EP4166858A1 - Unité extérieure pour dispositif de climatisation - Google Patents

Unité extérieure pour dispositif de climatisation Download PDF

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Publication number
EP4166858A1
EP4166858A1 EP20940548.9A EP20940548A EP4166858A1 EP 4166858 A1 EP4166858 A1 EP 4166858A1 EP 20940548 A EP20940548 A EP 20940548A EP 4166858 A1 EP4166858 A1 EP 4166858A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
exchange unit
heat exchange
column
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.)
Pending
Application number
EP20940548.9A
Other languages
German (de)
English (en)
Other versions
EP4166858A4 (fr
Inventor
Hiroyuki Toyoda
Gen Yasuda
Michael Sun
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Hitachi Johnson Controls Air Conditioning Inc
Original Assignee
Hitachi Johnson Controls Air Conditioning Inc
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 Hitachi Johnson Controls Air Conditioning Inc filed Critical Hitachi Johnson Controls Air Conditioning Inc
Publication of EP4166858A1 publication Critical patent/EP4166858A1/fr
Publication of EP4166858A4 publication Critical patent/EP4166858A4/fr
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/46—Component arrangements in separate outdoor units
    • F24F1/48—Component arrangements in separate outdoor units characterised by air airflow, e.g. inlet or outlet airflow
    • F24F1/50—Component arrangements in separate outdoor units characterised by air airflow, e.g. inlet or outlet airflow with outlet air in upward direction
    • 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
    • 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
    • F28D1/0443—Combination of units extending one beside or one above the other
    • 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
    • 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

Definitions

  • the present invention relates to an outdoor unit of an air conditioning device, and more specifically relates to a top flow type outdoor unit in which a blower fan is mounted above a heat exchanger.
  • Each of the indoor unit and the outdoor unit includes a heat exchanger that exchanges heat between air and refrigerant, a blower fan that supplies air to the heat exchanger, and a refrigerant pipe that connects the outdoor unit and the indoor unit to each other.
  • the heat exchanger of the outdoor unit has a function of absorbing heat from outdoor air in the case of a heating operation of heating the inside of the room, and releasing heat to outdoor air in the case of a cooling operation of cooling the inside of the room.
  • VRF variable refrigerant flow
  • a top flow type outdoor unit in which a blower fan is mounted above a heat exchanger has been often used as the outdoor unit used for the VRF type air conditioning device.
  • a heat exchanger used for such a top flow type outdoor unit one using flat pipes as heat transfer pipes is described in WO 2014/199501 A (Patent Literature 1).
  • the outdoor unit of Patent Literature 1 includes: the heat exchanger having the multiple flat heat transfer pipes arranged in parallel and used at least as a condenser in a refrigeration cycle; and a blower fan that generates the flow of air passing through the heat exchanger with predetermined wind speed distribution.
  • a "refrigerant path” described below indicates a refrigerant flow path.
  • the heat exchanger as the condenser exchanges heat between air and refrigerant flowing in the heat transfer pipe, thereby releasing the heat of the refrigerant to the air.
  • the heat exchanger has multiple refrigerant paths formed by one or more heat transfer pipes, and the multiple refrigerant paths include: multiple first refrigerant paths through which gas refrigerant flows in and two-phase refrigerant flows out; and multiple second refrigerant paths through which the two-phase refrigerant having flowed out of the multiple first refrigerant paths flows in and subcooled liquid refrigerant flows out.
  • the multiple second refrigerant paths are arranged in a region where the wind speed of air is lower than a region where the multiple first refrigerant paths are arranged.
  • the multiple first refrigerant paths are arranged in regions different from each other in the wind speed of air, and the multiple second refrigerant paths are also arranged in regions different from each other in the wind speed of air.
  • the multiple first refrigerant paths and the multiple second refrigerant paths are configured such that the first refrigerant path and the second refrigerant path correspond to each other in a descending order of the wind speed of air in the region and outlet sides of the multiple first refrigerant paths are respectively coupled to inlet sides of the multiple corresponding second refrigerant paths.
