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WO2018138770A1 - Unité côté source de chaleur et dispositif à cycle de réfrigération - Google Patents

Unité côté source de chaleur et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2018138770A1
WO2018138770A1 PCT/JP2017/002311 JP2017002311W WO2018138770A1 WO 2018138770 A1 WO2018138770 A1 WO 2018138770A1 JP 2017002311 W JP2017002311 W JP 2017002311W WO 2018138770 A1 WO2018138770 A1 WO 2018138770A1
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WO
WIPO (PCT)
Prior art keywords
heat
header
refrigerant
heat exchanger
source side
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2017/002311
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English (en)
Japanese (ja)
Inventor
加藤　央平
翼 丹田
将広 高村
雄大 坂部
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to US16/344,165 priority Critical patent/US20200072517A1/en
Priority to PCT/JP2017/002311 priority patent/WO2018138770A1/fr
Priority to JP2018563964A priority patent/JPWO2018138770A1/ja
Priority to EP17894243.9A priority patent/EP3575730A4/fr
Priority to CN201780079609.4A priority patent/CN110177988A/zh
Publication of WO2018138770A1 publication Critical patent/WO2018138770A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0452—Combination of units extending one behind the other with units extending one beside or one above the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0243—Header boxes having a circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates

Definitions

  • the present invention relates to a heat source side unit on which a heat exchanger including a header is mounted, and a refrigeration cycle apparatus including the heat source side unit.
  • a heat exchanger is mounted on a heat source side unit provided in a refrigeration cycle apparatus such as an air conditioner or a water heater.
  • a heat exchanger has a flow path (path) in which a plurality of heat transfer tubes are arranged in parallel in order to reduce the pressure loss of refrigerant flowing in the heat transfer tubes. Headers corresponding to the number of passes are provided at the refrigerant inlet and the refrigerant outlet of each heat transfer tube. Some headers are provided with a temperature sensor for measuring the temperature of the refrigerant flowing through the heat transfer tubes.
  • a heat exchanger for example, “an arrangement between two standing header collecting pipes (51, 52) and the two header collecting pipes (51, 52) in the vertical direction, one end of which is A plurality of flat tubes (53) inserted into one header collecting pipe (51, 52) and the other end inserted into the other header collecting pipe (51, 52), and joined to the flat tube (53)
  • a heat exchanger comprising a plurality of fins (55), a temperature sensor (100) for measuring the temperature of the refrigerant in the header collecting pipe (51, 52), and the header collecting pipe (51, 52)
  • the fixing member (110) for fixing the temperature sensor (100) to the header collecting pipe (51, 52) and the outer peripheral face of the header collecting pipe (51, 52)
  • the temperature sensor in the header collecting pipe is positioned by attaching a positioning member to the temperature sensor mounting position.
  • the temperature sensor can be positioned before brazing and the positioning workability can be improved compared to the case where the temperature sensor is positioned after brazing the header collecting pipe and the flat pipe. become.
  • Patent Document 1 the fixing position of the temperature sensor on the outer peripheral surface of the header collecting pipe is positioned by a positioning member, and no consideration is given to the state of the refrigerant flowing through the header collecting pipe. Therefore, when the number of heat transfer tubes is small and a temperature sensor is provided at the inlet of the subcool line, the temperature of the two-phase refrigerant cannot be measured.
  • the present invention has been made against the background of the above problems, and a heat source side unit that improves the reliability of temperature measurement of a gas-liquid two-phase refrigerant, and a refrigeration cycle including the heat source side unit
  • An object is to provide an apparatus.
  • a heat source side unit is a heat source side unit equipped with a heat exchanger having a plurality of heat exchange units and a temperature sensor for measuring the temperature of a refrigerant flowing through the heat exchanger, wherein the heat exchanger Is connected to a first heat exchange part that is at least one of the plurality of heat exchange parts, and includes a first header having a plurality of branch parts arranged in the vertical direction, and among the plurality of heat exchange parts Of the second header connected to the second heat exchange part which is at least the remaining one of the above, a part of the heat transfer pipe constituting the first heat exchange part, and the heat transfer pipe constituting the second heat exchange part Between the rows, the temperature sensor is located above a middle position in the vertical direction of the heat exchanger among the row connection members. It is installed on the connecting member.
  • the refrigeration cycle apparatus includes the above heat source side unit.
  • the temperature sensor is installed in the inter-row connecting member located above the intermediate position in the vertical direction of the heat exchanger among the inter-row connecting members. The certainty of temperature measurement is improved. Since the refrigeration cycle apparatus according to the present invention includes the above-described heat source unit, the control of each actuator can be optimized, and efficient system protection can be realized.
  • FIG. 6 is a schematic sectional view taken along line AA in FIG. 5.
  • the present invention is not limited to such a case.
  • the present invention may be applied to other refrigeration cycle apparatuses (for example, a water heater).
  • the refrigeration cycle apparatus can switch between the heating operation and the cooling operation
  • the invention is not limited to such a case, and only the heating operation or the cooling operation is performed. May be.
  • FIG. 1 and 2 are circuit configuration diagrams schematically showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100) according to an embodiment of the present invention.
  • the refrigeration cycle apparatus 100 will be described based on FIG.
  • an air conditioner will be described as an example of the refrigeration cycle apparatus 100. Therefore, the heating operation corresponds to the heating operation, and the cooling operation corresponds to the cooling operation.
  • coolant at the time of heating operation is shown
  • FIG. 2 the flow of the refrigerant
  • the refrigeration cycle apparatus 100 has a refrigerant circuit that circulates a refrigerant, and performs a cooling operation or a heating operation by circulating the refrigerant in the refrigerant circuit.
  • the refrigeration cycle apparatus 100 includes a heat source side unit 100A and a load side unit 100B.
  • the heat source side unit 100 ⁇ / b> A and the load side unit 100 ⁇ / b> B are connected to each other via a refrigerant circuit in which the elements mounted on them are connected by a refrigerant pipe 15.
  • Each element includes the compressor 10, the flow path switching device 11, the heat exchanger 50, the expansion device 12, and the load side heat exchanger 13.
  • the heat source side unit 100A is installed in a space different from the air-conditioning target space (for example, an outdoor space such as outdoors, an attic, or a basement), and has a function of supplying cold or warm energy to the load side unit 100B.
