WO2021245877A1 - 熱交換器および冷凍サイクル装置 - Google Patents

熱交換器および冷凍サイクル装置 Download PDF

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Publication number
WO2021245877A1
WO2021245877A1 PCT/JP2020/022105 JP2020022105W WO2021245877A1 WO 2021245877 A1 WO2021245877 A1 WO 2021245877A1 JP 2020022105 W JP2020022105 W JP 2020022105W WO 2021245877 A1 WO2021245877 A1 WO 2021245877A1
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WIPO (PCT)
Prior art keywords
heat exchange
exchange section
refrigerant
heat
heat exchanger
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/JP2020/022105
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English (en)
French (fr)
Japanese (ja)
Inventor
篤史 ▲高▼橋
剛志 前田
悟 梁池
敦 森田
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 US17/916,325 priority Critical patent/US20230194180A1/en
Priority to CN202080101449.0A priority patent/CN115917243A/zh
Priority to PCT/JP2020/022105 priority patent/WO2021245877A1/ja
Priority to EP20938547.5A priority patent/EP4163580A4/en
Priority to JP2022529249A priority patent/JP7399286B2/ja
Publication of WO2021245877A1 publication Critical patent/WO2021245877A1/ja
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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1607—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • 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
    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators

Definitions

  • This technology is related to heat exchangers and refrigeration cycle equipment.
  • it relates to a heat exchanger or the like that exchanges heat while distributing a refrigerant.
  • the gas refrigerant is biased to the upper side due to the inertial force. Therefore, the evaporator performance when the heat exchanger operates as an evaporator tends to deteriorate. Therefore, in order not to deteriorate the performance of the evaporator, when the heat exchanger operates as an evaporator, the flow direction of the refrigerant and the ventilation direction are opposed to each other in the section of the heat exchanger having a large number of stages in the heat exchanger. Make it a countercurrent flow. On the other hand, when the heat exchanger operates as a condenser, the flow of the refrigerant in the heat exchanger is opposite to that when it operates as an evaporator.
  • the heat exchanger when the heat exchanger operates as a condenser, it becomes a parallel flow in which the flow direction of the refrigerant and the ventilation direction flow in parallel.
  • parallel flow the temperature difference between the refrigerant and air cannot be secured as compared with the case of counter flow, so that the condensation performance is slowed down.
  • the purpose is to obtain a heat exchanger and a refrigeration cycle device that can solve the above-mentioned problems and improve the heat exchange performance.
  • a plurality of heat transfer tubes through which the refrigerant flows in the pipes are arranged side by side in the height direction, and a heat exchange unit for heat exchange between the refrigerant and air is connected to one end of the plurality of heat transfer tubes.
  • the folded part for circulating the refrigerant between the heat exchange parts arranged in the two rows of the upwind row and the leeward row and the other end of the heat transfer tube in the heat exchange part of each row are connected and transferred.
  • the main heat exchange section in the leeward row flows and flows out in the order of the second auxiliary heat exchange section in the upwind row.
  • the refrigerating cycle apparatus has the above-mentioned heat exchanger at least in the condenser.
  • the flow of the refrigerant in the main heat exchanger and the flow of air passing through the heat exchanger are the upstream side of the refrigerant in the main heat exchanger and the air.
  • the downstream side exchanges heat, and the downstream side of the refrigerant in the main heat exchange section and the upstream side of the air exchange heat, so that the flows face each other. Therefore, heat exchange can be performed while maintaining a temperature difference at which heat exchange can be effectively performed between the refrigerant and air over the entire refrigerant flow path of the heat exchanger, and the heat transfer performance of the heat exchanger can be improved. Can be improved.
  • FIG. It is a figure which shows the structure of the air conditioner which concerns on Embodiment 1.
  • FIG. It is a figure which shows the outline of the structure of the heat exchanger 1 which concerns on Embodiment 1.
  • FIG. It is a figure explaining each part of the heat exchange part 10 in the heat exchanger 1 which concerns on Embodiment 1.
