WO2018055740A9 - Échangeur de chaleur et dispositif à cycle de réfrigération - Google Patents

Échangeur de chaleur et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2018055740A9
WO2018055740A9 PCT/JP2016/078057 JP2016078057W WO2018055740A9 WO 2018055740 A9 WO2018055740 A9 WO 2018055740A9 JP 2016078057 W JP2016078057 W JP 2016078057W WO 2018055740 A9 WO2018055740 A9 WO 2018055740A9
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WIPO (PCT)
Prior art keywords
valve
heat exchanger
refrigerant
outdoor unit
unit heat
Prior art date
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PCT/JP2016/078057
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English (en)
Japanese (ja)
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WO2018055740A1 (fr
Inventor
孔明 仲島
航祐 田中
早丸　靖英
昭憲 坂部
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP16916807.7A priority Critical patent/EP3517855B1/fr
Priority to JP2018540571A priority patent/JP6671491B2/ja
Priority to PCT/JP2016/078057 priority patent/WO2018055740A1/fr
Publication of WO2018055740A1 publication Critical patent/WO2018055740A1/fr
Publication of WO2018055740A9 publication Critical patent/WO2018055740A9/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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • 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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F25B2313/02533—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements during heating
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
    • F25B2313/02541—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements during cooling

Definitions

  • the present invention relates to a heat exchanger and a refrigeration cycle apparatus.
  • a cold air conditioning device as an example of the refrigeration cycle apparatus.
  • a common cold air conditioning system includes a compressor, a four-way valve, a condenser, an expansion valve, and an evaporator. These components are communicated via connection piping to constitute a refrigeration cycle.
  • the flow of the refrigerant is reversed by switching of the four-way valve, and the heating operation and the cooling operation are switched.
  • the indoor unit heat exchanger is used as a condenser
  • the outdoor unit heat exchanger is used as an evaporator.
  • the indoor unit heat exchanger is used as an evaporator
  • the outdoor unit heat exchanger is used as a condenser.
  • the heat exchangers of the outdoor unit and the indoor unit are used differently in the cooling operation and the heating operation. That is, the heat exchangers of the outdoor unit and the indoor unit are used as a condenser or an evaporator, respectively.
  • the state of the refrigerant passing through the inside of the heat exchanger is different between the condenser and the evaporator.
  • the refrigerant flows in the form of a superheated gas at the heat exchanger inlet, and becomes a gas-liquid two-phase state along with heat exchange, and becomes a supercooling liquid at the heat exchanger outlet.
  • the refrigerant in a liquid phase or a gas-liquid two-phase state at the heat exchanger inlet, is gasified along with heat exchange, and is in a saturated gas state at the heat exchanger outlet.
  • the flow velocity of the refrigerant flowing through the inside of the heat transfer tube of the heat exchanger differs depending on whether the state of the refrigerant is a liquid state or a gas state.
  • the performance of the heat exchanger changes with the flow velocity of the refrigerant.
  • Patent Document 1 An air conditioner for solving this problem is described in JP-A-2015-117936 (Patent Document 1).
  • two unit flow paths are connected in series during the cooling operation, and two unit flow paths are connected in parallel during the heating operation. Further, in the outdoor unit heat exchanger, two unit flow paths are switched in series or in parallel by three valves.
  • the number of two unit flow paths is equal. That is, the heat exchanger is equally divided into two unit flow paths. Therefore, the number of refrigerant channels (number of passes) in the portion where the liquid phase of the refrigerant increases is increased, and the flow velocity of the refrigerant is reduced. Therefore, when this air conditioner is used as, for example, a condenser, the heat transfer performance in the downstream unit flow path, in which the liquid phase of the refrigerant increases, of the two unit flow paths is reduced. For this reason, there is a problem that the performance of the heat exchanger is lowered.
  • the outdoor unit heat exchanger has three valves in order to switch two unit flow paths in series or in parallel. For this reason, there is a problem that miniaturization of a heat exchanger is difficult.
  • This invention is made in view of the said subject,
  • the objective is to provide the refrigerating cycle apparatus provided with the heat exchanger which can improve performance, and can be miniaturized, and its heat exchanger.
  • the heat exchanger of the present invention includes a first heat exchange unit, a second heat exchange unit, and a switching valve.
  • the first heat exchange unit includes a plurality of first refrigerant channels, a first connection port communicating with the first refrigerant channel, and a second connection port communicating with the first refrigerant channel on the opposite side to the first connection port.
  • the second heat exchange unit includes at least one second refrigerant flow path, a third connection port communicating with the second refrigerant flow path, and a fourth connection communicating with the second refrigerant flow path opposite to the third connection port. Have a mouth.
  • the switching valve has a first inlet / outlet port, a second inlet / outlet port, a third inlet / outlet port, a fourth inlet / outlet port, a first in-valve channel, a second in-valve channel, and a third in-valve channel.
  • the first port is connected to the first connection port.
  • the second port is connected to the third connection port.
  • the third port is connected to the second connection port.
  • the fourth port is connected to the fourth connection port.
  • the first in-valve flow path communicates the first inlet / outlet with the second inlet / outlet.
  • the second in-valve flow path communicates the second port with the third port.
  • the third in-valve flow passage communicates the third port with the fourth port.
  • the number of the plurality of first refrigerant flow paths of the first heat exchange unit is larger than the number of the at least one second refrigerant flow path of the second heat exchange unit.
