US20230194180A1 - Heat exchanger and refrigeration cycle device - Google Patents

Heat exchanger and refrigeration cycle device Download PDF

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Publication number
US20230194180A1
US20230194180A1 US17/916,325 US202017916325A US2023194180A1 US 20230194180 A1 US20230194180 A1 US 20230194180A1 US 202017916325 A US202017916325 A US 202017916325A US 2023194180 A1 US2023194180 A1 US 2023194180A1
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United States
Prior art keywords
heat exchange
exchange portion
heat
refrigerant
heat exchanger
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Abandoned
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US17/916,325
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English (en)
Inventor
Atsushi Takahashi
Tsuyoshi Maeda
Satoru Yanachi
Atsushi Morita
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MAEDA, TSUYOSHI, MORITA, ATSUSHI, TAKAHASHI, ATSUSHI, YANACHI, SATORU
Publication of US20230194180A1 publication Critical patent/US20230194180A1/en
Abandoned legal-status Critical Current

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    • 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
    • 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
    • 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

  • the present disclosure has been achieved to solve the above problems, and it is an object of the present disclosure to provide a heat exchanger that can improve its heat exchange performance, and a refrigeration cycle device.
  • a heat exchanger includes: a heat exchange portion in which a plurality of heat transfer tubes, in which refrigerant flows, are arranged in a height direction, the plurality of heat transfer tubes being configured to exchange heat between the refrigerant and air; a turn-back portion to which one end of each of the plurality of heat transfer tube is connected and which is configured to allow the refrigerant to flow between two rows of heat exchange portions arranged in an airflow direction, one of the two rows of heat exchange portions being the heat exchange portion and arranged on an airflow upstream side, an other of the two rows of heat exchange portions being the heat exchange portion and arranged on an airflow downstream side; and a plurality of distribution merge portions to each of which the other end of the heat transfer tube of the heat exchange portion of each row is connected, and which is configured to distribute the refrigerant to the heat transfer tube or merge refrigerant flows from the heat exchange portions, the plurality of heat transfer tubes of the heat exchange portion being grouped into, in order from an upper side in the height
  • a refrigeration cycle device includes the heat exchanger described above to serve at least as a condenser.
  • a flow of refrigerant in the main heat exchange portion and a flow of air passing through the heat exchanger form a counter flow to exchange heat between the upstream side of the refrigerant in the main heat exchange portion and the downstream side of the air, and exchange heat between the downstream side of the refrigerant in the main heat exchange portion and the upstream side of the air. Due to this configuration, the heat exchanger can maintain a sufficient temperature difference between refrigerant and air to effectively exchange heat between them throughout the entire refrigerant flow passage, and can consequently improve the heat transfer performance of the heat exchanger.
  • FIG. 1 illustrates the configuration of an air-conditioning device according to Embodiment 1.
  • FIG. 2 schematically illustrates the configuration of a heat exchanger 1 according to Embodiment 1.
  • FIG. 3 is an explanatory view illustrating each part of a heat exchange portion 10 in the heat exchanger 1 according to Embodiment 1.
  • FIG. 4 schematically illustrates variations in the temperatures of air and refrigerant in the heat exchanger 1 according to Embodiment 1 when the heat exchanger 1 serves as a condenser.
  • FIG. 5 schematically illustrates variations in the temperatures of air and refrigerant in the heat exchanger 1 according to Embodiment 1 when the heat exchanger 1 serves as an evaporator.
  • FIG. 6 schematically illustrates variations in the temperatures of air and refrigerant in the heat exchanger 1 according to Embodiment 2 when the heat exchanger 1 serves as an evaporator.
  • FIG. 7 is an explanatory view illustrating allocation of flat heat transfer tubes 14 in the heat exchanger 1 according to Embodiment 3.
  • FIG. 8 schematically illustrates the configuration of the heat exchanger 1 according to Embodiment 4.
  • FIG. 9 illustrates an example of the configuration of a layered distributor 17 according to Embodiment 4.
  • the upper side in the drawings is described as “up,” while the lower side in the drawings is described as “down.” Furthermore, the level of the pressure and temperature is not particularly determined in relation to an absolute value, but is determined relative to the conditions or operation of a device or the like. When it is not necessary to distinguish or specify a plurality of devices of the same type that are distinguished from each other by subscripts, the subscripts may be omitted.