  • FIG. It is a figure which shows the outline of the temperature change of the air and the refrigerant in the heat exchanger 1 when the heat exchanger 1 which concerns on Embodiment 1 functions as a condenser.
  • FIG. 1 It is a figure which shows the outline of the temperature change of the air and the refrigerant in the heat exchanger 1 when the heat exchanger 1 which concerns on Embodiment 2 functions as an evaporator. It is a figure explaining the distribution of the flat heat transfer tube 14 in the heat exchanger 1 which concerns on Embodiment 3.
  • FIG. It is a figure which shows the outline of the structure of the heat exchanger 1 which concerns on Embodiment 4.
  • FIG. It is a figure which shows an example of the structure of the laminated distributor 17 which concerns on Embodiment 4.
  • the upper part in the figure will be referred to as “upper” and the lower part will be referred to as “lower”.
  • the high and low pressure and temperature are not fixed in relation to the absolute values, but are relatively fixed in terms of the state and operation of the device and the like.
  • the subscripts and the like may be omitted.
  • FIG. 1 is a diagram showing a configuration of an air conditioner according to the first embodiment.
  • an air conditioner will be described as an example of a refrigeration cycle device having the heat exchanger of the first embodiment.
  • the air conditioner of the first embodiment includes an outdoor unit 200, an indoor unit 100, and two refrigerant pipes 300. Then, the compressor 210, the four-way valve 220 and the outdoor heat exchanger 230 of the outdoor unit 200, and the indoor heat exchanger 110 and the expansion valve 120 of the indoor unit 100 are connected by a refrigerant pipe 300 to form a refrigerant circuit. ..
  • a refrigerant pipe 300 to form a refrigerant circuit.
  • the air conditioner of the first embodiment it is assumed that one outdoor unit 200 and one indoor unit 100 are connected by piping. However, the number of connected devices is not limited to this.
  • the indoor unit 100 has an indoor blower 130 in addition to the indoor heat exchanger 110 and the expansion valve 120.
  • the expansion valve 120 of the throttle device or the like decompresses and expands the refrigerant.
  • the expansion valve 120 is composed of, for example, an electronic expansion valve, the opening degree is adjusted based on an instruction from a control device (not shown) or the like.
  • the indoor heat exchanger 110 exchanges heat between the air in the room, which is the space to be air-conditioned, and the refrigerant.
  • the indoor heat exchanger 110 functions as a condenser to condense and liquefy the refrigerant.
  • the indoor heat exchanger 110 functions as an evaporator to evaporate and vaporize the refrigerant.
  • the indoor blower 130 passes indoor air through the indoor heat exchanger 110, and supplies the air that has passed through the indoor heat exchanger 110 into the room.
  • the outdoor unit 200 of the first embodiment has a compressor 210, a four-way valve 220, an outdoor heat exchanger 230, and an accumulator 240 as equipment constituting the refrigerant circuit. Further, the outdoor unit 200 has an outdoor blower 250.
  • the compressor 210 compresses and discharges the sucked refrigerant.
  • the compressor 210 is, for example, a scroll type compressor, a reciprocating type compressor, a vane type compressor, or the like. Further, although not particularly limited, the compressor 210 can change the capacity of the compressor 210 by arbitrarily changing the operating frequency by, for example, an inverter circuit or the like.
  • the four-way valve 220 which serves as a flow path switching device, is a valve that switches the flow of the refrigerant between the cooling operation and the heating operation, for example.
  • the four-way valve 220 connects the discharge side of the compressor 210 to the indoor heat exchanger 110 and the suction side of the compressor 210 to the outdoor heat exchanger 230 when the heating operation is performed. Further, the four-way valve 220 connects the discharge side of the compressor 210 to the outdoor heat exchanger 230 and the suction side of the compressor 210 to the indoor heat exchanger 110 when the cooling operation is performed.
  • the flow path switching device is not limited to this.
  • a plurality of two-way valves may be combined to form a flow path switching device.
  • the accumulator 240 is installed on the suction side of the compressor 210.
