23 2015-04-27 日立アプライアンス株式会社 冷凍サイクル装置、及び、空気調和装置
JP6238835B2 (ja) * 2014-05-21 2017-11-29 三菱電機株式会社 圧縮機、及びその圧縮機を備えたヒートポンプ装置
JP6509368B2 (ja) * 2015-11-18 2019-05-08 三菱電機株式会社 ヒートポンプ給湯装置
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JP7099201B2 (ja) * 2018-09-05 2022-07-12 富士電機株式会社 ヒートポンプ装置

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