  • the heat source side unit 100A includes a compressor 10, a flow path switching device 11, a heat exchanger (heat source side heat exchanger) 50, an expansion device 12, a heat source side blower 50A, a control device 40, and a temperature sensor. 80 are mounted.
  • the compressor 10 compresses and discharges the refrigerant circulating in the refrigerant circuit.
  • the refrigerant compressed by the compressor 10 is discharged and sent to the heat exchanger 50 or the load side heat exchanger 13.
  • the compressor 10 can be composed of, for example, a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor, or the like.
  • the flow path switching device 11 is provided on the discharge side of the compressor 10 and switches the flow of refrigerant between the heating operation and the cooling operation. That is, the flow path switching device 11 is switched so as to connect the compressor 10 and the heat exchanger 50 during the cooling operation, and is switched so as to connect the compressor 10 and the load-side heat exchanger 13 during the heating operation. .
  • the flow path switching device 11 may be constituted by a four-way valve, for example. However, a combination of a two-way valve or a three-way valve may be employed as the flow path switching device 11.
  • the heat exchanger 50 functions as an evaporator during heating operation and functions as a condenser during cooling operation.
  • the heat exchanger 50 exchanges heat between the low-temperature and low-pressure refrigerant flowing out of the expansion device 12 and the air supplied by the heat source side blower 50A, and the low-temperature and low-pressure liquid refrigerant or Two-phase refrigerant evaporates.
  • the heat exchanger 50 functions as a condenser
  • the heat exchanger 50 exchanges heat between the high-temperature and high-pressure refrigerant discharged from the compressor 10 and the air supplied by the heat source side blower 50A, and the high-temperature and high-pressure gas.
  • the refrigerant condenses.
  • the heat exchanger 50 will be described in detail later.
  • the expansion device 12 expands and decompresses the refrigerant that has flowed out of the heat exchanger 50 or the load-side heat exchanger 13.
  • the expansion device 12 may be configured by an electric expansion valve that can adjust the flow rate of the refrigerant, for example.
  • an electric expansion valve that can adjust the flow rate of the refrigerant, for example.
  • the expansion device 12 not only an electric expansion valve but also a mechanical expansion valve employing a diaphragm for a pressure receiving portion, a capillary tube, or the like can be applied.
  • the heat source side blower 50A is attached to the heat exchanger 50 and supplies air to the heat exchanger 50 by rotating.
  • the heat source side blower 50A for example, any of various types of fans such as a propeller fan and a turbo fan can be used.
  • the condensation capacity or evaporation capacity of the heat exchanger 50 is adjusted by the rotation speed of the heat source side blower 50A.
  • the control device 40 controls the drive frequency of the compressor 10 according to the required cooling capacity or heating capacity. Moreover, the control apparatus 40 controls the opening degree of the expansion apparatus 12 according to the required cooling capacity or heating capacity. Moreover, the control apparatus 40 controls the rotation speed of the heat-source side fan 50A and the load side fan 13A. Furthermore, the control device 40 controls the switching of the flow path switching device 11 according to the operation mode.
  • control device 40 uses information sent from a temperature sensor 80 described later, other temperature sensors not shown, and pressure sensors not shown, based on an operation instruction from the user, Each actuator (the compressor 10, the flow path switching device 11, the expansion device 12, the heat source side blower 50A, and the load side blower 13A) is controlled.
  • Each actuator the compressor 10, the flow path switching device 11, the expansion device 12, the heat source side blower 50A, and the load side blower 13A
  • the control device 40 may be provided in the load side unit 100B, or may be provided outside the heat source side unit 100A and the load side unit 100B.
  • the control device 40 can be configured by hardware such as a circuit device that realizes the function, or can be configured by an arithmetic device such as a microcomputer or a CPU, and software executed thereon. it can.
  • the load-side unit 100B is installed in a space (for example, an air-conditioning target space such as an indoor space or a space communicating with the air-conditioning target space through a duct) that supplies cold or warm heat to the air-conditioning target space. It has a function of cooling or heating the air-conditioning target space by the cold or warm heat supplied from 100A.
  • a load side heat exchanger 13 and a load side blower 13A are mounted on the load side unit 100B.
  • the load side heat exchanger 13 functions as a condenser during heating operation and functions as an evaporator during cooling operation.
  • the load-side heat exchanger 13 exchanges heat between the high-temperature and high-pressure refrigerant discharged from the compressor 10 and the air supplied by the load-side blower 13A, thereby causing high-temperature and high-pressure.
  • the gas refrigerant condenses.
  • the load-side heat exchanger 13 functions as an evaporator
  • the load-side heat exchanger 13 exchanges heat between the low-temperature and low-pressure refrigerant flowing out from the expansion device 12 and the air supplied by the load-side fan 13A.
  • the low-temperature and low-pressure liquid refrigerant or two-phase refrigerant evaporates.
  • the load-side heat exchanger 13 is, for example, a fin-and-tube heat exchanger, a microchannel heat exchanger, a shell-and-tube heat exchanger, a heat pipe heat exchanger, a double pipe heat exchanger, a plate heat It can be composed of an exchanger or the like.
  • the load side heat exchanger 13 is a heat exchanger that performs heat exchange between air and refrigerant is shown as an example.
  • the condensing capacity or evaporating capacity of the load side heat exchanger 13 is adjusted by the rotation speed of the load side fan 13A.
  • the load side blower 13A is attached to the load side heat exchanger 13 and supplies air to the load side heat exchanger 13 by rotating.
  • the load-side blower 13A for example, any of various types of fans such as a propeller fan, a cross flow fan, a sirocco fan, and a turbo fan can be used.
  • FIG. 1 shows an example in which one load side unit 100B is connected to one heat source side unit 100A, but the number of heat source side units 100A and load side units 100B is particularly limited. Not what you want.
  • the refrigeration cycle apparatus 100 may be configured by providing a plurality of each unit and connecting each unit in parallel or in series. Further, the expansion device 12 may be mounted on the load side unit 100B.
  • refrigerant usable in refrigeration cycle apparatus 100 examples include a non-azeotropic refrigerant mixture, a pseudo-azeotropic refrigerant mixture, and a single refrigerant.