  • the accumulator 240 passes a gaseous refrigerant (hereinafter referred to as a gas refrigerant) and stores a liquid refrigerant (hereinafter referred to as a liquid refrigerant).
  • the outdoor heat exchanger 230 exchanges heat between the refrigerant and the outdoor air.
  • the refrigerant is a fluid that serves as a heat exchange medium.
  • the outdoor heat exchanger 230 of the first embodiment functions as an evaporator during the heating operation, and evaporates and vaporizes the refrigerant.
  • the outdoor heat exchanger 230 of the first embodiment functions as a condenser and a supercooler to condense and liquefy the refrigerant to perform supercooling.
  • the outdoor heat exchanger 230 of the first embodiment has a heat exchanger 1 including a heat exchange unit 10 as a heat exchange portion, as will be described later. The details of the heat exchanger 1 will be described later.
  • the outdoor blower 250 is driven to pass air from the outside of the outdoor unit 200 to the outdoor heat exchanger 230 to form a flow of air flowing out from the inside of the outdoor unit 200.
  • the condensed and liquefied refrigerant passes through the expansion valve 120.
  • the refrigerant is depressurized as it passes through the expansion valve 120.
  • the refrigerant that has been decompressed by the expansion valve 120 and is in a gas-liquid two-phase state passes through the outdoor heat exchanger 230.
  • the refrigerant that evaporates and gasifies by exchanging heat with the outdoor air sent from the outdoor blower 250 passes through the four-way valve 220 and the accumulator 240 and is sucked into the compressor 210 again. Will be done.
  • the refrigerant of the air conditioner circulates to perform air conditioning related to heating.
  • the dotted line arrow in FIG. 1 indicates the flow of the refrigerant in the cooling operation.
  • the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 210 passes through the four-way valve 220 and flows into the outdoor heat exchanger 230. Then, the refrigerant passes through the outdoor heat exchanger 230 and is condensed and liquefied by exchanging heat with the outdoor air supplied by the outdoor blower 250.
  • the liquefied refrigerant passes through the expansion valve 120.
  • the pressure is reduced and the refrigerant is in a gas-liquid two-phase state.
  • the refrigerant that has been decompressed by the expansion valve 120 and is in a gas-liquid two-phase state passes through the indoor heat exchanger 110. Then, in the indoor heat exchanger 110, for example, the refrigerant that evaporates and gasifies by exchanging heat with the air in the air-conditioned space passes through the four-way valve 220 and is sucked into the compressor 210 again. As described above, the refrigerant of the air conditioner circulates to perform air conditioning related to cooling.
  • FIG. 2 is a diagram showing an outline of the configuration of the heat exchanger 1 according to the first embodiment.
  • FIG. 3 is a diagram illustrating each part of the heat exchange unit 10 in the heat exchanger 1 according to the first embodiment.
  • the outdoor heat exchanger 230 has the heat exchanger 1 according to the first embodiment.
  • the present invention is not limited to this, and the indoor heat exchanger 110 may have it.
  • the heat exchanger 1 is a corrugated fin tube type heat exchanger having a parallel piping type.
  • the heat exchanger 1 has two distribution headers 11 (distribution header 11A and distribution header 11B) serving as a distribution flow portion, a folding header 13 serving as a folding portion, a plurality of flat heat transfer tubes 14, and a plurality of corrugated fins 15.
  • the exchange unit 10 is provided.
  • the two distribution headers 11 and the folded header 13 are arranged separately on the left and right.
  • the wrapping header 13 is located on the right side, and the two distribution headers 11 are arranged on the left side of the wrapping header 13.
  • the positional relationship between the distribution header 11 and the wrapping header 13 may be reversed.
  • the vertical direction in FIGS. 2 and 3 is defined as the height direction.
  • the left-right direction in which the distribution header 11 and the wrapping header 13 are arranged is the horizontal direction.
  • the direction of the depth is the direction in which the air indicated by the dotted arrow in FIG. 2 flows by the outdoor blower 250.
