WO2018055740A1 - 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
WO2018055740A1
WO2018055740A1 PCT/JP2016/078057 JP2016078057W WO2018055740A1 WO 2018055740 A1 WO2018055740 A1 WO 2018055740A1 JP 2016078057 W JP2016078057 W JP 2016078057W WO 2018055740 A1 WO2018055740 A1 WO 2018055740A1
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WIPO (PCT)
Prior art keywords
valve
heat exchanger
refrigerant
flow path
outdoor unit
Prior art date
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PCT/JP2016/078057
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English (en)
Japanese (ja)
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WO2018055740A9 (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.)
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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 refrigeration cycle apparatus is a cold air conditioner.
  • a general cold air conditioner includes a compressor, a four-way valve, a condenser, an expansion valve, and an evaporator. These components communicate with each other via a connection pipe to constitute a refrigeration cycle.
  • the refrigerant flow is reversed by switching 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 usage of the outdoor unit and the heat exchanger of the indoor unit during cooling operation and heating operation are different. That is, the outdoor unit and the indoor unit heat exchanger are respectively used as a condenser or an evaporator.
  • the state of the refrigerant passing through the heat exchanger differs between the condenser and the evaporator.
  • the refrigerant flows in a superheated gas state at the heat exchanger inlet, becomes a gas-liquid two-phase state with heat exchange, and becomes a supercooled liquid at the heat exchanger outlet.
  • the refrigerant enters a liquid phase or a gas-liquid two phase state at the heat exchanger inlet, gasifies along with heat exchange, and enters a saturated gas state at the heat exchanger outlet.
  • the flow rate of the refrigerant flowing through the heat transfer tube of the heat exchanger differs depending on whether the refrigerant is in a liquid state or a gas state.
  • the performance of the heat exchanger varies depending on the flow rate of the refrigerant.
  • the number (number of passes) or length of the refrigerant flow paths of the outdoor unit heat exchanger must be adjusted.
  • the number or length of the refrigerant flow paths is constant during cooling operation and heating operation.
  • a general cooling / air-conditioning apparatus is designed so that optimum performance can be obtained in either one of the cooling operation and the heating operation. Therefore, a general cooling / heating air-conditioning apparatus has a problem that the performance of the other of the cooling operation and the heating operation is deteriorated.
  • Patent Document 1 An air conditioner for solving this problem is described in JP-A-2015-117936 (Patent Document 1).
  • the air conditioner described in this publication two unit channels are connected in series during cooling operation, and two unit channels are connected in parallel during heating operation.
  • the two unit channels are switched in series or in parallel by three valves.
  • the number of two unit channels is equal. That is, the heat exchanger is equally divided into the two unit channels. Therefore, the number of refrigerant flow paths (number of passes) at the location where the liquid phase of the refrigerant increases increases, and the flow velocity of the refrigerant slows down. Therefore, when this air conditioner is used as, for example, a condenser, the heat transfer performance in the unit flow channel on the downstream side where the liquid phase of the refrigerant increases among the two unit flow channels decreases. For this reason, there exists a problem that the performance of a heat exchanger falls.
  • the outdoor unit heat exchanger has three valves for switching two unit flow paths in series or in parallel. For this reason, there exists a problem that size reduction of a heat exchanger is difficult.
  • the present invention has been made in view of the above problems, and an object of the present invention is to provide a heat exchanger capable of improving performance and downsizing and a refrigeration cycle apparatus including the 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 side opposite to the first connection port. And have.
  • 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 on the side opposite to the third connection port. With mouth.
  • the switching valve has a first inlet / outlet, a second inlet / outlet, a third inlet / outlet, a fourth inlet / outlet, a first valve inner flow path, a second valve inner flow path, and a third valve inner flow path.
  • the first doorway is connected to the first connection port.
  • the second doorway is connected to the third connection port.
  • the third doorway is connected to the second connection port.
  • the fourth doorway is connected to the fourth connection port.
  • the first in-valve channel communicates the first entrance and the second entrance.