  • Non-azeotropic refrigerant mixture includes R407C (R32 / R125 / R134a) which is an HFC (hydrofluorocarbon) refrigerant. Since this non-azeotropic refrigerant mixture is a mixture of refrigerants having different boiling points, it has a characteristic that the composition ratio of the liquid-phase refrigerant and the gas-phase refrigerant is different. Examples of the pseudoazeotropic refrigerant mixture include R410A (R32 / R125) or R404A (R125 / R143a / R134a) which are HFC refrigerants. This pseudo azeotrope refrigerant has the same characteristic as that of the non-azeotrope refrigerant and has an operating pressure of about 1.6 times that of R22.
  • the single refrigerant includes R22, which is an HCFC (hydrochlorofluorocarbon) refrigerant, or R134a, which is an HFC refrigerant. Since this single refrigerant is not a mixture, it has the property of being easy to handle. In particular, it has been pointed out that HCFC refrigerants such as R22, which have been used in conventional refrigeration cycle apparatuses, have a higher ozone depletion coefficient than that of HFC refrigerants and have a large adverse environmental impact. From such a background, in recent years, the transition to a refrigerant having a small ozone depletion coefficient is progressing.
  • the refrigeration cycle apparatus 100 can perform a cooling operation or a heating operation in the load side unit 100B based on an instruction from the load side unit 100B.
  • the operation of each actuator is controlled by various sensors (a temperature sensor including the temperature sensor 80, a pressure sensor) and a control device 40 to which information sent from a remote controller is input.
  • the heat source side unit 100 ⁇ / b> A has a flow path so that the refrigerant discharged from the compressor 10 flows into the heat exchanger 50 via the load side heat exchanger 13.
  • the switching device 11 is switched. Specifically, in the heating operation mode, the refrigerant flows in the order of the compressor 10, the flow path switching device 11, the load side heat exchanger 13, the expansion device 12, and the heat exchanger 50.
  • the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and is discharged from the compressor 10 as a high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the load-side heat exchanger 13 via the flow path switching device 11.
  • the refrigerant that has flowed into the load-side heat exchanger 13 is heat-exchanged (condensed) with air supplied by the load-side fan 13A attached to the load-side heat exchanger 51, and becomes a high-temperature and high-pressure liquid refrigerant. It flows out from the side heat exchanger 13.
  • the air In the load-side heat exchanger 13, the air is heated by radiating heat from the refrigerant to the air, and the heated air is supplied to the air-conditioning target space, thereby heating the air-conditioning target space.
  • This refrigerant flows into the heat exchanger 50.
  • the refrigerant flowing into the heat exchanger 50 is heat-exchanged (evaporated) with the air supplied by the heat source side fan 50A attached to the heat exchanger 50, and becomes a low-temperature low-pressure gas refrigerant from the heat exchanger 50. leak.
  • the refrigerant that has flowed out of the heat exchanger 50 is again sucked into the compressor 10 via the flow path switching device 11. While the heating operation is continued, the cycle from the refrigerant discharge from the compressor 10 to the refrigerant suction to the compressor 10 is repeated.
  • the heat source side unit 100A has a flow path so that the refrigerant discharged from the compressor 10 flows into the load side heat exchanger 13 via the heat exchanger 50.
  • the switching device 11 is switched. Specifically, in the cooling operation, the refrigerant flows in the order of the compressor 10, the flow path switching device 11, the heat exchanger 50, the expansion device 12, and the load side heat exchanger 13.
  • the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and is discharged from the compressor 10 as a high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat exchanger 50 via the flow path switching device 11.
  • the refrigerant flowing into the heat exchanger 50 is heat-exchanged (condensed) with the air supplied by the heat source side fan 50A attached to the heat exchanger 50, and becomes a low-temperature high-pressure liquid refrigerant from the heat exchanger 50. leak.
  • the low-temperature and high-pressure liquid refrigerant that has flowed out of the heat exchanger 50 becomes a low-temperature and low-pressure liquid refrigerant (or a two-phase refrigerant) by the expansion device 12 and flows into the load-side heat exchanger 13.
  • the refrigerant flowing into the load-side heat exchanger 13 is heat-exchanged (evaporated) with the air supplied by the load-side fan 13A attached to the load-side heat exchanger 13, and becomes a low-temperature and low-pressure gas refrigerant. It flows out from the side heat exchanger 13.
  • the refrigerant absorbs heat from the air to cool the air, and the cooled air is supplied to the air conditioning target space, thereby cooling the air conditioning target space.
  • the refrigerant that has flowed out of the load side heat exchanger 13 is again sucked into the compressor 10 via the flow path switching device 11. While the cooling operation is continued, the cycle from the refrigerant discharge from the compressor 10 to the refrigerant suction to the compressor 10 is repeated.
  • FIG. 3 is a perspective view schematically showing an example of the heat exchanger 50 mounted on the heat source side unit 100A.
  • FIG. 4 is a perspective view schematically showing another example of the heat exchanger 50 mounted on the heat source side unit 100A.
  • the heat source unit 100A will be described in detail with reference to FIGS. 3 and 4 in addition to FIGS.
  • the heat exchanger 50 functioning as a heat source side heat exchanger is mounted on the heat source side unit 100A. Further, a temperature sensor 80 for measuring the temperature of the refrigerant flowing through the heat exchanger 50 is mounted on the heat source side unit 100A. The temperature information measured by the temperature sensor 80 is sent to the control device 40 and used for controlling each actuator.
  • the heat exchanger 50 includes a first heat exchange unit 51A disposed on the windward side in the passage direction of air passing therethrough (a white arrow in the figure), a second heat exchange unit 51B disposed on the leeward side, It has the 1st header 60 connected to the 1st heat exchange part 51A, and the 2nd header 70 connected to the 2nd heat exchange part 51B.
  • the first heat exchange unit 51A and the second heat exchange unit 51B may be collectively referred to as a heat exchange unit.
  • the first header 60 and the second header 70 may be collectively referred to as a header portion.
  • the 1st header 60 and the 2nd header 70 are along the passage direction (the white arrow in a figure) of the air which passes the heat exchanger 50 similarly to 51 A of 1st heat exchange parts, and the 2nd heat exchange part 51B. , Arranged side by side.