  • the switching valve is configured such that the first valve internal flow path and the third valve internal flow path are closed and the second valve internal flow path is opened, or the first valve internal flow path and the third valve internal flow path are opened It is comprised so that it may switch whether the flow path in 2 valve is closed.
  • the number of the plurality of first refrigerant flow paths of the first heat exchange unit is larger than the number of the at least one second refrigerant flow path of the second heat exchange unit. For this reason, if the second heat exchange unit is operated to be a location where the liquid phase of the refrigerant increases, the flow rate of the refrigerant can be increased by reducing the number of refrigerant channels in the location where the liquid phase of the refrigerant increases. it can. Therefore, since the heat transfer performance in the location where the liquid phase of the refrigerant increases can be improved, the performance of the heat exchanger can be improved.
  • the first in-valve passage and the third in-valve passage are closed and the second in-valve passage is opened, or the first in-valve passage and the third in-valve passage are opened. It is configured to switch whether the second in-valve channel is closed. Therefore, the first heat exchange unit and the second heat exchange unit can be switched in series or in parallel by one switching valve. Therefore, the heat exchanger can be miniaturized.
  • an air conditioner will be described as an example of a refrigeration cycle apparatus.
  • the refrigeration cycle apparatus is not limited to the air conditioner, and may be a refrigeration apparatus, a chiller, or the like.
  • FIG. 1 is a structural diagram of a refrigeration cycle during cooling operation of the air conditioner according to Embodiment 1 of the present invention.
  • FIG. 2 is a structural diagram of a refrigeration cycle during heating operation of the air conditioner according to Embodiment 1 of the present invention.
  • the air conditioner (refrigerating cycle device) includes the compressor 1, the four-way valve 2, and the outdoor unit heat exchanger 3 (a first outdoor unit heat exchanger 3a, a second outdoor unit heat exchanger 3b, A switching valve 4), an expansion valve 5 (first expansion valve 5a, second expansion valve 5b), and an indoor unit heat exchanger 6 are provided.
  • the refrigeration cycle (refrigerant circuit) is configured.
  • the refrigerant flows in the refrigeration cycle. That is, the refrigerant includes the compressor 1, the four-way valve 2, the first outdoor unit heat exchanger (first heat exchange unit) 3a, the second outdoor unit heat exchanger (second heat exchange unit) 3b, the switching valve 4, and the first It flows through the 1 expansion valve 5a, the 2nd expansion valve 5b and the indoor unit heat exchanger 6.
  • a refrigerant flowing through the refrigerant cycle it is possible to use either a single refrigerant or an azeotropic refrigerant.
  • R32 can be used as a single refrigerant.
  • R410a can be used as the azeotropic refrigerant.
  • a non-azeotropic refrigerant can be used as the non-azeotropic refrigerant.
  • the air conditioner also includes a controller (not shown).
  • the control device (controller) is configured to perform calculations, instructions and the like to control each means, equipment and the like of the refrigeration cycle apparatus.
  • the controller (controller) is configured to control the operation of the four-way valve 2 and the switching valve 4, for example.
  • the compressor 1, the four-way valve 2, the outdoor unit heat exchanger 3 (the first outdoor unit heat exchanger 3a, the second outdoor unit heat exchanger 3b, the switching valve 4) and the expansion valve 5 (the first The first expansion valve 5a and the second expansion valve 5b) are provided in an outdoor unit (not shown).
  • the indoor unit heat exchanger 6 is provided in an indoor unit (not shown).
  • the compressor 1 is configured to compress and discharge the sucked refrigerant.
  • the compressor 1 may be a constant speed compressor having a constant compression capacity, or may be an inverter compressor having a variable compression capacity.
  • the inverter compressor is configured to be capable of variably controlling the rotation speed. Specifically, the rotational frequency of this inverter compressor is adjusted by changing the drive frequency based on an instruction from a controller (not shown). This changes the compression capacity.
  • This compression capacity is an amount for sending out the refrigerant per unit time.
  • the four-way valve 2 is connected to the compressor 1, the outdoor unit heat exchanger 3, and the indoor unit heat exchanger 6.
  • the four-way valve 2 is configured to switch the flow of refrigerant to the outdoor unit heat exchanger 3 and the indoor unit heat exchanger 6 according to the cooling operation and the heating operation.
  • the outdoor unit heat exchanger 3 is connected to the four-way valve 2 and the expansion valve 5.
  • the outdoor unit heat exchanger 3 is a condenser that condenses the refrigerant compressed by the compressor 1 during the cooling operation.
  • the outdoor unit heat exchanger 3 is an evaporator that evaporates the refrigerant decompressed by the expansion valve 5 (throttle device) during the heating operation.
  • the outdoor unit heat exchanger (heat exchanger) 3 includes a first outdoor unit heat exchanger (first heat exchange unit) 3a, a second outdoor unit heat exchanger (second heat exchange unit) 3b, and a switching valve 4 And.
  • the first outdoor unit heat exchanger 3 a is connected to the four-way valve 2 and the switching valve 4.
  • the second outdoor unit heat exchanger 3b is connected to the switching valve 4 and the first expansion valve 5a.
  • the outdoor unit heat exchanger 3 is for exchanging heat between the refrigerant and the air. It is comprised by the outdoor unit heat exchanger 3, for example, a pipe (heat transfer pipe) and a fin.