  • the second valve flow path communicates the second entrance and the third entrance.
  • the third intra-valve channel has a third intra-valve channel that communicates the third entrance and the fourth entrance.
  • the number of the plurality of first refrigerant channels in the first heat exchange unit is greater than the number of at least one second refrigerant channel in the second heat exchange unit.
  • the switching valve the first valve flow path and the third valve flow path are closed and the second valve flow path is opened, or the first valve flow path and the third valve flow path are opened. It is configured to switch whether the two-valve flow path is closed.
  • the number of the plurality of first refrigerant channels in the first heat exchange unit is greater than the number of at least one second refrigerant channel in the second heat exchange unit. For this reason, if the second heat exchanging unit is operated so that 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 area 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 switching valve has the first valve flow path and the third valve flow path closed and the second valve flow path is opened, or the first valve flow path and the third valve flow path are opened. It is configured to switch whether the second valve flow path is closed. For this reason, a 1st heat exchange part and a 2nd heat exchange part can be switched in series or in parallel by one switching valve. Therefore, the heat exchanger can be reduced in size.
  • an air conditioner will be described as an example of a refrigeration cycle apparatus.
  • the refrigeration cycle apparatus is not limited to an 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 an air conditioner according to Embodiment 1 of the present invention.
  • FIG. 2 is a structural diagram of the refrigeration cycle during the heating operation of the air conditioner according to Embodiment 1 of the present invention.
  • the air conditioner (refrigeration cycle apparatus) in Embodiment 1 includes a compressor 1, a four-way valve 2, an outdoor unit heat exchanger 3 (a first outdoor unit heat exchanger 3a, a second outdoor unit heat exchanger 3b, The switching valve 4), the expansion valve 5 (first expansion valve 5a, second expansion valve 5b), and the indoor unit heat exchanger 6 are provided.
  • Compressor 1 four-way valve 2, outdoor unit heat exchanger 3 (first outdoor unit heat exchanger 3a, second outdoor unit heat exchanger 3b, switching valve 4), expansion valve 5 and indoor unit heat exchanger 6 are piped It is communicated through. In this way, a refrigeration cycle (refrigerant circuit) is configured.
  • the refrigerant flows through 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, the first It flows through the first expansion valve 5a, the second expansion valve 5b, and the indoor unit heat exchanger 6.
  • a single refrigerant or an azeotropic refrigerant can be used as the single refrigerant.
  • R410a can be used as the azeotropic refrigerant.
  • a non-azeotropic refrigerant can be used as the refrigerant.
  • R1234yf can be used as the non-azeotropic refrigerant.
  • the air conditioner includes a control device (controller) (not shown).
  • the control device is configured to control each means, device, etc. of the refrigeration cycle device by performing calculations, instructions, and the like.
  • the control device is configured to control the operation of the four-way valve 2 and the switching valve 4, for example.
  • a compressor 1, a four-way valve 2, an outdoor unit heat exchanger 3 (first outdoor unit heat exchanger 3a, second outdoor unit heat exchanger 3b, switching valve 4), and expansion valve 5 (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 with a constant compression capacity, or may be an inverter compressor with a variable compression capacity.
  • This inverter compressor is configured to be able to variably control the rotation speed. Specifically, the rotation speed of the inverter compressor is adjusted by changing the drive frequency based on an instruction from a control device (controller) (not shown). Thereby, the compression capacity changes.
  • This compression capacity is the amount of refrigerant delivered 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 refrigerant flow 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 have.
  • 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.
  • the outdoor unit heat exchanger 3 is composed of, for example, pipes (heat transfer tubes) and fins.
  • 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 serves as a throttle device that decompresses the refrigerant condensed by the outdoor unit heat exchanger (condenser) 3 during the cooling operation.
  • the expansion valve 5 serves as a throttle device that decompresses the refrigerant condensed by the indoor unit heat exchanger (condenser) 6 during heating operation.
  • the expansion valve 5 includes 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.