  • the heat exchanger 50 showed the example comprised by 2 rows of 51 A of 1st heat exchange parts, and the 2nd heat exchange part 51B, you may be comprised by 3 or more rows. In this case, what is necessary is just to add the heat exchange part provided with the structure equivalent to either the 1st heat exchange part 51A or the 2nd heat exchange part 51B.
  • the first heat exchange unit 51A includes a plurality of heat transfer tubes 52A and a plurality of fins 53A joined to the plurality of heat transfer tubes 52A, for example, by brazing.
  • the heat transfer tube 52A is, for example, a flat tube, and a plurality of flow paths are formed inside.
  • the heat transfer tubes 52A are arranged in a plurality of stages in a direction intersecting with the passing direction of air passing therethrough (the white arrow in the figure).
  • One end and the other end of each of the plurality of heat transfer tubes 52 ⁇ / b> A are arranged in parallel on the first header 60 side so as to face the first header 60.
  • each of the plurality of heat transfer tubes 52A is connected between one end and the other end by a hairpin portion 54A that is bent into a hairpin shape.
  • the second heat exchange unit 51B includes a plurality of heat transfer tubes 52B and a plurality of fins 53B joined to the plurality of heat transfer tubes 52B, for example, by brazing.
  • the heat transfer tube 52B is, for example, a flat tube, and a plurality of flow paths are formed inside.
  • the heat transfer tubes 52B are arranged in a plurality of stages in a direction intersecting with the passing direction of air passing therethrough (the white arrow in the figure).
  • One end and the other end of each of the plurality of heat transfer tubes 52 ⁇ / b> B are arranged in parallel on the second header 70 side so as to face the second header 70.
  • each of the plurality of heat transfer tubes 52B is connected between one end and the other end by a hairpin portion 54B that is bent into a hairpin shape.
  • the heat transfer tubes 52A and the heat transfer tubes 52B are not limited to flat tubes, and may be circular tubes. Moreover, although the heat-transfer tube 52A and the heat-transfer tube 52B showed the example which has the hairpin part 54A and the hairpin part 54B which were bend
  • the flow path may be folded using a U-shaped tube having a flow path formed therein as a separate member from 52B.
  • the 1st header 60 functions as a liquid header, and is comprised by the 2 or more branch part arranged in the vertical direction.
  • positioned in the vertical direction upper stage among two or more branch parts is shown in figure as the upper stage branch part 60a, and the branch part arrange
  • Each of the upper branch portion 60a and the lower branch portion 60b is connected to the number of heat transfer tubes 52A corresponding to the number of distributions.
  • the vertical direction means the vertical direction in a state where the heat exchanger 50 is mounted on the heat source side unit 100A.
  • the head difference between the paths due to the pressure loss of the heat transfer tube 52A is alleviated, and the difference in the refrigerant flow rate is reduced. The reason will be described in detail later.
  • the refrigerant pipe 15a is connected to the upper branch part 60a via the connection pipe 61a.
  • coolant piping 15b is connected to the lower branch part 60b via the connection piping 61b.
  • the refrigerant pipe 15 a and the refrigerant pipe 15 b are connected to the refrigerant pipe 15 via a distributor (distributor) 85.
  • the connection pipe 61a and the connection pipe 61b are, for example, circular pipes.
  • At least one split flow channel 65a is formed in the upper branch 60a.
  • the distribution flow channel 65a is a distribution channel that distributes the refrigerant flowing from the refrigerant pipe 15a to the plurality of heat transfer tubes 52A of the first heat exchange unit 51A and flows out when the heat exchanger 50 acts as an evaporator. Become.
  • the split flow channel 65a joins the refrigerant flowing in from the plurality of heat transfer tubes 52A of the first heat exchange unit 51A to the refrigerant pipe 15a. It becomes the merging channel that flows out. That is, the plurality of heat transfer tubes 52A are connected to one side of the split flow passage 65a, and the refrigerant pipe 15a is connected to the other side.
  • At least one mixed flow channel 65b is formed inside the lower branch 60b.
  • the distribution flow path 65b is a distribution flow path that distributes the refrigerant flowing from the refrigerant pipe 15b to the plurality of heat transfer tubes 52A of the first heat exchange section 51A and flows out when the heat exchanger 50 acts as an evaporator. Become.
  • the split flow channel 65b joins the refrigerant flowing in from the plurality of heat transfer tubes 52A of the first heat exchange unit 51A to the refrigerant pipe 15b. It becomes the merging channel that flows out. That is, the plurality of heat transfer tubes 52A are connected to one side of the mixed flow passage 65b, and the refrigerant pipe 15b is connected to the other side.
  • the second header 70 functions as a gas header.
  • 3 and 4 show an example of the heat exchanger 50 in which one second header 70 is provided for the first header 60 composed of a plurality of branching devices. Note that the second header 70 may also be composed of a plurality of branch portions, like the first header 60.
  • connection pipe 71 is, for example, a circular pipe.
  • a mixed flow channel 75 is formed in the second header 70.
  • the split flow channel 75 distributes the refrigerant flowing from the refrigerant pipe 15 to the plurality of heat transfer tubes 52B of the second heat exchange section 51B and flows out. It becomes a distribution channel.
  • the split flow channel 75 joins the refrigerant flowing from the plurality of heat transfer tubes 52B of the second heat exchange section 51B and flows out to the refrigerant pipe 15 when the heat exchanger 50 acts as an evaporator. It becomes a road. That is, a plurality of heat transfer tubes 52 ⁇ / b> B are connected to one side of the mixed flow passage 75, and the refrigerant pipe 15 is connected to the other side.
  • the heat exchanger 50 acts as an evaporator, the first header 60 in which the distribution flow path (split / mix flow path 65a, split flow / flow path 65b) is formed, and the merge flow path (distribution) And a second header 70 in which a confluence channel 75) is formed.
  • the heat exchanger 50 acts as a condenser, the heat exchanger 50 and the second header 70 in which the distribution flow path (split flow path 75) is formed, and the merge flow path (split flow path 65a, split flow). It also has the 1st header 60 in which the flow path 65b) is formed separately.
  • the heat transfer tube 52A and the heat transfer tube 52B are made of, for example, aluminum.
  • the fins 53A and the fins 53B are made of, for example, aluminum.
  • the heat transfer tubes 4 and the fins 5 are joined by brazing, for example.