  • the switching valve 4 is connected to the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b.
  • the switching valve 4 is configured to switch the flow path of the refrigerant flowing through the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b.
  • the expansion valve 5 is connected to the outdoor unit heat exchanger 3 and the indoor unit heat exchanger 6.
  • the expansion valve 5 is a throttling device that decompresses the refrigerant condensed by the outdoor unit heat exchanger (condenser) 3 during the cooling operation.
  • the expansion valve 5 is a throttling device that decompresses the refrigerant condensed by the indoor unit heat exchanger (condenser) 6 during the heating operation.
  • the expansion valve 5 has a first expansion valve 5a and a second expansion valve 5b.
  • the first expansion valve 5 a is connected to the second outdoor unit heat exchanger 3 b and the indoor unit heat exchanger 6.
  • the first expansion valve 5a is configured to expand (depressurize) the refrigerant by adjusting the valve opening degree.
  • the first expansion valve 5a is, for example, an electronic expansion valve.
  • the second expansion valve 5 b is connected between the first expansion valve 5 a and the indoor unit heat exchanger 6 and the four-way valve 2.
  • the second expansion valve 5 b is configured to expand (depressurize) the refrigerant by adjusting the valve opening degree.
  • the second expansion valve 5b is configured to close the refrigerant circuit by closing the valve.
  • the second expansion valve 5b is, for example, an electronic expansion valve.
  • two expansion valves a first expansion valve 5a and a second expansion valve 5b, are provided.
  • the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b are used as an evaporator
  • the first outdoor unit heat exchanger is used to equalize the refrigerant circulation amount flowing in per pass number.
  • the refrigerant circulation amount flowing to the heat exchanger 3b and the second outdoor unit heat exchanger 3b can be adjusted.
  • the expansion valve connected to the second outdoor unit heat exchanger 3b is set to be throttled compared to the expansion valve connected to the first outdoor unit heat exchanger 3a. Become.
  • the indoor unit heat exchanger 6 is connected to the first expansion valve 5 a and the four-way valve 2.
  • the indoor unit heat exchanger 6 is an evaporator that evaporates the refrigerant decompressed by the expansion device during the cooling operation.
  • the indoor unit heat exchanger 6 also serves as a condenser that condenses the refrigerant compressed by the compressor 1 during heating operation.
  • the indoor unit heat exchanger 6 is for heat exchange between the refrigerant and air.
  • the indoor unit heat exchanger 6 is composed of, for example, a pipe (heat transfer pipe) and a fin.
  • the number of refrigerant flow paths (number of passes) of both the outdoor unit heat exchanger 3 and the indoor unit heat exchanger 6 may be variable. That is, the heat exchanger of the present embodiment may be at least one of a condenser and an evaporator.
  • FIG. 3 is a structural diagram of the outdoor unit heat exchanger 3 according to Embodiment 1 of the present invention during cooling operation.
  • FIG. 4 is a structural diagram of the outdoor unit heat exchanger 3 according to Embodiment 1 of the present invention during heating operation.
  • the first outdoor unit heat exchanger (first heat exchange unit) 3a includes a plurality of first refrigerant channels RF1, a first connection port C1, and a second connection port C2.
  • the first connection port C1 is a refrigerant inlet
  • the second connection port C2 is a refrigerant outlet.
  • the first connection port C1 is a refrigerant outlet
  • the second connection port C2 is a refrigerant inlet.
  • the first connection port C1 communicates with the first refrigerant channel RF1.
  • the second connection port C2 communicates with the first refrigerant channel RF1 on the opposite side to the first connection port C1.
  • the plurality of first refrigerant channels RF1 can communicate with the first connection port C1 and the second connection port C2 via a header (not shown).
  • the second outdoor unit heat exchanger (second heat exchange unit) 3b includes at least one second refrigerant flow path RF2, a third connection port C3, and a fourth connection port C4.
  • the third connection port C3 is a refrigerant inlet
  • the fourth connection port C4 is a refrigerant outlet.
  • the third connection port C3 communicates with the second refrigerant channel RF2.
  • the fourth connection port C4 communicates with the second refrigerant channel RF2 on the opposite side of the third connection port C3.
  • the at least one second coolant channel RF2 can communicate with the third connection port C3 and the fourth connection port C4 via a header (not shown).
  • the number of the plurality of first refrigerant channels RF1 of the first outdoor unit heat exchanger (first heat exchange unit) 3a is at least one second refrigerant of the second outdoor unit heat exchanger (second heat exchange unit) 3b More than the number of channels RF2.
  • the number (the number of paths) of the plurality of first refrigerant channels RF1 is four, for example.
  • the number (the number of paths) of at least one second coolant channel RF2 is, for example, two.
  • the number of passes means the number of divisions of the refrigerant flow path of each of the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b.
  • the switching valve 4 includes a first port P1, a second port P2, a third port P3, a fourth port P4, a first valve flow path VF1, a second valve flow path VF2, and a third valve Inner flow path VF3, main body 10, shaft 11, first valve seat 12a, second valve seat 12b, third valve seat 12c, first valve body 13a, second valve body 13b, The third valve body 13 c and the drive unit 14 are provided.
  • the main body 10 of the switching valve 4 is provided with a total of four inlets and outlets through which the refrigerant flows.