  • the first expansion valve 5a is, for example, an electronic expansion valve.
  • the second expansion valve 5b is connected between the first expansion valve 5a and the indoor unit heat exchanger 6, and to the four-way valve 2.
  • the second expansion valve 5b is configured to expand (depressurize) the refrigerant by adjusting the valve opening.
  • 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.
  • Embodiment 1 two expansion valves, a first expansion valve 5a and a second expansion valve 5b, are provided.
  • the 1st outdoor unit heat exchanger 3a and the 2nd outdoor unit heat exchanger 3b are used as an evaporator, in order to arrange the refrigerant circulation amount which flows in per pass number, the 1st outdoor unit heat exchanger The refrigerant circulation amount flowing through 3a 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 narrower than 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 is a condenser that condenses the refrigerant compressed by the compressor 1 during heating operation.
  • the indoor unit heat exchanger 6 is for performing heat exchange between the refrigerant and the air.
  • the indoor unit heat exchanger 6 includes, for example, pipes (heat transfer tubes) and fins.
  • the case where the number of refrigerant channels (number of passes) of the outdoor unit heat exchanger 3 is variable will be described.
  • the number of refrigerant channels (number of passes) of the indoor unit heat exchanger 6 is variable.
  • the number of refrigerant flow paths (the 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 during cooling operation of the outdoor unit heat exchanger 3 according to Embodiment 1 of the present invention.
  • FIG. 4 is a structural diagram at the time of heating operation of the outdoor unit heat exchanger 3 according to Embodiment 1 of the present invention.
  • the first outdoor unit heat exchanger (first heat exchanging unit) 3a has a plurality of first refrigerant flow paths 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 side opposite 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 part) 3b has 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 flow path RF2 on the side opposite to the third connection port C3.
  • 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 first refrigerant flow paths 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. There are more than the number of flow paths RF2.
  • the number (number of passes) of the plurality of first refrigerant flow paths RF1 is, for example, four.
  • the number (number of passes) 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 paths of the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b.
  • the switching valve 4 includes a first inlet / outlet P1, a second inlet / outlet P2, a third outlet / inlet P3, a fourth inlet / outlet P4, a first valve inner flow path VF1, a second valve inner flow path VF2, and a third valve.
  • the main body 10 of the switching valve 4 is provided with a total of four inlets and outlets through which refrigerant flows in or out.
  • the 1st entrance / exit P1 of the switching valve 4 is connected to the 1st connection port C1 of the 1st outdoor unit heat exchanger 3a.
  • the 2nd entrance / exit P2 of the switching valve 4 is connected to the 3rd connection port C3 of the 2nd outdoor unit heat exchanger 3b.
  • the 3rd entrance / exit P3 of the switching valve 4 is connected to the 2nd connection port C2 of the 1st outdoor unit heat exchanger 3a.
  • the 4th entrance / exit P4 of the switching valve 4 is connected to the 4th connection port C4 of the 2nd outdoor unit heat exchanger 3b.
  • the first inlet / outlet P1 is connected to the refrigerant inlet side of the first outdoor unit heat exchanger 3a during the cooling operation.
  • the 2nd entrance / exit P2 is connected to the refrigerant
  • the 3rd entrance / exit P3 is connected to the refrigerant
  • the fourth inlet / outlet P4 is connected to the refrigerant outlet side of the second outdoor unit heat exchanger 3b during the cooling operation.
  • the 1st entrance / exit P1 is connected to the refrigerant
  • the 2nd entrance / exit P2 is connected to the refrigerant
  • the 3rd entrance / exit P3 is connected to the refrigerant
  • the 4th entrance / exit P4 is connected to the refrigerant
  • the main body 10 of the switching valve 4 has a cylindrical shape, and a first in-valve channel VF1, a second in-valve channel VF2, and a third in-valve channel VF3 are provided in the main body 10 of the switching valve 4. Yes.
  • the first in-valve channel VF1 communicates the first entrance P1 and the second entrance P2.