  • the indoor unit 100 includes an indoor air-sending device 130 in addition to the indoor heat exchanger 110 and the expansion valve 120 .
  • the expansion valve 120 that is an expansion device or other device reduces the pressure of refrigerant and expands the refrigerant.
  • the expansion valve 120 adjusts its opening degree based on an instruction provided by a controller (not illustrated) or other device.
  • the indoor heat exchanger 110 exchanges heat between refrigerant and air in a room that is an air-conditioned space. For example, during heating operation, the indoor heat exchanger 110 functions as a condenser, and condenses and liquefies the refrigerant.
  • the indoor heat exchanger 110 functions as an evaporator, and evaporates and vaporizes the refrigerant.
  • the indoor air-sending device 130 allows the air in the room to pass through the indoor heat exchanger 110 , and supplies the air having passed through the indoor heat exchanger 110 to the room.
  • the outdoor unit 200 in Embodiment 1 includes devices forming the refrigerant circuit, such as the compressor 210 , the four-way valve 220 , the outdoor heat exchanger 230 , and an accumulator 240 .
  • the outdoor unit 200 includes an outdoor air-sending device 250 .
  • the compressor 210 compresses suctioned refrigerant and discharges the compressed refrigerant.
  • the compressor 210 is, for example, a scroll compressor, a reciprocating compressor, or a vane compressor.
  • the compressor 210 may allow an inverter circuit to optionally change the operational frequency to change the capacity of the compressor 210 , although the configuration of the compressor 210 is not particularly limited.
  • the four-way valve 220 that serves as a flow switching device is a valve to change the flow direction of refrigerant depending on cooling operation or heating operation.
  • the four-way valve 220 connects the discharge side of the compressor 210 to the indoor heat exchanger 110 , while connecting the suction side of the compressor 210 to the outdoor heat exchanger 230 .
  • the four-way valve 220 connects the discharge side of the compressor 210 to the outdoor heat exchanger 230 , while connecting the suction side of the compressor 210 to the indoor heat exchanger 110 .
  • a case where the four-way valve 220 is used is described as an example, however, the flow switching device is not limited to this case.
  • the accumulator 240 is installed on the suction side of the compressor 210 .
  • the accumulator 240 allows refrigerant in gas form (hereinafter, referred to as “gas refrigerant”) to pass through the accumulator 240 , while accumulating refrigerant in liquid form (hereinafter, referred to as “liquid refrigerant”) in the accumulator 240 .
  • the outdoor heat exchanger 230 exchanges heat between refrigerant and outdoor air.
  • Refrigerant is fluid to serve as a heat exchange medium for the outdoor heat exchanger 230 .
  • the outdoor heat exchanger 230 in Embodiment 1 functions as an evaporator during heating operation, and evaporates and vaporizes the refrigerant.
  • the outdoor heat exchanger 230 functions as a condenser and a subcooling device, and condenses and liquefies the refrigerant to be subcooled.
  • the outdoor heat exchanger 230 in Embodiment 1 includes heat exchangers 1 , each of which includes a heat exchange portion 10 as will be described later.
  • the heat exchanger 1 will be described later in detail.
  • the outdoor air-sending device 250 is driven to allow air from the outside of the outdoor unit 200 to pass through the outdoor heat exchanger 230 to form a flow of air that flows out of the outdoor unit 200 .
  • each device in the air-conditioning device is described based on the flow of refrigerant.
  • operation of each device in the refrigerant circuit during heating operation is described based on the flow of refrigerant.
  • the solid arrows in FIG. 1 show the flow of refrigerant during heating operation.
  • High-temperature high-pressure gas refrigerant, compressed by and discharged from the compressor 210 passes through the four-way valve 220 , and then flows into the indoor heat exchanger 110 . While passing through the indoor heat exchanger 110 , the gas refrigerant exchanges heat with air in, for example, an air-conditioned space, and thereby condenses into liquid.
  • the refrigerant having condensed into liquid passes through the expansion valve 120 .
  • the pressure of the refrigerant is reduced.
  • the refrigerant exchanges heat with outdoor air delivered from the outdoor air-sending device 250 , and thereby evaporates into gas.