  • Patent Literature 2 JP-A-2014-126322 discloses that in an air conditioning device using, as heat transfer pipes, circular pipes bent in a U-shape for a heat exchanger of an outdoor unit, the number of refrigerant paths is increased in order to improve an air conditioning capacity in the outdoor heat exchanger.
  • the air conditioning device described in Patent Literature 2 is configured such that an outdoor unit having a compressor, the outdoor heat exchanger, and an outdoor expansion valve and an indoor unit inside a room are connected to each other through a liquid connection pipe and a gas connection pipe.
  • the outdoor heat exchanger includes multiple plate-shaped heat exchange fins, multiple heat transfer pipes, and a liquid refrigerant distributor and a gas refrigerant distributor for converging the heat transfer pipes to multiple paths.
  • the number of refrigerant paths on a gas refrigerant distributor side is equal to or greater than twice as many as the number of refrigerant paths on a liquid refrigerant distributor side, and one outdoor heat exchanger is divided into multiple heat exchangers.
  • Each of the multiple divided outdoor heat exchangers includes multiple plate-shaped heat exchange fins, multiple heat transfer pipes perpendicular to the plate-shaped heat exchanger fins, and a liquid refrigerant distributor and a gas refrigerant distributor for converging the heat transfer pipes to multiple paths. It is configured such that the total number of refrigerant paths on the liquid refrigerant distributor side in the multiple divided outdoor heat exchangers is greater than a value of the quarter of the number of rows of the heat transfer pipes of the outdoor heat exchanger before division.
  • the number of refrigerant paths in the heat exchanger is the number of refrigerant paths through which refrigerant flows so as to be branched in the heat exchanger. If the number of refrigerant paths is small, when liquid refrigerant is gasified, a flow speed in the refrigerant path is too high, and for this reason, an internal pressure loss increases.
  • a difference in height between a liquid-side outlet of the uppermost refrigerant path and a liquid-side outlet of the lowermost refrigerant path is often close to 1 m.
  • the pressure of liquid refrigerant corresponding to the height acts on the liquid-side outlet of the lowermost refrigerant path, and is close to 10 kPa.
  • a pressure difference between a gas side and a liquid side upon use as a condenser is generally small, and in some cases, falls below 10 kPa specifically under a condition where the number of refrigerant paths is great.
  • no refrigerant flows in the lower refrigerant path of the heat exchanger on the liquid-side outlet of which the pressure acts. Since no heat exchange is substantially made in the refrigerant path in which no refrigerant flows, a heat transfer area in such a region is wasted, leading to degradation of the heat exchange performance (the cooling performance).
  • a blower fan is at an upper portion in the outdoor unit, and at a side surface of the outdoor unit, the heat exchanger is arranged perpendicularly to an installation surface (e.g., a ground surface or a floor of a roof of a building).
  • an installation surface e.g., a ground surface or a floor of a roof of a building.
  • a heat exchange amount at the lower portion of the heat exchanger is smaller than that at the upper portion of the heat exchanger. For this reason, it is necessary to adjust a refrigerant distribution amount according to the heat exchange amount by a liquid refrigerant distributor and a pressure loss body such as a small-diameter pipe, and a manufacturing cost increases by an amount corresponding to such adjustment.
  • the first refrigerant paths are arranged in the region where the wind speed is relatively high, and the second refrigerant paths are arranged in the region where the wind speed is relatively low.
  • Patent Literature 1 since the heat exchanger described in Patent Literature 1 employs the flat pipe, the internal flow path is thin. For this reason, a pressure loss specifically upon use as an evaporator increases, and interferes with improvement in a heating capacity. In addition, there are problems that the flat pipe has a complicated structure and a manufacturing cost therefor increases.
  • the present invention is intended to provide an outdoor unit of an air conditioning device configured so that a high heating capacity and improved cooling performance can be achieved at a low cost under influence of a liquid head in association with wind speed distribution in a heat exchanger and the height of the heat exchanger.
  • an outdoor unit of an air conditioning device including at least: a compressor; a blower fan; and a heat exchanger.