  • a plurality of flat heat transfer tubes 14 are arranged side by side in the height direction.
  • a group of a plurality of flat heat transfer tubes 14 are arranged side by side in two rows in the depth direction which is the front-rear direction.
  • the group of flat heat transfer tubes 14 in one row is connected to one distribution header 11.
  • Each flat heat transfer tube 14 serves as a flow path for the refrigerant.
  • the manufacture of the heat exchanger 1 can be simplified.
  • the row on the leeward side upstream of the air passage direction in the heat exchanger 1 is referred to as the leeward row
  • the row on the leeward side downstream is referred to as the leeward row. do.
  • the flat heat transfer tubes 14 are arranged in two rows.
  • the distribution header 11 which is the equipment of the distribution / mixing flow unit, is connected to other devices constituting the refrigeration cycle device by piping, and the refrigerant, which is a fluid serving as a heat exchange medium, flows in and out, and the refrigerant is branched and distributed or merged. It is a pipe that serves as a refrigerant distributor.
  • the distribution header 11 has a cylindrical shape, but the shape is not particularly limited.
  • Each of the distribution headers 11 has a refrigerant inlet / outlet pipe 12 (refrigerant inlet / outlet pipe 12A and a refrigerant inlet / outlet pipe 12B) into which a refrigerant from the outside flows in and out.
  • the refrigerant flows in from the refrigerant inlet / outlet pipe 12A and flows out from the refrigerant inlet / outlet pipe 12B.
  • the heat exchanger 1 becomes an evaporator
  • the refrigerant flows in from the refrigerant inlet / outlet pipe 12B and flows out from the refrigerant inlet / outlet pipe 12A.
  • the inside of the distribution header 11 is partitioned by a plurality of partition plates (not shown) and is divided into a plurality of spaces. By dividing the inside of the distribution header 11 into a plurality of spaces, the heat exchanger 1 can be divided into a plurality of regions.
  • the region refers to a group of flat heat transfer tubes 14 in which the flow directions of the refrigerant in the flat heat transfer tubes 14 are the same.
  • the connection pipe 16 is a pipe that connects the spaces separated in the distribution header 11 from the outside.
  • the connection pipe 16 not only connects the spaces in the distribution header 11 on a one-to-one basis, but also branches one of the spaces to connect a plurality of spaces to one space in the distribution header 11. You can also do it.
  • the folded header 13 serves as a bridge for merging the refrigerant flowing in from the group of flat heat transfer tubes 14 in one row and branching out to the group of flat heat transfer tubes 14 in the other row. It is a header. Even inside the folded header 13, a partition plate (not shown) is installed at least at a position in the distribution header 11 that matches the position of the partition plate, and is divided into a plurality of spaces.
  • a partition plate may be installed inside the folded header 13 so as to correspond to each flat heat transfer tube 14.
  • the space between the main heat exchange unit 10A in the upwind row and the main heat exchange unit 10A in the leeward row which will be described later, may be divided into corresponding spaces on a one-to-one basis.
  • the refrigerant does not merge or branch in the folded header 13.
  • the flat heat transfer tube 14 in the heat exchange section 10 in the upwind row and the flat heat transfer tube 14 in the heat exchange section 10 in the downwind row are associated with each other on a one-to-one basis, the flat heat transfer tubes 14 are individually connected. It can also be connected with a pipe or the like.
  • the flat heat transfer tube 14 has a flat cross section, and the outer surface on the longitudinal side of the flat shape along the depth direction, which is the flow direction of air, is flat, and the outer surface on the lateral side orthogonal to the longitudinal direction is flat.
  • the flat heat transfer tube 14 of the first embodiment is a multi-hole flat heat transfer tube having a plurality of holes serving as a flow path for the refrigerant inside the tube.
  • the hole of the flat heat transfer tube 14 is formed so as to face the horizontal direction because it is a flow path between the distribution header 11 and the folded header 13.
  • the flat heat transfer tubes 14 are arranged at equal intervals in the height direction with the outer surfaces on the longitudinal side facing each other.