  • the first valve seat 12a is disposed in the first valve flow path VF1.
  • the first valve seat 12a is disposed between the first entrance P1 and the second entrance 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 to open the first in-valve flow path VF1 by leaving the first valve seat 12a. .
  • the second valve flow path VF2 communicates the second inlet / outlet P2 and the third inlet / outlet P3.
  • the second valve seat 12b is disposed in the second valve flow path VF2.
  • the second valve seat 12b is disposed between the second entrance P2 and the third entrance P3.
  • the second valve body 13b is configured to close the second in-valve flow path VF2 by contacting the second valve seat 12b, and open the second in-valve flow path VF2 by leaving the second valve seat 12b. .
  • the third in-valve channel VF3 communicates with the third inflow port P3 and the fourth inflow port P4 in the second in-valve channel VF2.
  • the third valve seat 12c is disposed in the third valve flow path VF3.
  • the third valve seat 12c is disposed between the third entrance / exit P3 and the fourth entrance / exit P4.
  • the third valve body 13c is configured to close the third valve passage VF3 by contacting the third valve seat 12c and to open the third valve passage VF3 by leaving the third valve seat 12c. .
  • the first valve body 13a, the second valve body 13b, and the third valve body 13c are attached to the shaft portion 11.
  • Each of the first valve body 13a, the second valve body 13b, and the third valve body 13c has a flat plate shape.
  • the first valve body 13a, the second valve body 13b, and the third valve body 13c may be attached to the shaft portion 11 with the shaft portion 11 penetrating through the center of each flat plate shape.
  • the first valve body 13a, the second valve body 13b, and the third valve body 13c are arranged away from each other in the axial direction of the shaft portion 11.
  • the switching valve 4 is composed of one axis, the flow path switching can be operated simultaneously.
  • the four-way valve 2 is switched from the refrigerant circuit during the heating operation to the refrigerant circuit during the cooling operation to defrost.
  • the flow path can be switched 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 14a and a coil 14b.
  • the movable part 14 a is attached to the shaft part 11.
  • the coil 14b is disposed so as to surround the movable portion 14a.
  • the movable portion 14a is configured to be movable in the axial direction of the shaft portion 11 by a magnetic flux generated by energizing the coil 14b based on an instruction from a control device (controller) (not shown). Accordingly, 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 with the movement of the movable portion 14a.
  • the switching valve 4 is composed of one shaft, only one drive unit 14 is required. Specifically, the switching valve 4 can be configured with one movable part 14 a and one coil 14 b of the drive part 14. For this reason, cost can be held down.
  • the switching valve 4 is configured such that the first valve flow path VF1 and the third valve flow path VF3 are closed and the second valve flow path VF2 is opened, or the first valve flow path VF1 and the third valve flow path VF3. It is configured to switch whether VF3 is opened and the second valve flow path VF2 is closed.
  • the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b are opened by closing the first valve flow path VF1 and the third valve flow path VF3 and opening the second valve flow path VF2. Are connected in series.
  • the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger are closed by opening the first valve flow path VF1 and the third valve flow path VF3 and closing the second valve flow path VF2. 3b is connected in parallel. In this way, 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 valve flow path VF2 is sandwiched between the first valve flow path VF1 and the third valve flow path VF3. Therefore, the first valve flow path VF1 and the third valve flow path VF3 disposed above and below are closed while the second valve flow path VF2 disposed at the center of the switching valve 4 is opened. On the other hand, in the state in which the second in-valve channel VF2 disposed in the central portion of the switching valve 4 is closed, the first in-valve channel VF1 and the third in-valve channel VF3 disposed in the vertical direction are opened.
  • the high-temperature and 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 and high-temperature gas refrigerant condenses into a liquid refrigerant by heat exchange with air. At this time, the air that has 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 into the first outdoor unit heat exchanger 3a from the first connection port C1 is condensed in the plurality of first refrigerant flow paths RF1 of the first outdoor unit heat exchanger 3a.