  • the blower fan is mounted above the heat exchanger.
  • the heat exchanger includes an upper heat exchanger and a lower heat exchanger, and each heat exchanger includes: a U-shaped heat transfer pipe configured with a circular pipe bent in a U-shape; a heat exchange fin; a liquid refrigerant distributor; a gas header; and a path connection pipe connecting end portions of the U-shaped heat transfer pipes.
  • the heat exchanger includes three columns of heat exchange units arranged along an air flow direction.
  • a first-column heat exchange unit as a windward-side heat exchange unit is configured such that the U-shaped heat transfer pipes are arranged in a row direction, and the U-shaped heat transfer pipes are arranged over two columns of a second-column heat exchange unit and a third-column heat exchange unit on a leeward side. End portions of the U-shaped heat transfer pipes of the third-column heat exchange unit in the upper heat exchanger are connected to the gas header, a number of refrigerant paths connected to this gas header is greater than a half of a total row number in the heat exchanger, and a number of rows in the upper heat exchanger is equal to the number of refrigerant paths connected to the gas header.
  • End portions of the U-shaped heat transfer pipes of the first-column heat exchange unit in the lower heat exchanger are connected to the liquid refrigerant distributor.
  • Each U-shaped heat transfer pipe of the third-column heat exchange unit in the lower heat exchanger is connected to a corresponding one of the U-shaped heat transfer pipes of the first-column heat exchange unit in the upper heat exchanger through the path connection pipe.
  • a high heating capacity and improved cooling performance can be achieved at a low cost under the influence of the liquid head in association with wind speed distribution in the heat exchanger and the height of the heat exchanger.
  • the outdoor unit to which the present invention is applied is a top flow type outdoor unit having a fan at an upper portion in a housing.
  • the height of the outdoor unit exceeds 1 m, and the height of a heat exchanger also exceeds 1 m.
  • the outdoor unit to which the present invention is applied includes two blower fans 13, two bell mouths 16 corresponding thereto, and two heat exchangers 12. Note that these components are housed in the housing including a front panel 15, and the like.
  • Fig. 2 shows a perspective view in which the fans, the bell mouths, and the front panel 15 are detached from the outdoor unit shown in Fig. 1 so that the inside of the outdoor unit can be viewed.
  • a compressor 10, a refrigerant tank 11, an accumulator 14, a control panel 17, and the like are arranged inside the outdoor unit.
  • the outdoor unit is placed on a bottom installation board 18.
  • the control panel 17 is equipped with an input unit of a sensor attached to the outdoor unit and an electrical component that controls operation of the compressor 10 or the blower fan 13.
  • the refrigerant tank 11 is attached in the middle of a refrigeration cycle to absorb a difference in the amount of refrigerant necessary in the cycle between cooling operation and heating operation.
  • Fig. 3 shows the outline of the refrigeration cycle in a VRF type air conditioning device, and specifically shows the refrigeration cycle in the heating operation.
  • High-temperature high-pressure gas refrigerant discharged from the compressor 10 flows into a gas-side blocking valve through a refrigerant pipe 9 and a four-way valve 19. From this location, the gas-side blocking valve is connected to an indoor unit 103 through a gas refrigerant pipe 101.
  • the gas refrigerant having flowed out of the gas-side blocking valve flows into an indoor heat exchanger 104 in the indoor unit 103.
  • the indoor units 103 are respectively provided in two rooms 300. Needless to say, the indoor units 103 may be provided in two or more rooms.
  • Air is supplied to the indoor heat exchanger 104 by an indoor blower fan 105, and after having taken heat from refrigerant, is supplied into the room.
  • the refrigerant is cooled and liquefied inside the indoor heat exchanger 104.
  • the liquefied refrigerant flows into a liquid-side blocking valve through a liquid refrigerant pipe 102.
  • the refrigerant having flowed into the outdoor unit 100 from the liquid-side blocking valve is decompressed into a low-temperature low-pressure gas-liquid two-phase state by an outdoor expansion valve 20 housed in the outdoor unit 100, and flows into an outdoor heat exchanger 12 by way of, e.g., the refrigerant tank.