  • each flat heat transfer tube 14 is inserted into an insertion hole (not shown) of the distribution header 11 and the folded header 13 (not shown), brazed, and joined. ..
  • the brazing brazing material for example, a brazing material containing aluminum is used.
  • the distribution header 11, the folded header 13, and the inside of each flat heat transfer tube 14 communicate with each other.
  • corrugated fins 15 are arranged between the flat surfaces of the arranged flat heat transfer tubes 14 facing each other.
  • the corrugated fins 15 are arranged to increase the heat transfer area between the refrigerant and the outside air.
  • the corrugated fin 15 is corrugated on the plate material, and is bent into a wavy shape and a bellows by a zigzag fold that repeats mountain folds and valley folds.
  • the bent portion due to the unevenness formed in the wave shape becomes the top of the wave shape.
  • the tops of the corrugated fins 15 are aligned in the height direction. In the corrugated fin 15, the top of the corrugated shape and the flat surface of the flat heat transfer tube 14 are in surface contact with each other.
  • the contact portion is brazed and joined by a brazing material.
  • the plate material of the corrugated fin 15 is made of, for example, an aluminum alloy. Then, the surface of the plate material is covered with a brazing material layer.
  • the coated wax material layer is based on, for example, a brazing material containing aluminum-silicon-based aluminum.
  • the heat exchange unit 10 of the heat exchanger 1 in the first embodiment when the heat exchange unit 10 is used as a condenser, high temperature and high pressure refrigerant flows through the refrigerant flow path in the flat heat transfer tube 14.
  • the heat exchange unit 10 when the heat exchange unit 10 is used as an evaporator, low-temperature and low-pressure refrigerant flows through the refrigerant flow path in the flat heat transfer tube 14.
  • the flat heat transfer tubes 14 in the upwind row and the downwind row are the main heat exchange section 10A and the first auxiliary heat exchange section, respectively. It is divided into regions of 10B and a second auxiliary heat exchange unit 10C. The uppermost region is the main heat exchange unit 10A, and the first auxiliary heat exchange unit 10B and the second auxiliary heat exchange unit 10C are in this order toward the lower side.
  • the number of flat heat transfer tubes 14 that form a group in each region of the heat exchanger 1 of the first embodiment is such that the main heat exchange unit 10A> the first auxiliary heat exchange unit 10B ⁇ the second auxiliary heat exchange unit 10C. be.
  • FIG. 4 is a diagram showing an outline of temperature changes of air and refrigerant in the heat exchanger 1 when the heat exchanger 1 according to the first embodiment functions as a condenser.
  • the solid line indicates the temperature of the refrigerant
  • the dotted line indicates the temperature of the air (hereinafter, the same applies).
  • the arrow shown by the heat exchange unit 10 indicates the flow of the refrigerant in the heat exchange unit 10 when the heat exchanger 1 is a condenser.
  • the heat exchanger 1 is a condenser
  • the refrigerant flows from the refrigerant inlet / outlet pipe 12A into the distribution header 11A.
  • the refrigerant flowing into the distribution header 11A passes through the flat heat transfer tube 14 in the leeward row belonging to the main heat exchange section 10A in the leeward row.
  • the flat heat transfer tube 14 exchanges heat between the refrigerant passing through the tube and the outside air, which is the outside air passing outside the tube. At this time, the refrigerant dissipates heat to the outside air while passing through the flat heat transfer tube 14.
  • the heat exchanger 1 is a condenser
  • the refrigerant dissipates heat to the outside air while passing through the flat heat transfer tube 14, which is the same in any region.
  • the refrigerant is folded back at the folded header 13 and passes through the flat heat transfer tube 14 of the upwind row belonging to the main heat exchange portion 10A of the upwind row.
  • the refrigerant heat-exchanged through the flat heat transfer tube 14 in the upwind row flows into the distribution header 11B.