  • the gas refrigerant passes through the four-way valve 220 and the accumulator 240 , and then is suctioned into the compressor 210 again.
  • refrigerant of the air-conditioning device circulates, and thus the air-conditioning device performs heating-related air conditioning.
  • FIG. 1 show the flow of refrigerant during cooling operation.
  • High-temperature high-pressure gas refrigerant compressed by and discharged from the compressor 210 , passes through the four-way valve 220 , and then flows into the outdoor heat exchanger 230 .
  • the refrigerant passes through the outdoor heat exchanger 230 , exchanges heat with outdoor air supplied by the outdoor air-sending device 250 , and thereby condenses into liquid.
  • the heat exchanger 1 will be described later.
  • the liquid refrigerant passes through the expansion valve 120 . When passing through the expansion valve 120 , the subcooled refrigerant is reduced in pressure and brought into a two-phase gas-liquid state.
  • This refrigerant reduced in pressure by the expansion valve 120 and brought into a two-phase gas-liquid state, then passes through the indoor heat exchanger 110 .
  • the refrigerant having exchanged heat with air in, for example, the air-conditioned space and thereby evaporated into gas, passes through the four-way valve 220 , and is suctioned into the compressor 210 again.
  • refrigerant of the air-conditioning device circulates, and thus the air-conditioning device performs cooling-related air conditioning.
  • FIG. 2 schematically illustrates the configuration of the heat exchanger 1 according to Embodiment 1.
  • FIG. 3 is an explanatory view illustrating each part of the heat exchange portion 10 in the heat exchanger 1 according to Embodiment 1.
  • the heat exchanger 1 according to Embodiment 1 is included in the outdoor heat exchanger 230 .
  • the heat exchanger 1 is not limited to being included in the outdoor heat exchanger 230 , but may be included in the indoor heat exchanger 110 .
  • the heat exchanger 1 is a corrugated-fin and tube heat exchanger that is a parallel pipe heat exchanger.
  • the heat exchanger 1 includes two distribution headers 11 (a distribution header 11 A and a distribution header 11 B) serving as a distribution merge portion, a turn-back header 13 serving as a turn-back portion, and the heat exchange portion 10 including a plurality of flat heat transfer tubes 14 and a plurality of corrugated fins 15 .
  • the plurality of flat heat transfer tubes 14 are arranged in the height direction to be perpendicular to the distribution headers 11 and the turn-back header 13 with the flat surfaces of the flat heat transfer tubes 14 facing parallel to each other.
  • groups of the plurality of flat heat transfer tubes 14 are arranged in two rows in the depth direction that is the front-rear direction. One row of a group of the flat heat transfer tubes 14 is connected to a single distribution header 11 .
  • Each of the flat heat transfer tubes 14 serves as a flow passage of refrigerant.
  • the number of the flat heat transfer tubes 14 is equal in each row group.
  • the number of the flat heat transfer tubes 14 is equal as described above, so that the flat heat transfer tubes 14 are equally spaced from each other, thereby not to interfere with the passage of air.
  • the heat exchanger 1 can be easily manufactured.
  • One of the two rows of the flat heat transfer tubes 14 arranged on the airflow upstream side relative to the direction in which air passes through the heat exchanger 1 , is defined as “airflow upstream side row,” while the other row arranged on the airflow downstream side is defined as “airflow downstream side row.”
  • the distribution headers 11 that are devices serving as a distribution merge portion are connected by pipes to other devices that make up the refrigeration cycle device.
  • Each of the distribution headers 11 is a pipe serving as a refrigerant distributor to allow refrigerant to flow into and out of the heat exchanger 1 , and divide and distribute the refrigerant or merge refrigerant flows.
  • the refrigerant is fluid serving as a heat exchange medium. While the distribution headers 11 have a circular cylindrical shape, the distribution headers 11 are not limited to having a particular shape.
  • the distribution headers 11 respectively include refrigerant inlet/outlet pipes 12 (a refrigerant inlet/outlet pipe 12 A and a refrigerant inlet/outlet pipe 12 B) through which refrigerant flows in from and out to the outside.
  • the region refers to a group of the flat heat transfer tubes 14 , in each of which refrigerant flows in the same direction.
  • the baffles partition the interior of the distribution header 11 , so that a plurality of the flat heat transfer tubes 14 can be grouped into a single region.