  • Outdoor air is supplied to the outdoor heat exchanger 12 by an outdoor blower fan 13, and the refrigerant is decompressed to a temperature lower than the temperature of the outdoor air flowing in the heat exchanger 12.
  • heat of the outdoor air is absorbed by the refrigerant, and the refrigerant is evaporated in the heat exchanger 12.
  • connection at the four-way valve 19 is switched such that a discharge pipe of the compressor 10 and the outdoor heat exchanger 12 are connected to each other and the gas-side blocking valve and the accumulator 14 are connected to each other by the four-way valve 19.
  • Fig. 4 shows the structure of a typical heat exchanger using circular heat transfer pipes.
  • the heat exchanger includes U-shaped heat transfer pipes 22 as circular heat transfer pipes bent in a U-shape and plate-shaped heat exchange fins 21.
  • the heat exchanger includes three columns, and a first-column heat exchange unit 28, a second-column heat exchange unit 29, and a third-column heat exchange unit 30 are arranged in this order from a windward side along the flow of wind so as to extend in a longitudinal direction.
  • Fig. 5 shows an assembly structure of the heat exchanger.
  • the heat exchanger shown in Fig. 4 is produced in such a manner that the U-shaped heat transfer pipes 22 are inserted into the heat exchange fins 21 stacked at equal pitches.
  • a pipe expansion machine is inserted into the U-shaped heat transfer pipe 22 from end portions thereof, and the U-shaped heat transfer pipe 22 is expanded from the inside.
  • the heat exchange fin 21 and the U-shaped heat transfer pipe 22 closely contact each other.
  • the U-shaped heat transfer pipes 22 are arranged in the longitudinal direction in each column (see Fig. 5 ) so that a heat exchanger assembling step of inserting the U-shaped heat transfer pipes 22 into the heat exchange fin 21 can be performed for each column.
  • Fig. 6 shows typical refrigerant paths (refrigerant flow paths) formed by the U-shaped heat transfer pipes 22.
  • a lateral direction in Fig. 6 is taken as a column direction, and the heat exchange units are counted as the first-column heat exchange unit 28, the second-column heat exchange unit 29, and the third-column heat exchange unit 30 in this order from the left.
  • a longitudinal direction in Fig. 6 is taken as a row direction, and the number of heat transfer pipes is counted as a first row or a second row.
  • the heat exchanger has 3 columns and 12 rows.
  • the typical heat exchanger is configured such that the U-shaped heat transfer pipes 22 are arranged in the row direction and three columns thereof are arranged.
  • Black arrows in Fig. 6 indicate the flow of refrigerant.
  • a two-phase flow having flowed out of an expansion valve is distributed to each liquid-side refrigerant inlet/outlet port 25 of the heat exchanger through a not-shown liquid refrigerant distributor.
  • the refrigerant flows into a gas header 24 from the third-column heat exchange unit 30 of the heat exchanger along the arrows in the figure.
  • the refrigerant having joined together in the gas header 24 flows into a four-way valve.
  • the heat exchanger of the outdoor unit needs to function as an evaporator to gasify a large amount of liquid refrigerant. Since a phase change from liquid to gas significantly increases the volume of refrigerant per same mass, the flow speed of refrigerant increases in the heat transfer pipe in the heat exchanger, leading to a great pressure loss. This pressure loss causes refrigerant temperature distribution inside the heat exchanger, and degrades heat exchange performance of the heat exchanger.
  • the refrigerant paths as shown in Fig. 6 have been employed so that the maximum number of divisions can be formed using the U-shaped heat transfer pipes.
  • the number of refrigerant paths which is the number of refrigerant flow paths, in the heat exchanger is increased as much as possible. Accordingly, the pipe length of one refrigerant path is shortened, and the amount of refrigerant flowing in one refrigerant path is reduced. In this manner, the pressure loss is reduced.
  • a heat exchanger of an outdoor unit is, as in Patent Literature 2, divided so that the amount of refrigerant flowing in one heat exchanger can be reduced and the width of the heat exchanger can be shortened.