  • the refrigerant that has flowed into the distribution header 11B flows into another space of the distribution header 11B through the connection pipe 16. Then, it passes through the flat heat transfer tube 14 of the upwind row belonging to the first auxiliary heat exchange section 10B of the upwind row, is folded back by the folded header 13, and passes through the first auxiliary heat exchange section 10B of the leeward row. It flows into the distribution header 11A.
  • the refrigerant that has flowed into the distribution header 11A flows into another space of the distribution header 11A through the connection pipe 16. Then, it passes through the flat heat transfer tube 14 of the leeward row belonging to the second auxiliary heat exchange section 10C of the leeward row, is folded back by the folded header 13, passes through the second auxiliary heat exchange section 10C of the leeward row, and is distributed. It flows into the header 11B.
  • the refrigerant that has flowed and condensed in the above order flows out from the refrigerant inlet / outlet pipe 12B. Therefore, when the heat exchanger 1 of the first embodiment is a condenser, the flow of the refrigerant is countercurrent to the air flow in the main heat exchange unit 10A.
  • the countercurrent is a flow in which heat is exchanged between the refrigerant on the downstream side in the flow of the refrigerant, the air on the upstream side in the flow of air, the refrigerant on the upstream side in the flow of the refrigerant, and the air on the downstream side in the flow of air.
  • FIG. 5 is a diagram showing an outline of temperature changes of air and refrigerant in the heat exchanger 1 when the heat exchanger 1 according to the first embodiment functions as an evaporator.
  • the heat exchanger 1 When the heat exchanger 1 is an evaporator, the refrigerant flows from the refrigerant inlet / outlet pipe 12B into the distribution header 11B.
  • the refrigerant flowing into the distribution header 11B passes through the flat heat transfer tube 14 of the upwind row belonging to the second auxiliary heat exchange unit 10C of the upwind row.
  • the flat heat transfer tube 14 exchanges heat between the refrigerant passing through the tube and the outside air, which is the outside air passing outside the tube. At this time, the refrigerant absorbs heat from the outside air while passing through the flat heat transfer tube 14.
  • the heat exchanger 1 when the heat exchanger 1 is an evaporator, the refrigerant absorbs heat with respect to the outside air while passing through the flat heat transfer tube 14, which is the same in any region.
  • the refrigerant is folded back at the folded header 13 and passes through the flat heat transfer tube 14 in the leeward row belonging to the second auxiliary heat exchange section 10C in the leeward row.
  • the refrigerant that has passed through the flat heat transfer tube 14 in the leeward row and exchanged heat flows into the distribution header 11A.
  • the refrigerant that has flowed into the distribution header 11A flows into another space of the distribution header 11A through the connection pipe 16. Then, it passes through the flat heat transfer tube 14 of the leeward row belonging to the first auxiliary heat exchange section 10B of the leeward row, is folded back by the folded header 13, passes through the first auxiliary heat exchange section 10B of the leeward row, and is distributed. It flows into the header 11B.
  • the refrigerant that has flowed into the distribution header 11B flows into another space of the distribution header 11B through the connection pipe 16. Then, it passes through the flat heat transfer tube 14 of the upwind row belonging to the main heat exchange portion 10A of the upwind row, is folded back by the folded header 13, passes through the main heat exchange portion 10A of the leeward row, and reaches the distribution header 11A. Inflow.
  • the refrigerant that has flowed and evaporated in the above order flows out from the refrigerant inlet / outlet pipe 12A. Therefore, when the heat exchanger 1 of the first embodiment is an evaporator, the flow of the refrigerant is parallel to the air flow in the main heat exchange unit 10A.
  • the parallel flow is a flow in which heat is exchanged between the refrigerant on the upstream side in the flow of the refrigerant, the air on the upstream side in the flow of air, the refrigerant on the downstream side in the flow of the refrigerant, and the air on the downstream side in the flow of air.