  • the regions in Embodiment 1 will be described later.
  • Connection pipes 16 connect the spaces, separated from each other inside the distribution header 11 , from the outside.
  • Each of the connection pipes 16 not only connects the spaces inside the distribution header 11 on a one-to-one basis, but can also branch off on one side to connect one of the spaces inside the distribution header 11 to a plurality of the spaces.
  • the turn-back header 13 serves as a bridge configured to merge refrigerant flows from one row of a group of the flat heat transfer tubes 14 , and then divide the refrigerant into the other row of a group of the flat heat transfer tubes 14 to allow the refrigerant to flow out.
  • baffles are also installed at least at positions corresponding to the positions of the baffles in the distribution headers 11 to divide the interior of the turn-back header 13 into a plurality of spaces.
  • baffles may be installed inside the turn-back header 13 corresponding to the respective flat heat transfer tubes 14 .
  • the interior of the turn-back header 13 may be divided into spaces in a one-to-one correspondence with their respective flat heat transfer tubes 14 .
  • the main heat exchange portions 10 A of the airflow upstream side row and the airflow downstream side row will be described later.
  • refrigerant flows are not merged, or the refrigerant is not divided into flows.
  • the flat heat transfer tubes 14 in the heat exchange portion 10 of the airflow upstream side row are brought into one-to-one correspondence with the flat heat transfer tubes 14 in the heat exchange portion 10 of the airflow downstream side row.
  • individual connection pipes or the like can be used to connect the flat heat transfer tubes 14 corresponding to each other.
  • Each of the flat heat transfer tubes 14 has an elongated shape in cross-section in which the outer surface on the longitudinal side of the elongated shape along the depth direction that is an air flow direction is flat, while the outer surface on the relatively short side of the elongated shape perpendicular to the longitudinal direction is curved.
  • Each of the flat heat transfer tubes 14 in Embodiment 1 is a multi-hole flat heat transfer tube having a plurality of holes serving as a flow passage of refrigerant inside the tube. In Embodiment 1, since the holes of the flat heat transfer tubes 14 serve as a flow passage extending between the distribution headers 11 and the turn-back header 13 , these holes are formed in the horizontal direction.
  • each of the flat heat transfer tubes 14 is inserted into an insertion hole (not illustrated) formed on the distribution header 11 and an insertion hole (not illustrated) formed on the turn-back header 13 to be brazed and joined to the distribution header 11 and the turn-back header 13 .
  • the brazing material to be used include an aluminum-containing brazing material. With this brazing, the inside of each of the flat heat transfer tubes 14 communicates with the distribution header 11 and the turn-back header 13 .
  • the corrugated fins 15 are located between the opposite flat surfaces of the flat heat transfer tubes 14 aligned in a row.
  • the corrugated fins 15 are located to increase the heat transfer area between refrigerant and outside air.
  • Each of the corrugated fins 15 is formed by corrugating a plate material into a wavy shape in which the plate material is folded in a zigzag pattern with a series of alternate crest folds and valley folds.
  • the folded portions of protrusions and recesses formed into a wavy shape are the peaks of the wavy shape.
  • the peaks of the corrugated fins 15 are arranged along the height direction.
  • Each of the corrugated fins 15 is in surface contact at the peaks of the wavy shape with the flat surfaces of the flat heat transfer tubes 14 .
  • the contact portions are brazed and joined to each other by using a brazing material.
  • the plate material for the corrugated fins 15 is made of, for example, aluminum alloy.
  • the surface of the plate material is coated with a layer of brazing material.
  • the coating layer of brazing material is, for example, based on a brazing material containing aluminum silicon-based aluminum.
  • the baffles installed inside the distribution headers 11 and the turn-back header 13 divide the flat heat transfer tubes 14 of the airflow upstream side row into regions, and divide the flat heat transfer tubes 14 of the airflow downstream side row into regions.
  • the regions are the main heat exchange portion 10 A, a first auxiliary heat exchange portion 10 B, and a second auxiliary heat exchange portion 10 C.
  • the uppermost region is defined as the main heat exchange portion 10 A.
  • the region lower than the main heat exchange portion 10 A is defined as the first auxiliary heat exchange portion 10 B.
  • the region lower than the first auxiliary heat exchange portion 10 B is defined as the second auxiliary heat exchange portion 10 C.