  • the flow path length of one turn of a U-shaped heat transfer pipe can be shortened, and naturally, a refrigerant pressure loss can be reduced.
  • the heat exchanger is used, which is configured such that the U-shaped heat transfer pipes are arranged in the row direction in each column.
  • This structure leads to reduction in a manufacturing cost because it is only required that the same heat exchanger is produced for each column and these heat exchangers are combined with each other.
  • a heat exchange amount is the greatest in the first-column heat exchange unit on the windward side, and decreases in the order of the second-column heat exchange unit and the third-column heat exchange unit on the leeward side.
  • the outer diameter of the U-shaped heat transfer pipe 22 is 5 mm to 8 mm, whereas a row pitch is between 15 mm and 30 mm.
  • the height of the heat exchanger in Fig. 6 is approximately 240 mm, assuming that the row pitch is 20 mm.
  • Some of heat exchangers of top flow type outdoor units for a high heating capacity actually have nearly 50 rows and a height exceeding 1 m.
  • the drawing shows 12 rows of the heat exchanger, but actually, refrigerant paths are further present at a similar ratio in the row direction (an upward direction). If the number of rows is 50, it means that the number of refrigerant paths in the typical structure shown in Fig. 6 is 25.
  • refrigerant recently used in the air conditioning device, there are refrigerants such as "R410A” and "R32.”
  • the liquid density of such refrigerant at 2.2 MPa at 35°C is 1006 kg/m 3 in the case of "R410A,” and is 917 kg/m 3 in the case of "R32.”
  • a liquid head of at least 8.9 kPa acts on the lower liquid-side refrigerant inlet/outlet port 25 of the heat exchanger.
  • the pressure loss between the gas header and the liquid refrigerant distributor is often about 10 kPa.
  • a refrigerant circulation amount decreases by an amount corresponding to such a liquid head, and the refrigerant flow pressure loss decreases. This achieves a balance.
  • a liquid head alone exceeds 10 kPa, and a state in which almost no refrigerant flows is brought.
  • No refrigerant flow means that no heat exchange is performed in such a refrigerant path, and the performance is degraded by an amount corresponding to a heat transfer area which cannot be effectively used.
  • the wind speed of air flowing into the heat exchanger is different between an upper portion and a lower portion. That is, it has been known that the wind speed is high on the upper side of the heat exchanger closer to the outdoor blower fan and is low on the lower side of the heat exchanger farther from the outdoor blower fan.
  • the heat exchange amount is greater at the upper portion at which the wind speed is high, it is necessary to supply a large amount of refrigerant. It is necessary to decrease the amount of refrigerant targeted for heat exchange at the lower portion at which the wind speed is low.
  • small-diameter pipes having different lengths are provided among the liquid-side refrigerant inlet/outlet ports 25 and the liquid refrigerant distributor connected thereto, and in this manner, the amount of refrigerant supplied to each refrigerant path is adjusted specifically in the case of use as the evaporator.
  • refrigerant paths as shown in Fig. 7 have been employed for a model not requiring a high heating capacity. That is, in a refrigerant path configuration similar to that of Patent Literature 1, a heat exchanger is divided into an upper portion and a lower portion. In the heating operation, refrigerant having flowed into the lower heat exchanger passes through a path connection pipe 26, and flows out to a gas header through the upper heat exchanger.
  • the number of paths with liquid-side refrigerant inlet/outlet ports 25 can be decreased when an outdoor heat exchanger is used as a condenser in the cooling operation.
  • a two-phase flow of which liquid phase has been increased by progress of condensation of refrigerant tends to decrease in a flow speed, but such a flow speed decrease can be suppressed if the number of paths with the liquid-side refrigerant inlet/outlet ports 25 can be reduced.
  • the refrigerant flow speed can be increased in one with a smaller number of refrigerant paths, and therefore, a thermal conductivity on a refrigerant side is likely to be high and the subcooling amount is easily ensured.