  • the condensed refrigerant flows out from the second connection port C2 and flows into the switching valve 4 from the third inlet / outlet P3.
  • the second valve body channel VF2 is opened by the second valve body 13b being separated from the second valve seat 12b. For this reason, the refrigerant flows out from the second inlet / outlet P2 through the second valve flow path VF2.
  • the refrigerant that has flowed out of the second inlet / outlet P2 flows into the second outdoor unit heat exchanger 3b from the third connection port C3.
  • the refrigerant that has flowed into the second outdoor unit heat exchanger 3b is condensed in at least one second refrigerant channel RF2 of the second outdoor unit heat exchanger 3b.
  • the 1st valve body 13a contact
  • the refrigerant that has flowed from the first inlet / outlet P1 of the switching valve 4 does not flow to the second inlet / outlet P2 through the first valve flow path VF1.
  • the third valve body 13c is in contact with the third valve seat 12c so that the third valve flow path VF3 is closed. For this reason, the refrigerant flowing in 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 passage VF3.
  • the low-temperature and low-pressure refrigerant flows into the indoor unit heat exchanger 6 and exchanges heat with air.
  • the air that has passed through the indoor unit heat exchanger 6 is cooled.
  • the refrigerant heated by the surrounding air changes from the gas-liquid two phase to the gas phase, and then passes through the four-way valve 2 and then flows into the compressor 1.
  • 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 indicated by solid line arrows in FIG.
  • the flow path is set so that the second flow path VF2 disposed in the center is opened.
  • the refrigerant flows through the first outdoor unit heat exchanger 3a and then flows into the second outdoor unit heat exchanger 3b.
  • the flow rate is increased even when the condensed and increased liquid phase flows to the second outdoor unit heat exchanger 3b.
  • the in-tube heat transfer coefficient can be increased. Thereby, heat exchanger performance can be improved.
  • the high-temperature and 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 during the heating operation.
  • the indoor unit heat exchanger 6 the high-pressure and high-temperature gas refrigerant condenses into a liquid refrigerant by heat exchange with air. At this time, the air that has passed 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 so as 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 by RF2 and becomes a low-pressure low-temperature gas refrigerant.
  • the low-temperature and low-pressure gas refrigerant flows out from the third connection port C3 and flows into the switching valve 4 from the second inlet / outlet P2.
  • the first valve body flow path VF1 is opened when the first valve body 13a is separated from the first valve seat 12a. For this reason, the refrigerant flows out of the first inlet / outlet port P1 through the first in-valve channel VF1.
  • the refrigerant flowing out from the first inlet / outlet P ⁇ b> 1 flows to the four-way valve 2.
  • the refrigerant flows into the switching valve 4 from the fourth inlet / outlet P4 through the second expansion valve 5b.
  • the third valve body channel VF3 is opened when the third valve body 13c is separated from the third valve seat 12c. For this reason, the refrigerant flows out of the third inlet / outlet P3 through the third valve flow path VF3, and flows into the first outdoor unit heat exchanger 3a from the second connection port C2.
  • the refrigerant flowing into the first outdoor unit heat exchanger 3a from the second connection port C2 exchanges heat with air in the plurality of first refrigerant channels RF1 of the first outdoor unit heat exchanger 3a to become low-pressure low-temperature gas refrigerant.
  • the low-temperature and low-pressure gas refrigerant flows out from the first connection port C ⁇ b> 1 and flows into the four-way valve 2.
  • 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 indicated by solid line arrows in FIG.
  • the flow path is set so that the second valve flow path VF2 disposed at the center is closed and the first valve flow path VF1 and the third valve flow path VF3 disposed above and below are opened.
  • the refrigerant passes through the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b in parallel.
  • the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b are used as an evaporator, a gas-liquid two-phase refrigerant flows in, but since it flows in parallel, there is little pressure loss and Heat transfer rate can be secured. Thereby, the performance of a heat exchanger can be improved.