  • the first inlet / outlet P1 of the switching valve 4 is connected to the first connection port C1 of the first outdoor unit heat exchanger 3a.
  • the second inlet / outlet P2 of the switching valve 4 is connected to the third connection port C3 of the second outdoor unit heat exchanger 3b.
  • the third inlet / outlet P3 of the switching valve 4 is connected to the second connection port C2 of the first outdoor unit heat exchanger 3a.
  • the fourth inlet / outlet P4 of the switching valve 4 is connected to the fourth connection port C4 of the second outdoor unit heat exchanger 3b.
  • the first inlet / outlet port P1 is connected to the refrigerant inlet side of the first outdoor unit heat exchanger 3a during the cooling operation.
  • the second inlet / outlet port P2 is connected to the refrigerant inlet side of the second outdoor unit heat exchanger 3b during the cooling operation.
  • the third inlet / outlet port P3 is connected to the refrigerant outlet side of the first outdoor unit heat exchanger 3a during the cooling operation.
  • the fourth inlet / outlet port P4 is connected to the refrigerant outlet side of the second outdoor unit heat exchanger 3b during the cooling operation.
  • the first inlet / outlet port P1 is connected to the refrigerant outlet side of the first outdoor unit heat exchanger 3a during the heating operation.
  • the second inlet / outlet port P2 is connected to the refrigerant outlet side during heating operation of the second outdoor unit heat exchanger 3b.
  • the third inlet / outlet port P3 is connected to the refrigerant inlet side during heating operation of the first outdoor unit heat exchanger 3a.
  • the fourth port P4 is connected to the refrigerant inlet side of the second outdoor unit heat exchanger 3b during the cooling operation.
  • the main body 10 of the switching valve 4 has a cylindrical shape, and a first in-valve flow path VF1, a second in-valve flow path VF2, and a third in-valve flow path VF3 are provided in the main body 10 of the switching valve 4 There is.
  • the first in-valve flow passage VF1 communicates the first inlet / outlet port P1 with the second inlet / outlet port P2.
  • the first valve seat 12a is disposed in the first in-valve flow passage VF1.
  • the first valve seat 12a is disposed between the first port P1 and the second port P2.
  • the first valve body 13a is configured to close the first in-valve flow path VF1 by contacting the first valve seat 12a and open the first in-valve flow path VF1 by separating from the first valve seat 12a. .
  • the second in-valve flow passage VF2 brings the second inlet / outlet P2 into communication with the third inlet / outlet P3.
  • the second valve seat 12b is disposed in the second in-valve flow passage VF2.
  • the second valve seat 12b is disposed between the second port P2 and the third port P3.
  • the second valve body 13b is configured to close the second valve inner flow passage VF2 by contacting the second valve seat 12b and open the second valve inner flow passage VF2 by being separated from the second valve seat 12b. .
  • the third in-valve flow passage VF3 connects the third inlet / outlet P3 and the fourth inlet / outlet P4.
  • the third valve seat 12c is disposed in the third in-valve flow passage VF3.
  • the third valve seat 12c is disposed between the third port P3 and the fourth port P4.
  • the third valve body 13c is configured to close the third valve inner flow path VF3 by contacting the third valve seat 12c and open the third valve inner flow path VF3 by separating from the third valve seat 12c. .
  • the first valve body 13 a, the second valve body 13 b and the third valve body 13 c are attached to the shaft portion 11.
  • the first valve body 13a, the second valve body 13b and the third valve body 13c each have a flat plate shape.
  • the axial part 11 may penetrate to the center of each flat plate shape, and the 1st valve body 13a, the 2nd valve body 13b, and the 3rd valve body 13c may be attached to the axial part 11.
  • the first valve body 13 a, the second valve body 13 b, and the third valve body 13 c are disposed apart from each other in the axial direction of the shaft portion 11.
  • the switching valve 4 is comprised by 1 axis
  • the heating operation in order to frost the outdoor unit heat exchanger 3, it is necessary to perform the defrost operation.
  • the four-way valve 2 is switched from the refrigerant circuit in the heating operation to the refrigerant circuit in the cooling operation to perform defrosting.
  • flow path switching can be performed immediately.
  • the drive unit 14 is configured to drive the shaft unit 11 in the axial direction.
  • the drive unit 14 includes a movable unit 14 a and a coil 14 b.
  • the movable portion 14 a is attached to the shaft portion 11.
  • the coil 14 b is disposed to surround the movable portion 14 a.
  • the movable portion 14a is configured to be movable in the axial direction of the shaft portion 11 by the magnetic flux generated when the coil 14b is energized on the basis of an instruction from a control device (controller) (not shown). Therefore, the first valve body 13a, the second valve body 13b, and the third valve body 13c are movable in the axial direction of the shaft portion 11 as the movable portion 14a moves.
  • the drive part 14 may be one.
  • the switching valve 4 can be configured by one each of the movable part 14 a and the coil 14 b of the drive part 14. For this reason, cost can be held down.
  • the first in-valve passage VF1 and the third in-valve passage VF3 are closed and the second in-valve passage VF2 is opened, or the first in-valve passage VF1 and the third in-valve passage It is configured to switch whether the VF 3 is opened and the second in-valve passage VF 2 is closed.
  • the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b are connected in series.
  • first outdoor heat exchanger 3a and the second outdoor heat exchanger are opened by opening the first in-valve flow passage VF1 and the third in-valve flow passage VF3 and closing the second in-valve flow passage VF2. 3b are connected in parallel.