  • the number of the heat transfer tubes 52A and the heat transfer tubes 52B is not limited to the number shown in FIGS.
  • the number of fins 53A and fins 53B is not limited to the number shown in FIGS.
  • FIG. 5 is a top view schematically showing an example of the heat exchanger 50 mounted on the heat source side unit 100A.
  • FIG. 6 is a schematic cross-sectional view taken along line AA in FIG. Based on FIG.5 and FIG.6, the connection of a heat exchange part and a header part is demonstrated. In FIG. 5, the air flow is represented by white arrows.
  • a joint member 56 ⁇ / b> A is joined to the end 52 a on the first header 60 side of the heat transfer tube 52 ⁇ / b> A.
  • a flow path is formed inside the joint member 56A.
  • One end of the flow path has a shape along the outer peripheral surface of the heat transfer tube 52A, and the other end has a circular shape.
  • a joint member 56B is joined to the end 52b of the heat transfer tube 52B on the second header 70 side.
  • a flow path is formed inside the joint member 56B.
  • One end of the flow path has a shape along the outer peripheral surface of the heat transfer tube 52B, and the other end has a circular shape.
  • the joint member 56 ⁇ / b> A and the joint member 56 ⁇ / b> B are connected by the inter-row connecting member 57.
  • the inter-column connecting member 57 is, for example, a circular tube bent in an arc shape.
  • a connection pipe 62 of the first header 60 is connected to the joint member 56A joined to the end 52a of the heat transfer pipe 52A.
  • an upper branching unit 60 a constituting the first header 60 is illustrated.
  • the connection pipe 62 connected to the upper branch portion 60a is described as the connection pipe 62a.
  • a connection pipe 72 of the second header 70 is connected to the joint member 56B joined to the end 52b of the heat transfer pipe 52B.
  • the joint member 56A and the connection pipe 62 may be integrated. Further, the joint member 56B and the connection pipe 72 may be integrated. Further, the joint member 56A, the joint member 56B, and the inter-row connecting member 57 may be integrated. Furthermore, in FIG. 6, the inter-row connecting member 57 is illustrated as being connected with an inclination, but the inter-row connecting member 57 may be connected horizontally.
  • FIG. 7 is a schematic diagram illustrating the flow of refrigerant in the heat exchanger 50 mounted on the heat source side unit 100A.
  • FIG. 8 is a graph schematically showing the state transition of the refrigerant in the heat exchanger 50 mounted on the heat source side unit 100A. Based on FIG.7 and FIG.8, the flow of the refrigerant
  • the flow of the refrigerant when the heat exchanger 50 acts as a condenser is indicated by arrows as (1) to (5).
  • (1) to (5) shown in FIG. 8 correspond to (1) to (5) of FIG.
  • the air temperature in the heat exchanger 50 is shown with the broken line.
  • the refrigerant flowing through the refrigerant pipe 15 flows into the second header 70 and is divided into a plurality of distribution flow paths 75, and flows in from the respective end portions 52b of the plurality of heat transfer tubes 52B of the second heat exchange unit 51B (arrows). (1)).
  • the refrigerant at this time is in a gas state, similar to the state of the refrigerant discharged from the compressor 10 (FIG. 8 (1)).
  • the refrigerant that has flowed in from the end 52b flows toward the other end of the heat transfer tube 52B.
  • the refrigerant exchanges heat with the air supplied by the heat source side blower 50A.
  • the refrigerant at this time is in a superheated gas state (FIG. 8 (2)).
  • the refrigerant that has flowed to the other end of the heat transfer tube 52B flows into the heat transfer tube 52B located above itself through the hairpin portion 54B (arrow (2)).
  • the refrigerant flowing in from the other end flows toward the end 52b of the heat transfer tube 52B. Also at this time, the refrigerant exchanges heat with the air supplied by the heat source side blower 50A.
  • the refrigerant that has flowed to the end portion 52b of the heat transfer tube 52B moves to the first heat exchange portion 51A via the inter-row connecting member 57 (arrow (3)).
  • the refrigerant at this time is in a gas-liquid two-phase state (FIG. 8 (3)).
  • the refrigerant that has moved to the first heat exchange unit 51A flows in from the respective end portions 52a of the plurality of heat transfer tubes 52A of the first heat exchange unit 51A.
  • the refrigerant flowing in from the end 52a flows toward the other end of the heat transfer tube 52A. At this time, the refrigerant exchanges heat with the air supplied by the heat source side blower 50A.
  • the refrigerant that has flowed to the other end of the heat transfer tube 52A flows into the heat transfer tube 52A located below itself through the hairpin portion 54A (arrow (4)).
  • the refrigerant flowing in from the other end flows toward the end 52a of the heat transfer tube 52A.
  • the refrigerant exchanges heat with the air supplied by the heat source side blower 50A.
  • the refrigerant at this time is in a supercooled liquid state (FIG. 8 (2)).
  • the refrigerant that has flowed to the end 52a of the heat transfer tube 52A flows into the first header 60 (arrow (5)).
  • the refrigerant flowing into the first header 60 joins at the first header 60 and flows out from the heat exchanger 50.
  • the temperature sensor 80 is provided at the position shown in the upper part of FIG.
  • a refrigeration cycle apparatus is provided with a temperature sensor that measures the temperature of a refrigerant circulating in the refrigerant circuit and a pressure sensor that measures the pressure of the refrigerant circulating in the refrigerant circuit at a predetermined location of the refrigerant circuit. Is supposed to protect. That is, since each actuator is controlled based on temperature information and pressure information measured by each sensor, it is important to protect the system that the refrigerant state is reliably measured.
  • a temperature sensor may be provided at a location where the gas-liquid two-phase refrigerant flows instead of the pressure sensor, and the refrigerant pressure is converted from the refrigerant temperature in the two-phase state measured by the temperature sensor.
  • the refrigerant flowing through the heat exchanger changes state as a superheated gas state, a two-phase state, and a supercooled liquid state. Therefore, it is very important for the system to reliably measure the refrigerant temperature in the two-phase state. Therefore, it is necessary to install the temperature sensor at a position where the two-phase refrigerant can be reliably measured.