  • a first embodiment of the present invention is intended to provide an outdoor unit of an air conditioning device configured so that a pressure loss upon use of a heat exchanger as an evaporator can be reduced and a high heating capacity and improved cooling performance can be achieved at a low cost under influence of a liquid head in association with wind speed distribution in the heat exchanger and the height of the heat exchanger.
  • Fig. 8 shows the structure of the heat exchanger used in the present embodiment.
  • a windward-side first-column heat exchange unit 28 of the heat exchanger is configured such that U-shaped heat transfer pipes 22 are arranged in a row direction (a height direction), and a second-column heat exchange unit 29 and a third-column heat exchange unit 30 on the leeward side are configured such that U-shaped heat transfer pipes 22 are arranged over the second-column heat exchange unit 29 and the third-column heat exchange unit 30.
  • the U-shaped heat transfer pipe 22 is bent in a U-shape, and is configured such that a bent portion 22B is exposed on one surface of the heat exchanger 12 parallel with the flow of air and end portions 22E through which refrigerant flows in or out are exposed on the other surface of the heat exchanger 12 parallel with the flow of air.
  • Fig. 9 shows a refrigerant path configuration of the present embodiment.
  • the heat exchanger 12 includes an upper heat exchanger 12U and a lower heat exchanger 12B, and the number of rows in the upper heat exchanger 12U is set greater than that in the lower heat exchanger 12B. In terms of the number of rows in the third-column heat exchange unit 30, the number of rows is doubled.
  • a refrigerant path formed by the U-shaped heat transfer pipes 22 is in a zigzag pattern as viewed in an air flow direction, and is configured so that an interval between the heat transfer pipes can be increased and an air flow pressure loss can be decreased without acceleration of the air flow.
  • a two-phase flow having passed through an expansion valve is first distributed by way of a liquid refrigerant distributor, and thereafter, slightly passes through a small-diameter pipe for distribution adjustment and flows into two liquid-side refrigerant inlet/outlet ports 25 in Fig. 9 .
  • the refrigerant having flowed in through each of two ports flows upward in the U-shaped heat transfer pipe of the first-column heat exchange unit 28, and then on the leeward side thereof, is distributed and flows into two U-shaped heat transfer pipes arranged over the columns of the second-column heat exchange unit 29 and the third-column heat exchange unit 30.
  • the refrigerant path is branched using a three-pronged joint 23 (see Fig. 10 ).
  • the refrigerant having flowed in through two ports flows and passes through four refrigerant paths of the second-column heat exchange unit 29 and the third-column heat exchange unit 30 in the lower heat exchanger 12B. These four refrigerant paths reach the upper heat exchanger 12U through path connection pipes 26.
  • the gasified refrigerant flows into a gas header 24 from eight rows of the third-column heat exchange unit 30 in the upper heat exchanger 12U through eight refrigerant paths.
  • a connection portion (the liquid-side refrigerant inlet/outlet port 25) of the lower heat exchanger 12B with the liquid refrigerant distributor is a lower end portion in the direction of the force of gravity of the U-shaped heat transfer pipe arranged in the row direction in the first-column heat exchange unit 28.
  • Fig. 10 shows a perspective view of the heat exchanger with a refrigerant path pipe of Fig. 9 assembled.
  • the refrigerant path pipe includes the U-shaped heat transfer pipes 22, the three-pronged joints 23, the gas header 24, the path connection pipes 26, and the like.
  • the U-shaped heat transfer pipe 22, the three-pronged joint 23, and the path connection pipe 26 are formed in a circular pipe shape, thereby reducing the pressure loss when the heat exchanger is used as the evaporator.
  • the three-pronged joints 23, the gas header 24, the end portions 22E of the U-shaped heat transfer pipes 22 as the liquid-side refrigerant inlet/outlet ports 25, and the path connection pipes 26 are arranged concentratedly on one surface of the heat exchanger parallel with the air flow, and the U-shaped bent portions 22B of the U-shaped heat transfer pipes 22 are arranged on the other surface of the heat exchanger parallel with the air flow.