  • the inlet side of the second outdoor unit heat exchanger 3b is connected to 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 the outdoor unit heat exchanger 3 is used as a condenser, all the outdoor unit heat exchangers 3 face each other. By using it as a flow, the performance of the heat exchanger can be enhanced.
  • the switching valve 4 can switch the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b in series or in parallel. For this reason, the number of refrigerant flow paths (number of passes) 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 channels RF1 of the first outdoor unit heat exchanger 3a is equal to or more than the second number of the second outdoor unit heat exchanger 3b. More than the number of refrigerant channels RF2. For this reason, if the second outdoor unit heat exchanger 3b is operated so that the liquid phase of the refrigerant increases, the flow rate of the refrigerant is increased by reducing the number of refrigerant flow paths in the area where the liquid phase of the refrigerant increases. can do. Therefore, since the heat transfer performance in the location where the liquid phase of the refrigerant increases can be improved, the performance of the outdoor unit heat exchanger 3 can be improved.
  • the switching valve 4 is configured such that the first valve flow path VF1 and the third valve flow path VF3 are closed and the second valve flow path VF2 is opened, or the first valve flow path VF1 and the third valve flow path VF3 are opened.
  • the flow path VF3 is opened and the second valve flow path VF2 is switched. 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 reduced in size.
  • the three valves have a total of six entrances. According to the outdoor unit heat exchanger 3 of the present embodiment, since there are four doorways, the outdoor unit heat exchanger 3 can be downsized also from this point.
  • the switching valve 4 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 in the axial direction.
  • each of the first intra-valve channel VF1, the second intra-valve channel VF2, and the third intra-valve channel VF3 can be opened and closed.
  • each of the 1st valve flow path VF1, the 2nd valve flow path VF2, and the 3rd valve flow path VF3 can be controlled simultaneously.
  • 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 valve flow path VF2 is sandwiched between the first valve flow path VF1 and the third valve flow path VF3. Therefore, the shaft 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 first valve flow path VF1 and the third valve flow The path VF3 is closed and the second valve flow path VF2 is opened, or the first valve flow path VF1 and the third valve flow path VF3 are opened and the second valve flow path 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, an expansion valve 5, and an indoor unit heat exchanger 6.
  • the heat exchanger of this Embodiment is applicable to both 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. For this reason, the refrigerating cycle apparatus provided with at least any one of the outdoor unit heat exchanger 3 and the indoor unit heat exchanger 6 which can improve performance and can be reduced in size can be provided.
  • Embodiment 2 FIG. In the following, unless otherwise specified, the same reference numerals are given to the same components as those in the first embodiment, and description thereof will not be repeated. This also applies to the following third and fourth embodiments.
  • 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 allow communication between the first inlet / outlet P1 and the second inlet / outlet P2, the second inlet / outlet P2 and the third outlet / inlet P3, and the third inlet / outlet P3 and the fourth inlet / outlet.
  • the valve body 15 causes the first entrance P1 and the second entrance P2 to communicate with each other or the second entrance P2 and the third entrance P3 to communicate with each other when the shaft portion 11 is driven in the axial direction by the drive unit 14. Or it is comprised so that it may switch whether the 3rd entrance / exit P3 and the 4th entrance / exit P4 are connected.
  • the valve body 15 is disposed at the center of the switching valve 4 during the cooling operation. Then, the second in-valve channel VF2 is opened by the channel 15a of the valve body 15. That is, the valve body 15 is disposed so that the refrigerant flows in series 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. Specifically, the refrigerant that 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 port P3, passes through the flow path 15a of the valve body 15, and passes through the second port. It flows out from P2, and flows into the 2nd outdoor unit heat exchanger 3b from the 3rd connection port C3.
  • the valve body 15 is disposed above the switching valve 4. Then, the first in-valve channel VF1 is opened by the channel 15a of the valve body 15. That is, the valve body 15 is disposed such 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. Specifically, the refrigerant that has flowed out from the fourth connection port C4 of the second outdoor unit heat exchanger 3b flows into the switching valve 4 from the second inlet / outlet P2, passes through the flow path 15a of the valve body 15, and enters the first inlet / outlet. It flows out from P1 and flows into the four-way valve 2 shown in FIG.