  • the temperature sensor 80 is installed at a position where the degree of supercooling is difficult to be attached. Specifically, as shown in FIG. 5, the temperature sensor 80 is installed on the upper part of the inter-row connecting member 57 located at the uppermost stage. If the temperature sensor 80 is installed at this position, the reliability of the temperature measurement of the refrigerant that is in a two-phase state in the heat exchanger 50 is improved.
  • the separation position between the upper branch portion 60 a and the lower branch portion 60 b corresponds to the intermediate position in the vertical direction of the heat exchanger 50. That is, the temperature sensor 80 may be installed on the inter-column connection member 57 connected to a position above the intermediate position in the height direction of the heat exchanger 50. However, as shown in FIG. 5, it is preferable to install a temperature sensor 80 above the inter-row connecting member 57 located at the uppermost stage. Note that the temperature sensor 80 may be installed not on the upper side of the inter-row connecting member 57 but on the lower side or the side portion of the inter-row connecting member 57.
  • FIG. 9 is a longitudinal cross-sectional view showing an example of the upper branching portion 60a constituting the first header 60 of the heat exchanger 50 mounted on the heat source side unit 100A.
  • FIG. 10 is a perspective view showing another example of the upper branching portion 60a constituting the first header 60 of the heat exchanger 50 mounted on the heat source unit 100A.
  • the thickness of the plate-like body is illustrated as being substantially uniform.
  • the cross section cut along the flow direction of the fluid is shown.
  • the upper branch part 60a is illustrated, the lower branch part 60b has the same configuration.
  • the first header 60 can be configured as a laminated header having a plate-like body 90.
  • the plate-like body 90 is formed by alternately laminating first plate-like members 91a to 91d serving as bare materials and second plate-like members 92a to 92d serving as clad materials. It is formed.
  • a first plate member 91a and a first plate member 91e are stacked on the outermost side of the plate body 90 in the stacking direction.
  • the first plate-like member 91a to the first plate-like member 91e may be collectively referred to as the first plate-like member 91.
  • the second plate-like member 92a to the second plate-like member 92d may be collectively referred to as the second plate-like member 92 in some cases.
  • the first plate member 91 is made of, for example, aluminum. A brazing material is not applied to the first plate-like member 91.
  • Each of the first plate-like members 91 is formed with a through-hole that becomes the mixed flow channel 65. The through hole penetrates the front and back of the first plate-like member 91. By laminating the first plate-like member 91 and the second plate-like member 92, the through hole formed in the first plate-like member 91 functions as a part of the split flow channel 65.
  • the second plate-like member 92 is made of, for example, aluminum and is formed thinner than the first plate-like member 91.
  • a brazing material is applied to at least the front and back surfaces of the second plate-shaped member 92.
  • Each of the second plate-like members 92 is formed with a through-hole that becomes the mixed flow channel 65. The through hole penetrates the front and back of the second plate-like member 92.
  • connection pipe 61a is connected to the through hole formed in the first plate-like member 91a.
  • a base or the like may be provided on the surface of the first plate-like member 91a on the refrigerant inflow side, and the connection pipe 61a may be connected via the base or the like, or may be formed on the first plate-like member 91a.
  • the inner peripheral surface of the through hole is shaped to fit with the outer peripheral surface of the connection pipe 61a, and the connection pipe 61a may be directly connected without using a base or the like.
  • connection pipe 62a is connected to the through hole formed in the first plate-like member 91e.
  • a base or the like may be provided on the surface of the first plate-like member 91e on the refrigerant inflow side, and the connection pipe 62a may be connected through the base or the like, and the first plate-like member 91e is formed on the first plate-like member 91e.
  • the inner peripheral surface of the through hole is shaped to fit with the outer peripheral surface of the connection pipe 62a, and the connection pipe 62a may be directly connected without using a base or the like.
  • the connection pipe 62a may be connected by inserting the connection pipe 62a so as to reach the through hole of the first plate-like member 91d.
  • the through holes formed in the first plate-like member 91a and the first plate-like member 91c are formed, for example, so as to penetrate in a channel cross section Z shape.
  • the channel cross section is a cross section obtained by cutting the channel in a direction orthogonal to the fluid flow.
  • the through-hole formed in the first plate-like member 91, the through-hole formed in the second plate-like member 92 Communicate with each other to form a diverging flow channel 65. That is, when the first plate-shaped member 91 and the second plate-shaped member 92 are laminated, the adjacent through holes communicate with each other, and the portions other than the communicating through holes are adjacent to each other. The two-plate-shaped member 92 is closed, and the split flow channel 65 is formed.
  • the distribution flow path 65 has four fluid outlet parts with respect to one fluid inlet part is illustrated as an example, the number of branches is limited to four branches is not.
  • the flow of the refrigerant in the upper branch portion 60a when the refrigerant flows in from the connection pipe 61a will be described.
  • the refrigerant that has flowed through the connection pipe 61a flows into the upper branch 60a using the through hole of the first plate-like member 91a as a fluid inlet.
  • This refrigerant flows into the through hole of the second plate member 92a.
  • the refrigerant that has flowed into the through hole of the second plate member 92a flows into the center of the through hole of the first plate member 91b.
  • the refrigerant that has flowed into the center of the through hole of the first plate-like member 91b branches against the surface of the second plate-like member 92d that is laminated adjacently and flows to the end of the through-hole of the first plate-like member 91b.
  • the refrigerant that has reached the end of the through hole of the first plate member 91b passes through the through hole of the second plate member 92b and flows into the center of the through hole of the first plate member 91c.
  • the refrigerant that has flown into the center of the through hole of the first plate-like member 91c branches against the surface of the second plate-like member 92c that is laminated adjacently, and flows to the end of the through-hole of the first plate-like member 91c.
  • the refrigerant that has reached the end of the through hole of the first plate member 91c passes through the through hole of the second plate member 92c and flows into the through hole of the first plate member 91d.
  • the refrigerant flowing into the through hole of the first plate-like member 91d passes through the through-hole of the second plate-like member 92d and enters the heat transfer tube 52A via the connection pipe 62a located in the through-hole of the first plate-like member 91e. Inflow.
  • the uniformity of refrigerant distribution in the first header 60 is improved.
  • 9 shows an example in which the first header 60 is configured as a stacked header, the first header 60 may be configured as a cylindrical header as shown in FIG.