  • the number of the flat heat transfer tubes 14 grouped together in each region of the heat exchanger 1 in Embodiment 1 has the relationship expressed as “the main heat exchange portion 10 A>the first auxiliary heat exchange portion 10 B ⁇ the second auxiliary heat exchange portion 10 C.”
  • FIG. 4 schematically illustrates variations in the temperatures of air and refrigerant in the heat exchanger 1 according to Embodiment 1 when the heat exchanger 1 serves as a condenser.
  • the solid line shows the temperature of refrigerant, while the dotted line shows the temperature of air (the same applies in FIGS. 5 and 6 ).
  • the arrows illustrated in the heat exchange portion 10 show the flow of refrigerant in the heat exchange portion 10 when the heat exchanger 1 serves as a condenser.
  • refrigerant flows through the refrigerant inlet/outlet pipe 12 A into the distribution header 11 A.
  • the refrigerant having flowed into the distribution header 11 A passes through the flat heat transfer tubes 14 belonging to the main heat exchange portion 10 A of the airflow downstream side row.
  • the flat heat transfer tubes 14 exchange heat between refrigerant passing through the inside of the tubes and outside air passing outside the tubes. At this time, while passing through the flat heat transfer tubes 14 , the refrigerant transfers heat to the outside air.
  • the heat exchanger 1 serves as a condenser
  • refrigerant transfers heat to the outside air while passing through the flat heat transfer tubes 14 , in all the regions in the same manner.
  • the refrigerant is turned back in the turn-back header 13 , and passes through the flat heat transfer tubes 14 belonging to the main heat exchange portion 10 A of the airflow upstream side row.
  • the refrigerant having passed through the flat heat transfer tubes 14 of the airflow upstream side row and having exchanged heat with air, flows into the distribution header 11 B.
  • the refrigerant having flowed into the distribution header 11 B passes through the connection pipes 16 and flows into other spaces in the distribution header 11 B.
  • the refrigerant passes through the flat heat transfer tubes 14 belonging to the first auxiliary heat exchange portion 10 B of the airflow upstream side row, is turned back in the turn-back header 13 , passes through the first auxiliary heat exchange portion 10 B of the airflow downstream side row, and then flows into the distribution header 11 A.
  • the refrigerant having flowed into the distribution header 11 A passes through the connection pipes 16 and flows into other spaces in the distribution header 11 A. Then, the refrigerant passes through the flat heat transfer tubes 14 belonging to the second auxiliary heat exchange portion 10 C of the airflow downstream side row, is turned back in the turn-back header 13 , passes through the second auxiliary heat exchange portion 10 C of the airflow upstream side row, and then flows into the distribution header 11 B.
  • the refrigerant, having flowed in the order described and condensed flows out through the refrigerant inlet/outlet pipe 12 B.
  • the heat exchanger 1 in Embodiment 1 serves as a condenser
  • refrigerant that flows in the main heat exchange portions 10 A forms a counter flow to the flow of air.
  • the counter flow refers to a flow in which refrigerant on the downstream side of the refrigerant flow and air on the upstream side of the air flow exchange heat between them, and also refrigerant on the upstream side of the refrigerant flow and air on the downstream side of the air flow exchange heat between them.
  • FIG. 5 schematically illustrates variations in the temperatures of air and refrigerant in the heat exchanger 1 according to Embodiment 1 when the heat exchanger 1 serves as an evaporator.
  • refrigerant flows through the refrigerant inlet/outlet pipe 12 B into the distribution header 11 B.
  • the refrigerant having flowed into the distribution header 11 B passes through the flat heat transfer tubes 14 belonging to the second auxiliary heat exchange portion 10 C of the airflow upstream side row.
  • the flat heat transfer tubes 14 exchange heat between refrigerant passing through the inside of the tubes and outside air passing outside the tubes.
  • the refrigerant receives heat from the outside air.
  • refrigerant receives heat from the outside air while passing through the flat heat transfer tubes 14 , in all the regions in the same manner.
  • the refrigerant is turned back in the turn-back header 13 , and passes through the flat heat transfer tubes 14 belonging to the second auxiliary heat exchange portion 10 C of the airflow downstream side row.
  • the refrigerant having passed through the flat heat transfer tubes 14 of the airflow downstream side row and having exchanged heat with air, flows into the distribution header 11 A.