  • the switching valve 4 can be switched so that the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b are connected in series or in parallel.
  • the second in-valve flow path VF2 is sandwiched between the first in-valve flow path VF1 and the third in-valve flow path VF3. Therefore, in a state where the second in-valve flow passage VF2 disposed in the central portion of the switching valve 4 is opened, the first in-valve flow passage VF1 and the third in-valve flow passage VF3 arranged vertically are closed. On the other hand, in a state where the second in-valve flow passage VF2 disposed at the central portion of the switching valve 4 is closed, the first and third in-valve flow passage VF1 and the third in-valve flow passage VF3 are opened.
  • the high-temperature high-pressure gas refrigerant discharged from the compressor 1 flows into the four-way valve 2.
  • the four-way valve 2 is set so that the refrigerant flows into the outdoor unit heat exchanger 3.
  • the high-pressure high-temperature gas refrigerant is condensed to be liquid refrigerant by heat exchange with air. At this time, the air having passed through the outdoor unit heat exchanger 3 is heated.
  • the switching valve 4 is set so that the refrigerant flows into the second outdoor unit heat exchanger 3b after passing through the first outdoor unit heat exchanger 3a.
  • the refrigerant flowing from the first connection port C1 into the first outdoor unit heat exchanger 3a is condensed in the plurality of first refrigerant channels RF1 of the first outdoor unit heat exchanger 3a.
  • the condensed refrigerant flows out of the second connection port C2 and flows into the switching valve 4 from the third port P3.
  • the second valve in-flow path VF2 is opened as the second valve body 13b separates from the second valve seat 12b. For this reason, the refrigerant flows out of the second inlet / outlet P2 through the second in-valve channel VF2.
  • the refrigerant which has flowed out from the second inlet / outlet P2 flows into the second outdoor unit heat exchanger 3b from the third connection port C3.
  • the refrigerant flowing into the second outdoor unit heat exchanger 3b is condensed in at least one second refrigerant flow path RF2 of the second outdoor unit heat exchanger 3b.
  • the 1st valve in-valve flow path VF1 is closed because the 1st valve body 13a contacts the 1st valve seat 12a. Therefore, the refrigerant flowing from the first inlet / outlet P1 of the switching valve 4 does not flow to the second inlet / outlet P2 through the first in-valve channel VF1.
  • the third valve in-flow path VF3 is closed by the third valve body 13c being in contact with the third valve seat 12c. For this reason, the refrigerant flowing from the third inlet / outlet P3 of the switching valve 4 does not flow to the fourth inlet / outlet P4 through the third valve inner flow path VF3.
  • the refrigerant condensed in the second refrigerant flow path RF2 to become a liquid phase flows into the first expansion valve 5a, and becomes a low-pressure low-temperature gas-liquid two-phase refrigerant by the throttling of the first expansion valve 5a.
  • the low temperature and low pressure refrigerant flows into the indoor unit heat exchanger 6 and exchanges heat with air. At this time, the air having passed through the indoor unit heat exchanger 6 is cooled.
  • the refrigerant heated by the ambient air changes from gas-liquid 2 phase to gas phase, and then flows into the compressor 1 after passing through the four-way valve 2.
  • the compressor 1 compresses the sucked refrigerant and discharges it again. That is, during the cooling operation, the refrigerant circulates in the refrigeration cycle as shown by the solid arrow in FIG.
  • the flow path is set such that the second in-valve flow path VF2 disposed at the center is opened.
  • the refrigerant passes through the first outdoor unit heat exchanger 3a and then flows into the second outdoor unit heat exchanger 3b.
  • the number of passes of the second outdoor unit heat exchanger 3b is smaller than that of the first outdoor unit heat exchanger 3a, even if the refrigerant which has condensed and increased in the liquid phase flows to the second outdoor unit heat exchanger 3b Can be enhanced. Therefore, the heat transfer coefficient in the pipe can be increased. Thereby, the heat exchanger performance can be improved.
  • the high-temperature high-pressure gas refrigerant discharged from the compressor 1 flows into the four-way valve 2.
  • the four-way valve 2 is set so that the refrigerant flows into the indoor unit heat exchanger 6.
  • the indoor unit heat exchanger 6 the high-pressure high-temperature gas refrigerant condenses to be liquid refrigerant by heat exchange with air. At this time, the air passing through the indoor unit heat exchanger 6 is heated.
  • the refrigerant flows into the first expansion valve 5a and the second expansion valve 5b, and the refrigerant is in a low pressure and low temperature state. Thereafter, when the refrigerant flows into the outdoor unit heat exchanger 3, the switching valve 4 is set to flow in parallel to the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b. Specifically, the refrigerant that has flowed into the second outdoor unit heat exchanger 3b from the fourth connection port C4 through the first expansion valve 5a is at least one second refrigerant flow path of the second outdoor unit heat exchanger 3b. It exchanges heat with air at RF2 and becomes a low pressure low temperature gas refrigerant.
  • the low-temperature low-pressure gas refrigerant flows out of the third connection port C3 and flows into the switching valve 4 from the second port P2.
  • the first in-valve flow passage VF1 is opened. For this reason, the refrigerant flows out of the first inlet / outlet P1 through the first in-valve channel VF1.
  • the refrigerant flowing out of the first inlet / outlet P1 flows to the four-way valve 2.