  • FIG. 11 is a perspective view showing an example of the configuration of the first header 60 of the heat exchanger 50 mounted on the heat source side unit 100A.
  • FIG. 12 is a perspective view showing another example of the configuration of the first header 60 of the heat exchanger 50 mounted on the heat source side unit 100A.
  • the first header 60 can be configured by separating the upper branch portion 60a and the lower branch portion 60b.
  • each of the upper branch portion 60a and the lower branch portion 60b may be configured as a stacked header, and the first header 60 may be configured as a cylindrical header.
  • the first header 60 may be configured with one being a stacked header and the other being a cylindrical header.
  • the entire first header 60 may be integrally formed, a partition portion 69 may be provided therein, and an upper branch portion 60a and a lower branch portion 60b may be formed.
  • a plurality of fluid inlet portions may be formed in the plate-like body 90, and the mixed flow passage 65 from each fluid inlet portion to the fluid outlet portion may not be communicated.
  • the internal space may be divided into a plurality of parts by the partition 69 as shown in FIG.
  • FIG. 13 is a graph for explaining the pressure loss of a header not having a plurality of branch portions.
  • FIG. 14 is a graph for explaining the pressure loss of a header having a plurality of branch portions.
  • FIG. 15 is a perspective view schematically showing still another example of the heat exchanger 50 mounted on the heat source side unit 100A.
  • FIG. 16 is a table for explaining combinations of heat transfer tubes and header channels. The operation of the header having a plurality of branch portions will be described with reference to FIGS.
  • the vertical axis represents pressure
  • the horizontal axis represents temperature
  • “A” indicates a subcool line inlet
  • “B” indicates a header inlet
  • “C” indicates a heat transfer tube inlet
  • “D” indicates a heat transfer tube outlet.
  • the upper stage represents the cross-sectional shape of the heat transfer tube
  • the lower stage represents the header flow path.
  • the left side shows a combination of a circular pipe and a header flow path
  • the right side shows a combination of a flat pipe and a header flow path.
  • the refrigerant branched at the header is liquefied by exchanging heat with air, and the pressure loss of each path varies due to the liquid head of the liquefied refrigerant. Specifically, the refrigerant flows more easily in the upper path, and the flow rate of the refrigerant increases. However, the refrigerant hardly flows in the lower path. Therefore, in general, as shown in FIG. 15, in the heat exchanger acting as a condenser, a subcool is often provided on the downstream side of the heat transfer tube in order to improve the heat exchange performance.
  • the downstream heat transfer tube for attaching the subcool is referred to as a subcool line (subcool line 55 shown in FIG. 15).
  • the pipe connecting the header flow path and the heat transfer tube has a capillary or the like. I used a thin tube. For this reason, the hydraulic diameter is such that the heat transfer pipe> the distributor flow path, and it is difficult to be affected by the liquid head, and the flow rate difference between the upper and lower sides during cooling is small.
  • the header channel and the flat tube are connected by a joint member. Since the hydraulic diameter of flat tubes is generally as small as 1 mm or less, the hydraulic diameter becomes a heat transfer tube ⁇ distributor flow path, pressure loss in the header flow path is reduced, and it is easily affected by the liquid head. . That is, in the heat exchanger 50 as well, a configuration in which the header channel and the flat tube are connected by the joint member 56A can be adopted, so that it is required to cope with the pressure loss in the header channel.
  • the pressure loss of the refrigerant flow path in the header is large as shown in FIG. ⁇ P2), the refrigerant temperature at the inlet of the header becomes higher than the air temperature. That is, the amount of refrigerant that cannot be evaporated increases, resulting in poor heat exchange efficiency and a lot of waste.
  • a conventional heat exchanger as described in Patent Document 1 in order to use the lower stage as a subcool line, each path is connected using a thin tube to absorb a head difference by applying pressure loss. I am doing so. However, this increases the pressure loss of the refrigerant flow path in the header and does not improve the heat exchange efficiency.
  • the header has a plurality of branch portions like the heat exchanger 50 and the heat exchanger provided with the subcool line is operated as an evaporator
  • the refrigerant in the header is shown in FIG.
  • the pressure loss of the flow path is small ( ⁇ P2 shown in FIG. 14), and the refrigerant temperature at the inlet of the header is lower than the air temperature. That is, the refrigerant can be evaporated in the entire heat exchanger, and the heat exchange efficiency is improved.
  • the first header 60 of the heat exchanger 50 is configured by two or more branch portions arranged in the vertical direction (vertical direction). Therefore, in the heat source side unit 100A, the head difference between the paths due to the pressure loss of the heat transfer tube 52A in the first header 60 can be reduced, and the difference in the refrigerant flow rate of the entire heat transfer tube can be reduced. Therefore, according to the heat source side unit 100A, heat exchange can be performed in the entire heat exchanger 50, and the heat exchange efficiency is improved.
  • the heat source side unit 100A even when the distributor 85 as shown in FIG. 4 is used, the heat source side unit 100A is branched according to the number of branch portions constituting the first header 60. An increase in the size of the main body and an increase in the number of pipes connected to the distributor 85 can be suppressed. Therefore, it is not necessary to make the internal space of the heat source unit 100A larger than necessary, and the space can be used effectively.
  • the heat source unit 100A measures the temperature of the heat exchanger 50 including a plurality of heat exchange units (the first heat exchange unit 51A and the second heat exchange unit 51B) and the refrigerant flowing through the heat exchanger 50.
  • Temperature exchanger 80 is mounted, and heat exchanger 50 is connected to first heat exchanging portion 51A, which is at least one of the plural heat exchanging portions, and has a plurality of branch portions (upper branch) arranged in the vertical direction.
  • the inter-row connecting member 57 that connects a part of the heat transfer tube 52A constituting the heat exchange part 51A and a part of the heat transfer pipe 52B constituting the second heat exchange part 51B, and the temperature sensor 80 , Of the inter-column connecting member 57 above the heat exchanger 50 It is installed in the column between the connecting member 57 is positioned above the direction of the intermediate position.
  • the temperature of the gas-liquid two-phase refrigerant flowing through the inter-column connecting member 57 is measured, so that the accurate temperature of the two-phase refrigerant used for controlling each actuator of the refrigeration cycle apparatus 100 is measured. Can be measured and the system can be efficiently protected.