  • the refrigerant having flowed into the distribution header 11 A passes through the connection pipes 16 and flows into other spaces in the distribution header 11 A.
  • the refrigerant passes through the flat heat transfer tubes 14 belonging to the first auxiliary heat exchange portion 10 B of the airflow downstream side row, is turned back in the turn-back header 13 , passes through the first auxiliary heat exchange portion 10 B of the airflow upstream side row, and then flows into the distribution header 11 B.
  • the refrigerant having flowed into the distribution header 11 B passes through the connection pipes 16 and flows into other spaces in the distribution header 11 B. Then, the refrigerant passes through the flat heat transfer tubes 14 belonging to the main heat exchange portion 10 A of the airflow upstream side row, is turned back in the turn-back header 13 , passes through the main heat exchange portion 10 A of the airflow downstream side row, and then flows into the distribution header 11 A.
  • the refrigerant, having flowed in the order described and condensed flows out through the refrigerant inlet/outlet pipe 12 A. Therefore, when the heat exchanger 1 in Embodiment 1 serves as an evaporator, refrigerant that flows in the main heat exchange portions 10 A forms a parallel flow to the flow of air.
  • the refrigerant passing through the main heat exchange portion 10 A has a sufficient temperature difference from the air passing through the heat exchanger 1 to effectively exchange heat between them. This prevents the heat exchanger 1 from degrading its heat exchange performance when the heat exchanger 1 serves as an evaporator. Thus, the heat exchanger 1 can maintain its evaporator performance.
  • the heat exchanger 1 As described above, in the heat exchanger 1 to be used as the outdoor heat exchanger 230 of the air-conditioning device in Embodiment 1, when the heat exchanger 1 serves as a condenser, refrigerant flows in such a manner that a flow of refrigerant in the main heat exchange portion 10 A, and a flow of air passing through the heat exchanger 1 form a counter flow. Due to this configuration, the heat exchanger 1 can maintain a sufficient temperature difference between refrigerant and air to effectively exchange heat between them throughout the entire refrigerant flow passage, and can consequently improve the heat transfer performance of the heat exchanger 1 .
  • the heat exchanger 1 serves as an evaporator
  • a flow of refrigerant in the main heat exchange portion 10 A, and a flow of air passing through the heat exchanger 1 form a parallel flow.
  • this causes pressure loss of refrigerant in the second auxiliary heat exchange portion 10 C, and refrigerant whose temperature has decreased flows into the main heat exchange portion 10 A. Due to this configuration, the refrigerant passing through the main heat exchange portion 10 A has a sufficient temperature difference from the air passing through the heat exchanger 1 to effectively exchange heat between them.
  • the heat exchanger 1 can maintain its evaporator performance.
  • the number of the flat heat transfer tubes 14 is equal in both two rows, and consequently air can pass through the flat heat transfer tubes 14 that are equally spaced from each other.
  • the turn-back header 13 refrigerant flows are not merged, or the refrigerant is not divided into flows, and one row of the flat heat transfer tubes 14 are brought into one-to-one correspondence with another row of the flat heat transfer tubes 14 . This can prevent an uneven flow of refrigerant in the turn-back header 13 .
  • FIG. 6 schematically illustrates variations in the temperatures of air and refrigerant in the heat exchanger 1 according to Embodiment 2 when the heat exchanger 1 serves as an evaporator.
  • the air-conditioning device and the heat exchanger 1 in Embodiment 2 have identical configurations to the air-conditioning device and the heat exchanger 1 described in Embodiment 1.
  • the number of the flat heat transfer tubes 14 grouped into each region of the heat exchanger 1 in Embodiment 2 particularly has a relationship expressed as “the main heat exchange portion 10 A>the first auxiliary heat exchange portion 10 B>the second auxiliary heat exchange portion 10 C.”
  • the heat exchanger 1 serves as an evaporator
  • refrigerant flows through the refrigerant inlet/outlet pipe 12 B into the distribution header 11 B, and then passes through the flat heat transfer tubes 14 belonging to the second auxiliary heat exchange portion 10 C of the airflow upstream side row, that is the region at the lowermost position of the heat exchanger 1 .