  • the heat exchanger 1 When the heat exchanger 1 is an evaporator, the relationship between the air flow and the refrigerant flow in the main heat exchange unit 10A becomes a parallel flow. However, the refrigerant first passes through the second auxiliary heat exchange section 10C, which has a small number of flat heat transfer tubes 14 and a small flow path area, and then flows into the main heat exchange section 10A. Therefore, the temperature of the refrigerant drops at the stage of passing through the main heat exchange section 10A due to a pressure loss or the like. Therefore, the refrigerant passing through the main heat exchange unit 10A has a temperature difference capable of effectively exchanging heat with the air passing through the heat exchanger 1. As a result, the heat exchanger 1 can prevent the heat exchange performance as an evaporator from deteriorating and maintain the performance as an evaporator.
  • the flow of the refrigerant in the main heat exchanger 10A when the heat exchanger 1 becomes the condenser is such that the flow of air passing through the heat exchanger 1 and the flow of air are opposed to each other. Therefore, heat exchange can be performed while maintaining a temperature difference at which heat exchange can be effectively performed between the refrigerant and air over the entire refrigerant flow path of the heat exchanger 1, and heat transfer of the heat exchanger 1 can be performed. Performance can be improved.
  • the heat exchanger 1 becomes an evaporator
  • the flow of the refrigerant in the main heat exchange section 10A and the flow of air passing through the heat exchanger 1 become parallel flows, but in the second auxiliary heat exchange section 10C.
  • a pressure loss occurs in the refrigerant, and the cooled refrigerant flows into the main heat exchange section 10A. Therefore, the refrigerant passing through the main heat exchanger 10A has a temperature difference capable of effectively exchanging heat with the air passing through the heat exchanger 1, and the heat exchanger 1 serves as an evaporator. Performance can be maintained.
  • the air can pass through the flat heat transfer tubes 14 at the same interval. Further, by making the two rows of flat heat transfer tubes 14 have a one-to-one correspondence without merging and branching the refrigerant in the folded header 13, it is possible to prevent the refrigerant from being biased in the folded header 13.
  • FIG. 6 is a diagram showing an outline of temperature changes of air and refrigerant in the heat exchanger 1 when the heat exchanger 1 according to the second embodiment functions as an evaporator.
  • the air conditioner and heat exchanger 1 of the second embodiment have the same configuration as the air conditioner and heat exchanger 1 described in the first embodiment.
  • the number of flat heat transfer tubes 14 that form a group in each region of the heat exchanger 1 of the second embodiment is particularly determined by the main heat exchange unit 10A> the first auxiliary heat exchange unit 10B> the second auxiliary heat exchange unit 10C. Suppose there is.
  • the refrigerant flows from the refrigerant inlet / outlet pipe 12B into the distribution header 11B, and is the second auxiliary heat exchange section 10C in the upwind row, which is a region located at the bottom of the heat exchanger 1. It passes through the flat heat transfer tube 14 of the upwind row belonging to.
  • a refrigerant having a temperature higher than the temperature of the air passing through the heat exchange section 10 of the upwind row flows into the second auxiliary heat exchange section 10C of the upwind row. As such, the refrigerant in the refrigerant circuit is circulated.
  • the refrigerant passing through the second auxiliary heat exchange section 10C in the upwind row located at the lowest stage has a temperature higher than the temperature of the air, so that it is outdoors.
  • the drain water collected in the lower part of the heat exchanger 1 which is the outdoor heat exchanger 230 of the machine 200 does not freeze. Therefore, root ice and the like do not obstruct the passage of air in the heat exchanger 1, and the heat exchange efficiency can be maintained.
  • FIG. 7 is a diagram illustrating the distribution of the flat heat transfer tubes 14 in the heat exchanger 1 according to the third embodiment.
  • the flat heat transfer tube 14 belonging to the main heat exchange unit 10A is further divided into a plurality of sets having different distribution paths by the partition plate in the distribution header 11 and the folded header 13. It shall be.
  • the number of flat heat transfer tubes 14 in each set does not have to be equal, and may be different.