  • the refrigerant flowing into the switching valve 4 from the fourth inlet / outlet P4 flows out of the third inlet / outlet P3 through the third valve flow path VF3, and flows into the first outdoor unit heat exchanger 3a from the second connection port C2. To do.
  • the refrigerant flowing into the first outdoor unit heat exchanger 3a flows out from the first connection port C1, and flows into the four-way valve 2 shown in FIG.
  • valve body 15 may be disposed below the switching valve 4 and the third in-valve flow path VF3 may be opened by the flow path 15a of the valve body 15.
  • the valve body 15 may be moved in the axial direction of the shaft portion 11 by an electromagnetic valve, but is not limited thereto, and may be moved in the axial direction of the shaft portion 11 by, for example, refrigerant pressure.
  • Embodiment 3 Referring to FIG. 8, in the air conditioner according to Embodiment 3 of the present invention, 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 Embodiment 3, the number of refrigerant flow paths (the number of passes) of both the outdoor unit heat exchanger 3 and the indoor unit heat exchanger 6 is variable.
  • the operation of the switching valve 4 is reversed because the indoor unit heat exchanger 6 acts as an evaporator.
  • the switching valve 4 (4a) of the outdoor unit heat exchanger 3 is switched so 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 acts as an evaporator, so that the operation of the switching valve 4 is reversed.
  • the switching valve 4 (4b) of the indoor unit heat exchanger 6 is switched so 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 so that the first outdoor unit heat exchanger 3a and the second outdoor unit heat exchanger 3b are arranged in parallel.
  • Embodiment 4 FIG. Referring to FIGS. 9 and 10, in the air conditioner according to the fourth embodiment of the present invention, 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 portion 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 plate-shaped valve seat 12 and a columnar valve body 13 are arranged in a cylindrical main body 10.
  • the valve seat 12 is provided with a first entrance P1, a second entrance P2, a third entrance P3, and a fourth entrance 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 path 131 and a second flow path 132.
  • a shaft portion 11 is connected to the center of the valve body 13. When the shaft portion 11 is rotated by a driving force of a motor (not shown), the cylindrical valve body 13 rotates in the circumferential direction as indicated by an arc arrow in the drawing.
  • the valve body 13 rotates in the circumferential direction by the rotation of the shaft portion 11, so that the first flow path 131 communicates the first inlet / outlet P ⁇ b> 1 and the second inlet / outlet P ⁇ b> 2, or the second flow path 132 is the second inlet / outlet P ⁇ b> 2.
  • 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 arranged 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 outlet P3, and the second It flows out from the 2nd entrance / exit P2 through the flow path 132, and flows in into the 2nd outdoor unit heat exchanger 3b from the 3rd connection port C3.
  • the outdoor unit heat exchanger 3 is used as an evaporator (during heating operation)
  • 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 arranged such 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 from the 1st entrance / exit P1 through the flow path 131, and flows in into the four-way valve 2 shown in FIG.
  • the refrigerant flowing into the second flow path 132 from the fourth inlet / outlet P4 flows out of the third inlet / outlet P3 through the second flow path 132, and flows into the first outdoor unit heat exchanger 3a from the second connection port C2.
  • the performance of the heat exchanger can be improved as in the first embodiment. Therefore, it is possible to provide a heat exchanger capable of improving performance and reducing the size, and a refrigeration cycle apparatus including 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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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

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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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WO2021250738A1 (fr) * 2020-06-08 2021-12-16 三菱電機株式会社 Climatiseur

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EP3517855A1 (fr) 2019-07-31
EP3517855B1 (fr) 2020-09-16
JPWO2018055740A1 (ja) 2019-06-24
EP3517855A4 (fr) 2019-10-09
WO2018055740A9 (fr) 2019-02-21
JP6671491B2 (ja) 2020-03-25

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