  • the refrigerant flows into the switching valve 4 from the fourth port P4 through the second expansion valve 5b.
  • the third valve body 13c is separated from the third valve seat 12c, the third valve in-flow passage VF3 is opened.
  • the refrigerant flows out of the third inlet / outlet P3 through the third valve inner flow path VF3 and flows into the first outdoor unit heat exchanger 3a from the second connection port C2.
  • the refrigerant flowing from the second connection port C2 into the first outdoor unit heat exchanger 3a exchanges heat with air in the plurality of first refrigerant channels RF1 of the first outdoor unit heat exchanger 3a, and becomes a low-pressure low-temperature gas refrigerant.
  • the low-temperature low-pressure gas refrigerant flows out of the first connection port C 1 and flows to the four-way valve 2.
  • the second valve in-flow path VF2 is closed by bringing the second valve body 13b into contact with the second valve seat 12b. For this reason, the refrigerant which has flowed in from the second inlet / outlet P2 of the switching valve 4 through the second outdoor unit heat exchanger 3b does not flow to the third inlet / outlet P3 through the second valve inner flow path VF2. Further, the refrigerant flowing from the fourth inlet / outlet P4 of the switching valve 4 through the second expansion valve 5b does not flow to the second inlet / outlet P2 through the second valve inner flow passage VF2.
  • the refrigerant flows into the compressor 1 through the four-way valve 2.
  • the compressor 1 compresses the sucked refrigerant and discharges it again. That is, during the heating operation, the refrigerant circulates in the refrigeration cycle as shown by the solid arrow in FIG.
  • the second valve in-flow path VF2 disposed at the center is closed, and the first in-valve flow path VF1 and the third in-valve flow path VF3 disposed at the upper and lower sides are opened.
  • the refrigerant passes through the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b in parallel.
  • gas-liquid two-phase refrigerant flows in but flows in parallel, so there is little pressure loss, and the pipe The heat transfer rate can also be secured. This can enhance the performance of the heat exchanger.
  • the inlet side of the second outdoor unit heat exchanger 3 b is connected to the location on the air suction side of the outdoor unit heat exchanger 3.
  • This is, for example, an azeotropic refrigerant such as R410a and a single refrigerant such as R32 with a small pressure loss, and when using the outdoor unit heat exchanger 3 as a condenser, all the outdoor unit heat exchangers 3 are opposed
  • the use as a stream can enhance the performance of the heat exchanger.
  • the outdoor unit heat exchanger 3 of the present embodiment the first outdoor unit heat exchanger 3 a and the second outdoor unit heat exchanger 3 b can be switched in series or in parallel by the switching valve 4. Therefore, the number of refrigerant channels (the number of paths) can be changed between the cooling operation and the heating operation. Thereby, the performance of the outdoor unit heat exchanger 3 can be enhanced.
  • the number of the plurality of first refrigerant flow paths RF1 of the first outdoor unit heat exchanger 3a is at least one second of the second outdoor unit heat exchanger 3b.
  • the number is larger than the number of refrigerant channels RF2.
  • the first in-valve flow passage VF1 and the third in-valve flow passage VF3 are closed and the second in-valve flow passage VF2 is opened, or the first in-valve flow passage VF1 and third valve It is configured to switch whether the flow path VF3 is opened and the second in-valve flow path VF2 is closed. Therefore, the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b can be switched in series or in parallel by one switching valve 4. Therefore, the outdoor unit heat exchanger 3 can be miniaturized. Moreover, when switching the 1st outdoor unit heat exchanger 3a and the 2nd outdoor unit heat exchanger 3b with three valves like before, three valves have a total of six inlet-outlets. According to the outdoor unit heat exchanger 3 of the present embodiment, since there are four inlets and outlets, the outdoor unit heat exchanger 3 can be miniaturized from this point as well.
  • the switching valve 4 axially drives the shaft portion 11 to which the first valve body 13a, the second valve body 13b, and the third valve body 13c are attached.
  • each of the first in-valve flow path VF1, the second in-valve flow path VF2, and the third in-valve flow path VF3 can be opened and closed. Therefore, it is possible to simultaneously control each of the first in-valve flow path VF1, the second in-valve flow path VF2, and the third in-valve flow path VF3. Further, the operability of the first valve body, the second valve body and the third valve body is excellent.
  • the drive part 14 which drives the axial part 11 to which the 1st valve body 13a, the 2nd valve body 13b, and the 3rd valve body 13c were attached may be one, cost can be held down.
  • the second in-valve flow passage VF2 is sandwiched between the first in-valve flow passage VF1 and the third in-valve flow passage VF3.
  • the axial portion 11 to which the first valve body 13a, the second valve body 13b, and the third valve body 13c are attached is driven in the axial direction, whereby the flow in the first valve internal flow VF1 and the third valve It switches whether the passage VF3 is closed and the second in-valve passage VF2 is opened, or the first in-valve passage VF1 and the third in-valve passage VF3 are opened and the second in-valve passage VF2 is closed be able to.
  • the refrigerant flowing through the first outdoor unit heat exchanger 3a, the second outdoor unit heat exchanger 3b and the switching valve 4 is either a single refrigerant or an azeotropic refrigerant. It is. Therefore, a single refrigerant and an azeotropic refrigerant can be used as the refrigerant.