  • At least the number of flat heat transfer tubes 14 of the set closest to the center of rotation of the blower is determined. Arrange the set so that the number of flat heat transfer tubes 14 is smaller than that of the other sets. Basically, the wind speed of the air at the center of rotation of the blower becomes faster. Therefore, by reducing the number of the flat heat transfer tubes 14 and increasing the refrigerant flow rate of the flat heat transfer tubes 14 having a high heat load, the heat exchanger performance in the heat exchanger 1 can be improved.
  • FIG. 8 is a diagram showing an outline of the configuration of the heat exchanger 1 according to the fourth embodiment.
  • the members and the like having the same reference numerals as those in FIG. 2 are the same members and the like as described in the first embodiment.
  • the flat heat transfer tube 14 belonging to the main heat exchange section 10A of the windward row is connected by a laminated distributor 17 for each set instead of the distribution header 11B.
  • the laminated distributor 17 distributes the refrigerant that has flowed in through the first auxiliary heat exchange unit 10B, the distribution header 11B, and the connection pipe 16 in the upwind row. Further, when the heat exchanger 1 becomes an evaporator, the laminated distributor 17 merges the refrigerant that has passed through the main heat exchange unit 10A.
  • FIG. 9 is a diagram showing an example of the configuration of the laminated distributor 17 according to the fourth embodiment.
  • the laminated distributor 17 is a distributor manufactured by laminating a plurality of plates 17A, which are a plurality of plate-shaped members having through holes or through grooves serving as flow paths.
  • the plate 17A has a flow path groove 17B and a flow path hole 17C.
  • the flow path groove 17B is a groove through which the refrigerant passes.
  • the flow path hole 17C is a through hole that communicates with the adjacent plate 17A and allows the refrigerant to pass through.
  • the laminated distributor 17 is not limited to the configuration shown in FIG.
  • the heat exchanger 1 is used for the outdoor heat exchanger 230 of the outdoor unit 200, but the present invention is not limited to this. It may be used for the indoor heat exchanger 110 of the indoor unit 100, or may be used for both the outdoor heat exchanger 230 and the indoor heat exchanger 110.
  • the air conditioner can also be applied to other refrigeration cycle devices such as a refrigerating device, a refrigerating device, and a hot water supply device.
  • the heat exchange unit 10 is a corrugated fin tube type heat exchanger 1 using a flat heat transfer tube 14, but for example, a heat transfer tube such as a circular tube.
  • a heat exchanger 1 having a heat exchange unit 10 that exchanges heat using the above may be used.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2020/022105 2020-06-04 2020-06-04 熱交換器および冷凍サイクル装置 Ceased WO2021245877A1 (ja)

Priority Applications (5)

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US17/916,325 US20230194180A1 (en) 2020-06-04 2020-06-04 Heat exchanger and refrigeration cycle device
CN202080101449.0A CN115917243A (zh) 2020-06-04 2020-06-04 热交换器和制冷循环装置
PCT/JP2020/022105 WO2021245877A1 (ja) 2020-06-04 2020-06-04 熱交換器および冷凍サイクル装置
EP20938547.5A EP4163580A4 (en) 2020-06-04 2020-06-04 HEAT EXCHANGER AND REFRIGERATION CYCLE DEVICE
JP2022529249A JP7399286B2 (ja) 2020-06-04 2020-06-04 熱交換器および冷凍サイクル装置

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JPWO2023234121A1 (https=) * 2022-05-31 2023-12-07
JPWO2023233572A1 (https=) * 2022-06-01 2023-12-07

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WO2022114849A1 (ko) * 2020-11-27 2022-06-02 주식회사 경동나비엔 증발식 응축기 및 이를 포함하는 공기 조화기

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JP7840404B2 (ja) 2022-05-31 2026-04-03 株式会社デンソーエアクール 車載用熱交換器
JPWO2023233572A1 (https=) * 2022-06-01 2023-12-07
JP7738754B2 (ja) 2022-06-01 2025-09-12 三菱電機株式会社 熱交換器及び冷凍サイクル装置

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JPWO2021245877A1 (https=) 2021-12-09
CN115917243A (zh) 2023-04-04

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