  • the temperature sensor 80 is installed in the inter-row connecting member 57 located at the uppermost stage among the inter-row connecting members 57, so that the supercooling degree is not easily attached.
  • the inter-row connecting member 57 can measure the refrigerant temperature. Therefore, the temperature measurement of the two-phase refrigerant is further ensured.
  • the heat source side unit 100A is provided with a hairpin portion 54A at the end opposite to the end on the first header 60 side of the heat transfer tube 52A constituting the first heat exchanging portion 51A, and the second heat exchanging portion A hairpin portion 54B is provided at the end opposite to the end on the second header 70 side of the heat transfer tube 52B constituting the 51B, and the inter-row connecting member 57 is on the first header 60 side and the second header 70 side. Is provided. Therefore, according to the heat source side unit 100A, the temperature sensor 80 can be installed in the inter-row connecting member 57 without adopting a complicated configuration.
  • the first header 60 is a stacked header in which a plurality of plate-like members (first plate-like member 91 and second plate-like member 92) are laminated, so Uniformity is improved.
  • the heat transfer tubes are flat tubes, the heat exchange efficiency in the heat exchange section is improved.
  • the heat source side blower 50A that supplies air to the heat exchanger 50 is provided, and the first heat exchange unit 51A and the second heat exchange unit 51B are air supplied by the heat source side blower 50A. Therefore, the heat exchanger 50 does not increase in size.
  • the refrigeration cycle apparatus 100 since the heat source side unit 100A and the load side unit 100B connected to the heat source side unit 100A are provided, all the effects of the heat source side unit 100A are exhibited. . That is, according to the refrigeration cycle apparatus 100, the reliability of the temperature measurement of the gas-liquid two-phase refrigerant is improved, so that the control of each actuator is optimized and efficient system protection is realized.
  • Heat transfer tubes 5 fins, 10 compressors, 11 flow switching devices, 12 throttle devices, 13 load side heat exchangers, 13A load side blowers, 15 refrigerant piping, 15a refrigerant piping, 15b refrigerant piping, 40 control device, 50 Heat exchanger, 50A heat source side blower, 51 load side heat exchanger, 51A first heat exchange unit, 51B second heat exchange unit, 52A heat transfer tube, 52B heat transfer tube, 52a end, 52b end, 53A fin, 53B Fin, 54A hairpin part, 54B hairpin part, 55 subcool line, 56A joint member, 56B joint member, 57 inter-row connection member, 60 first header, 60a upper branch part, 60b lower branch part, 60c middle branch part, 61a connection Piping, 61b connecting piping, 62 connecting piping, 62a connecting piping, 6 Split flow channel, 65a Split flow channel, 65b Split flow channel, 69 partition, 70 second header, 71 connection pipe, 72 connection pipe, 75 split flow path, 80 temperature sensor

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

L'invention concerne une unité côté source de chaleur qui est installée dans un élément de connexion entre colonnes dans lequel un capteur de température est positionné plus haut qu'une position intermédiaire dans une direction verticale d'un échangeur de chaleur, parmi des éléments de connexion entre colonnes.
PCT/JP2017/002311 2017-01-24 2017-01-24 Unité côté source de chaleur et dispositif à cycle de réfrigération Ceased WO2018138770A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US16/344,165 US20200072517A1 (en) 2017-01-24 2017-01-24 Heat source-side unit and refrigeration cycle apparatus
PCT/JP2017/002311 WO2018138770A1 (fr) 2017-01-24 2017-01-24 Unité côté source de chaleur et dispositif à cycle de réfrigération
JP2018563964A JPWO2018138770A1 (ja) 2017-01-24 2017-01-24 熱源側ユニット、及び、冷凍サイクル装置
EP17894243.9A EP3575730A4 (fr) 2017-01-24 2017-01-24 Unité côté source de chaleur et dispositif à cycle de réfrigération
CN201780079609.4A CN110177988A (zh) 2017-01-24 2017-01-24 热源侧单元以及制冷循环装置

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PCT/JP2017/002311 WO2018138770A1 (fr) 2017-01-24 2017-01-24 Unité côté source de chaleur et dispositif à cycle de réfrigération

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WO2024236766A1 (fr) * 2023-05-17 2024-11-21 三菱電機株式会社 Distributeur de fluide frigorigène et climatiseur équipé d'un distributeur de fluide frigorigène
JP7633573B1 (ja) 2023-09-25 2025-02-20 ダイキン工業株式会社 熱交換器ユニット、空調室内機、冷凍サイクル装置、熱交換器ユニットの製造方法
JP2025060388A (ja) * 2023-09-29 2025-04-10 ダイキン工業株式会社 熱交換器および空気調和装置

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CN111189339B (zh) * 2020-01-22 2023-05-05 航天海鹰(哈尔滨)钛业有限公司 一种拼接式微通道换热器
US20250020420A1 (en) * 2022-02-02 2025-01-16 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
US20230304749A1 (en) * 2022-03-23 2023-09-28 Carrier Corporation Fluid distributor for a microchannel heat exchanger

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JP2020076537A (ja) * 2018-11-07 2020-05-21 ダイキン工業株式会社 熱交換器及び熱交換器の製造方法
JP7335690B2 (ja) 2018-11-07 2023-08-30 ダイキン工業株式会社 熱交換器及び熱交換器の製造方法
WO2024236766A1 (fr) * 2023-05-17 2024-11-21 三菱電機株式会社 Distributeur de fluide frigorigène et climatiseur équipé d'un distributeur de fluide frigorigène
JP7633573B1 (ja) 2023-09-25 2025-02-20 ダイキン工業株式会社 熱交換器ユニット、空調室内機、冷凍サイクル装置、熱交換器ユニットの製造方法
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JP2025060388A (ja) * 2023-09-29 2025-04-10 ダイキン工業株式会社 熱交換器および空気調和装置
JP7701659B2 (ja) 2023-09-29 2025-07-02 ダイキン工業株式会社 熱交換器および空気調和装置

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EP3575730A1 (fr) 2019-12-04
EP3575730A4 (fr) 2020-01-15
US20200072517A1 (en) 2020-03-05
CN110177988A (zh) 2019-08-27
JPWO2018138770A1 (ja) 2019-11-07

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