  • the refrigerant flowing through the first outdoor unit heat exchanger 3a, the second outdoor unit heat exchanger 3b, and the switching valve 4 may be a non-azeotropic refrigerant. . Therefore, a non-azeotropic refrigerant can be used as the refrigerant.
  • the refrigeration cycle apparatus of the present embodiment includes a compressor 1, the outdoor unit heat exchanger 3 described above, an expansion valve 5, and an indoor unit heat exchanger 6. Further, the heat exchanger of the present embodiment can be applied to any of the outdoor unit heat exchanger 3 and the indoor unit heat exchanger 6. That is, the heat exchanger of the present embodiment may be at least one of a condenser and an evaporator. Therefore, it is possible to provide a refrigeration cycle apparatus equipped with at least one of the outdoor unit heat exchanger 3 and the indoor unit heat exchanger 6 that can be improved in performance and miniaturized.
  • the structure of switching valve 4 is different from that of the first embodiment.
  • the valve body 15 attached to the shaft portion 11 has a U-shaped flow path 15 a inside the valve body 15.
  • the flow path 15a is configured to be able to communicate the first inlet / outlet P1 and the second inlet / outlet P2, the second inlet / outlet P2 and the third inlet / outlet P3, the third inlet / outlet P3 and the fourth inlet / outlet.
  • the valve body 15 causes the first inlet / outlet P1 and the second inlet / outlet P2 to communicate with each other or causes the second inlet / outlet P2 to communicate with the third inlet / outlet P3 when the shaft portion 11 is axially driven by the drive portion 14 It is configured to switch whether the third port P3 and the fourth port P4 are in communication with each other.
  • valve body 15 is disposed at the center of switching valve 4. Then, the second valve in-flow path VF2 is opened by the flow path 15a of the valve body 15. That is, the valve body 15 is disposed such that the refrigerant flows through the flow path 15a of the valve body 15 in series with the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b. Specifically, the refrigerant which has flowed out from the second connection port C2 of the first outdoor unit heat exchanger 3a flows into the switching valve 4 from the third inlet / outlet P3 and passes through the flow path 15a of the valve body 15 to form the second inlet / outlet. It flows out from P2 and flows into the second outdoor unit heat exchanger 3b from the third connection port C3.
  • valve body 15 is disposed above the switching valve 4. Then, the first in-valve flow passage VF1 is opened by the flow passage 15a of the valve body 15. That is, the valve body 15 is disposed so that the refrigerant flows in parallel through the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b through the flow path 15a of the valve body 15.
  • valve body 15 may be disposed below the switching valve 4 and the third valve in-flow path VF3 may be opened by the flow path 15a of the valve body 15.
  • valve body 15 may be moved to the axial direction of the axial part 11 by a solenoid valve, it is not limited to this, For example, you may move to the axial direction of the axial part 11 with a refrigerant
  • both the outdoor unit heat exchanger 3 and the indoor unit heat exchanger 6 are equipped with the heat exchanger of the present invention. That is, both the condenser and the evaporator are the heat exchangers of the present invention. Therefore, in the air conditioner according to the third embodiment, the number of refrigerant channels (number of passes) of both the outdoor unit heat exchanger 3 and the indoor unit heat exchanger 6 is variable.
  • the indoor unit heat exchanger 6 acts as an evaporator when the outdoor unit heat exchanger 3 functions as a condenser, the operation of the switching valve 4 is reversed.
  • the switching valve 4 (4a) of the outdoor unit heat exchanger 3 is switched such that the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b are arranged in series, the indoor unit heat exchanger 6
  • the switching valve 4 (4b) is switched so that the first indoor unit heat exchanger 6a and the second indoor unit heat exchanger 6b are arranged in parallel.
  • the outdoor unit heat exchanger 3 functions as an evaporator, so the operation of the switching valve 4 is reversed.
  • the switching valve 4 (4b) of the indoor unit heat exchanger 6 is switched such that the first indoor unit heat exchanger 6a and the second indoor unit heat exchanger 6b are arranged in series, the outdoor unit heat exchanger 3
  • the switching valve 4 (4a) is switched such that the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b are arranged in parallel.
  • the structure of switching valve 4 is different from that of the first embodiment.
  • the switching valve 4 is a circular rotary valve.
  • the switching valve 4 includes a main body 10, a shaft 11, a flat valve seat 12, and a valve body 13.
  • the main body 10 has a cylindrical shape.
  • the shaft portion 11 is connected to a motor (not shown).
  • the valve seat 12 has a flat plate shape.
  • the valve body 13 has a cylindrical shape.
  • a flat valve seat 12 and a cylindrical valve body 13 are disposed in a cylindrical main body 10.
  • the valve seat 12 is provided with a first port P1, a second port P2, a third port P3 and a fourth port P4.
  • the valve body 13 is configured to be slidable on one surface of the valve seat 12.
  • the valve body 13 has a first flow passage 131 and a second flow passage 132.
  • the shaft portion 11 is connected to the center of the valve body 13. When the shaft portion 11 is rotated by the driving force of a motor (not shown), the cylindrical valve element 13 rotates in the circumferential direction as shown by the arc arrow in the drawing.
  • the valve body 13 is rotated in the circumferential direction by the rotation of the shaft 11, so that the first passage 131 communicates the first inlet / outlet P1 with the second inlet / outlet P2, or the second passage 132 is connected with the second inlet / outlet P2. And the third inlet / outlet port P3 are switched.