  • the first-column heat exchange unit 28 in which the U-shaped heat transfer pipes 22 are arranged in the row direction is combined with the second-column heat exchange unit 29 and the third-column heat exchange unit 30 over which the U-shaped heat transfer pipes 22 are arranged in the row direction, so that the refrigerant paths can be easily divided and increased in number only by means of the three-pronged joints 23 when refrigerant flows from the first-column heat exchange unit 28 to the second-column heat exchange unit 29.
  • the heat exchanger is divided into the upper heat exchanger 12U and the lower heat exchanger 12B, and refrigerant passes through each heat exchanger.
  • refrigerant path only by branching the refrigerant path into two paths from the first-column heat exchange unit 28 to the second-column heat exchange unit 29, one refrigerant path at the liquid-side refrigerant inlet/outlet port 25 can be easily increased to four refrigerant paths until reaching the gas header 24.
  • refrigerant can be branched by the three-pronged joints 23 even in the middle of moving from the refrigerant paths in the lower heat exchanger 12B to the refrigerant paths in the upper heat exchanger 12U.
  • various refrigerant paths can be formed only by means of the three-pronged joints 23. This will be described in detail in second and third embodiments.
  • inlet/outlet ports on a refrigerant path side are designed so that a common three-pronged joint 23 can be easily used. That is, the refrigerant paths can be formed only by the three-pronged joints 23 having the same shape. With this configuration, a component cost can be reduced without the need for newly preparing three-pronged joints having different shapes.
  • the gas header 24 is connected to all the U-shaped heat transfer pipes 22 of 2/3 of the rows in the third-column heat exchange unit 30 in the upper heat exchanger 12U.
  • the liquid-side refrigerant inlet/outlet ports 25 for the liquid refrigerant distributor are connected to all the U-shaped heat transfer pipes 22 of 1/3 of the rows in the first-column heat exchange unit 28 in the lower heat exchanger 12B.
  • the number of refrigerant paths connected to the gas header 24 in Fig. 9 is eight refrigerant paths, which is greater than six refrigerant paths (the maximum number of refrigerant paths) in the typical heat exchanger shown in Fig. 6 .
  • the pressure loss when the heat exchanger is used as the evaporator can be effectively reduced.
  • the number of refrigerant paths connected to the gas header can be increased only to the half of the total row number at the maximum.
  • the heat exchanger can be divided into the upper heat exchanger and the lower heat exchanger, and in addition, the number of refrigerant paths can be increased to the same number as the number of rows in the upper heat exchanger.
  • refrigerant passes through both the upper heat exchanger 12U and the lower heat exchanger 12B, and therefore, effects similar to those of the refrigerant paths shown in Fig. 7 are produced. That is, it is not necessary to consider refrigerant amount distribution adjustment in association with wind speed distribution, an adjustment pressure loss body design, and performance degradation due to insufficient adjustment.
  • refrigerant gas having flowed in from the gas header 24 passes through the refrigerant paths provided in the upper heat exchanger 12U (an upper 2/3 region of the heat exchanger 12) from the leeward side to the windward side, and thereafter, passes through a subcooling region provided at the lower heat exchanger 12B (a lower 1/3 region of the heat exchanger 12) from the leeward side to the windward side. Since the liquid-side refrigerant inlet/outlet ports 25 of the refrigerant paths provided in the region of the lower heat exchanger 12B are connected to the liquid refrigerant distributor, a head difference between the liquid-side inlet/outlet ports 25 can be reduced.
  • the subcooling region is provided in the lower heat exchanger 12B, so that the head difference can be eliminated, and in addition, the performance of the heat exchanger can be improved.
  • the present embodiment has been described using 12 rows of the heat exchanger in Fig. 9 , but actually, it is assumed that 60 rows of the heat exchanger are employed with a row pitch of 20 mm. In this case, the height of the heat exchanger is about 1.2 m. Since the same ratio is applied, the upper heat exchanger 12U has 40 rows, and the number of connection paths for the gas header 24 is also 40. Similarly, the lower heat exchanger 12B has 20 rows, and the number of liquid-side refrigerant inlet/outlet ports 25 is 10.