  • the air-conditioning device allows refrigerant to circulate in the refrigerant circuit such that the refrigerant flows into the second auxiliary heat exchange portion 10 C of the airflow upstream side row with a temperature of the refrigerant higher than the temperature of air that passes through the heat exchange portion 10 of the airflow upstream side row.
  • the refrigerant passing through the second auxiliary heat exchange portion 10 C of the airflow upstream side row at the lowermost position has a temperature higher than the temperature of air. This prevents drain water accumulating at the bottom of the heat exchanger 1 to be used as the outdoor heat exchanger 230 in the outdoor unit 200 from freezing. With this configuration, the passage of air through the heat exchanger 1 is prevented from being interfered with by root ice or the like, and the heat exchange efficiency can be maintained.
  • FIG. 7 is an explanatory view illustrating allocation of flat heat transfer tubes 14 in the heat exchanger 1 according to Embodiment 3.
  • the flat heat transfer tubes 14 belonging to the main heat exchange portion 10 A are further divided into a plurality of subgroups with different distribution paths by baffles in the distribution headers 11 and the turn-back header 13 .
  • the number of the flat heat transfer tubes 14 may not be equal in each of the subgroups, but may differ between the subgroups.
  • an air-sending device includes a side flow fan with its rotational shaft extending in the same direction as the direction in which air passes through the heat exchanger 1 .
  • the subgroups are arranged at least in such a manner that the number of the flat heat transfer tubes 14 in the nearest subgroup from the rotation center of the air-sending device is fewer than those in the other subgroups.
  • a fewer number of the flat heat transfer tubes 14 are allocated near the rotation center, while a larger amount of refrigerant flows in the flat heat transfer tubes 14 with a higher thermal load, so that the heat exchanger 1 can improve its heat exchange performance.
  • FIG. 8 schematically illustrates the configuration of the heat exchanger 1 according to Embodiment 4.
  • the same components as those described in Embodiment 1 are denoted by the same reference numerals as those illustrated in FIG. 2 .
  • the subgroups of the flat heat transfer tubes 14 belonging to the main heat exchange portion 10 A of the airflow upstream side row are connected to each other by using a layered distributor 17 , instead of using the distribution header 11 B.
  • the layered distributor 17 distributes refrigerant flowing therein after the refrigerant has passed through the first auxiliary heat exchange portion 10 B of the airflow upstream side row, the distribution header 11 B, and the connection pipes 16 .
  • the layered distributor 17 merges refrigerant flows having passed through the main heat exchange portion 10 A.
  • FIG. 9 illustrates an example of the configuration of the layered distributor 17 according to Embodiment 4.
  • the layered distributor 17 is manufactured by stacking a plurality of plates 17 A on one another, that are a plurality of plate-like parts including through holes or through grooves serving as a flow passage.
  • the plates 17 A include flow passage grooves 17 B and flow passage holes 17 C.
  • the flow passage grooves 17 B allow refrigerant to pass therethrough.
  • the flow passage holes 17 C are through holes communicating with the adjacent plates 17 A to allow the refrigerant to pass therethrough.
  • the layered distributor 17 is not limited to having the configuration illustrated in FIG. 9 .
  • the heat exchangers 1 are used as the outdoor heat exchanger 230 of the outdoor unit 200 , however, use of the heat exchangers 1 is not limited to this example.
  • the heat exchangers 1 may be used as the indoor heat exchanger 110 of the indoor unit 100 , or may be used as both the outdoor heat exchanger 230 and the indoor heat exchanger 110 .
  • the air-conditioning device has been explained.
  • the heat exchanger 1 is also applicable to other refrigeration cycle devices, such as a refrigerator, a freezer, or a water heater.
  • the heat exchanger 1 is described as a corrugated-fin and tube heat exchanger including the heat exchange portion 10 using the flat heat transfer tubes 14 .
  • the heat exchanger 1 may include the heat exchange portion 10 configured to exchange heat by using, for example, circular heat transfer tubes.

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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)
US17/916,325 2020-06-04 2020-06-04 Heat exchanger and refrigeration cycle device Abandoned US20230194180A1 (en)

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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

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EP4163580A1 (en) 2023-04-12
WO2021245877A1 (ja) 2021-12-09
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JPWO2021245877A1 (https=) 2021-12-09
CN115917243A (zh) 2023-04-04

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