  • the flow path of the switching valve 4 is set so that the refrigerant flows in series between the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b. That is, the valve body 13 is disposed such that the refrigerant flows in series through the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b through the second flow path 132.
  • the refrigerant flowing out from the second connection port C2 of the first outdoor unit heat exchanger 3a flows into the second flow path 132 from the third port P3, and the second It flows out through the flow path 132 from the second inlet / outlet P2, and flows into the second outdoor unit heat exchanger 3b from the third connection port C3.
  • the case where the outdoor unit heat exchanger 3 is used as an evaporator (during heating operation) will be described with reference to FIG.
  • the valve body 13 rotates from the state of FIG. 9, the circuit shown in FIG. 10 is obtained.
  • the flow path of the switching valve 4 is set so that the refrigerant flows in parallel between the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b. That is, the valve body 13 is disposed so that the refrigerant flows in parallel through the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b through the first flow path 131 and the second flow path 132. .
  • the refrigerant flowing out from the third connection port C3 of the second outdoor unit heat exchanger 3b flows into the first flow path 131 from the second inlet / outlet P2, and the first It flows out of the first inlet / outlet P1 through the flow path 131 and flows into the four-way valve 2 shown in FIG. Further, the refrigerant flowing from the fourth inlet / outlet P4 into the second flow path 132 flows out through the second flow path 132 from the third inlet / outlet P3 and flows into the first outdoor unit heat exchanger 3a from the second connection port C2. Do.
  • the performance of the heat exchanger can be enhanced as in the first embodiment. Therefore, it is possible to provide a heat exchanger capable of improving performance and downsizing, and a refrigeration cycle apparatus equipped with the heat exchanger.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention concerne un échangeur de chaleur d'unité extérieure (3) comprenant un premier échangeur de chaleur d'unité extérieure (3a), d'un second échangeur de chaleur d'unité extérieure (3b) et d'une soupape de commutation (4). Le nombre d'une pluralité de premiers canaux d'écoulement de fluide frigorigène (RF1) du premier échangeur de chaleur d'unité extérieure (3a) est supérieur au nombre d'au moins un second canal d'écoulement de fluide frigorigène (RF2) du second échangeur de chaleur d'unité extérieure (3b). La soupape de commutation (4) est configurée de manière à commuter entre la fermeture du premier passage d'écoulement interne de soupape (VF1) et du troisième passage d'écoulement interne de soupape (VF3) et l'ouverture d'un second passage d'écoulement interne de soupape (VF2)), et l'ouverture du premier passage d'écoulement interne de soupape (VF1) et du troisième passage d'écoulement interne de soupape (VF3) et la fermeture du second passage d'écoulement interne de soupape (VF2)
PCT/JP2016/078057 2016-09-23 2016-09-23 Échangeur de chaleur et dispositif à cycle de réfrigération WO2018055740A1 (fr)

Priority Applications (3)

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EP16916807.7A EP3517855B1 (fr) 2016-09-23 2016-09-23 Échangeur de chaleur et dispositif à cycle de réfrigération
JP2018540571A JP6671491B2 (ja) 2016-09-23 2016-09-23 熱交換器および冷凍サイクル装置
PCT/JP2016/078057 WO2018055740A1 (fr) 2016-09-23 2016-09-23 Échangeur de chaleur et dispositif à cycle de réfrigération

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PCT/JP2016/078057 WO2018055740A1 (fr) 2016-09-23 2016-09-23 Échangeur de chaleur et dispositif à cycle de réfrigération

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WO2018055740A9 true WO2018055740A9 (fr) 2019-02-21

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WO2019215881A1 (fr) * 2018-05-10 2019-11-14 三菱電機株式会社 Dispositif à cycle frigorifique
WO2021250738A1 (fr) * 2020-06-08 2021-12-16 三菱電機株式会社 Climatiseur
KR20220043595A (ko) * 2020-09-29 2022-04-05 엘지전자 주식회사 유로전환장치
CN117203476A (zh) * 2021-04-23 2023-12-08 三菱电机株式会社 空调机

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JP4209860B2 (ja) * 1997-12-16 2009-01-14 パナソニック株式会社 可燃性冷媒を用いた空気調和装置
JP2002243296A (ja) * 2001-02-20 2002-08-28 Fujitsu General Ltd 空気調和機
JP5625691B2 (ja) * 2010-09-30 2014-11-19 ダイキン工業株式会社 冷凍装置
KR101233209B1 (ko) 2010-11-18 2013-02-15 엘지전자 주식회사 히트 펌프
US9752803B2 (en) * 2011-02-16 2017-09-05 Johnson Controls Technology Company Heat pump system with a flow directing system
JP5927415B2 (ja) * 2011-04-25 2016-06-01 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置
JP5985418B2 (ja) * 2013-03-04 2016-09-06 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 冷凍サイクル装置、ならびに冷凍サイクル装置を備えた冷凍装置および空気調和装置
JP2015075211A (ja) * 2013-10-11 2015-04-20 ダイキン工業株式会社 流路切換弁および冷媒回路

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EP3517855B1 (fr) 2020-09-16
WO2018055740A1 (fr) 2018-03-29
JPWO2018055740A1 (ja) 2019-06-24
EP3517855A4 (fr) 2019-10-09
JP6671491B2 (ja) 2020-03-25

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