  • the upper heat exchanger 12U and the lower heat exchanger 12B are formed to be arranged in the height direction on an installation surface of a bottom installation board 18 on which the heat exchanger 12 is placed, and the total length of the upper heat exchanger 12U and the lower heat exchanger 12B in the height direction is preferably 1 m or more.
  • refrigerant divided into 10 paths after having passed through the expansion valve and the liquid refrigerant distributor flows into 10 liquid-side refrigerant inlet/outlet ports 25.
  • the refrigerant having passed through the first-column heat exchange unit 28 in the lower heat exchanger 12B through 10 refrigerant paths is branched such that each refrigerant path is branched into two paths by the three-pronged joint 23 when reaching the second-column heat exchange unit 29, and therefore, passes through two columns of the leeward-side heat exchange units 29, 30 through 20 refrigerant paths in the lower heat exchanger 12B.
  • each refrigerant path is further branched into two paths by the three-pronged joint 23, and the refrigerant passes through two columns of the leeward-side heat exchange units 29, 30 through 40 refrigerant paths in the upper heat exchanger. Since 40 refrigerant paths are connected to the gas header 24, the refrigerant flows into the four-way valve after having been joined together in the gas header.
  • the refrigerant paths can be formed in two stages of the upper heat exchanger and the lower heat exchanger while the number of refrigerant paths on a gas side is ensured.
  • the number of refrigerant paths in the lower heat exchanger can be reduced, a subcooling amount can be easily ensured and the cooling performance can be improved upon used as the condenser.
  • refrigerant is easily branched into two paths when flowing from the first-column heat exchange unit to the second-column heat exchange unit. Only the three-pronged joint is used for the first-column heat exchange unit and the second-column heat exchange unit in the upper heat exchanger and the lower heat exchanger, so that the number of refrigerant paths connected to the gas header can be easily increased to four times as many as the number of refrigerant paths of the liquid-side refrigerant inlet/outlet ports.
  • the three-pronged joint can be produced at a lower cost than that of a distributor or a distribution joint with three or more branches, and therefore, formation of the refrigerant paths only by the three-pronged joints leads to cost reduction.
  • the lowermost refrigerant path in which the wind speed is low is connected to the uppermost refrigerant path in which the wind speed is high.
  • the air volume received by one refrigerant path is relatively uniform between the upper and lower portions of the heat exchanger.
  • a refrigerant distribution amount is relatively uniform among the refrigerant paths, and therefore, the heating performance can be improved.
  • the small-diameter pipe is provided between the liquid refrigerant distributor and the liquid-side refrigerant path to adjust the distribution amount by, e.g., the length of the small-diameter pipe. For this reason, it is difficult to constantly adjust a distribution ratio to an optimal distribution ratio according to each refrigerant circulation amount. However, if the distribution ratio can be adjusted substantially uniformly, adjustment for each refrigerant path by the small-diameter pipe is not necessary. Even if the refrigerant circulation amount changes, performance close to an optimal level can be provided.
  • a high heating capacity and improved cooling performance can be achieved at a low cost under the influence of the liquid head in association with wind speed distribution in the heat exchanger and the height of the heat exchanger.
  • Fig. 11 shows refrigerant paths of the present embodiment.
  • the number of refrigerant paths is increased using the three-pronged joints 23 in the lower heat exchanger 12B.
  • a configuration is proposed, in which the number of paths is not increased using three-pronged joints 23 in a lower heat exchanger 12B and each refrigerant path is branched into two paths by the three-pronged joint 23 at a position before a first-column heat exchange unit 28 in an upper heat exchanger 12U such that the number of refrigerant paths is increased.
  • the refrigerant path is branched into two paths by the three-pronged joint 23 at the position immediately before the first-column heat exchange unit 28 in the upper heat exchanger 12U such that the number of refrigerant paths is increased.
  • the refrigerant path is further branched into two paths by the three-pronged joint 23 at a position immediately before the second-column heat exchange unit 29 such that the number of refrigerant paths is increased.
  • the flow of refrigerant is opposite to the flow of refrigerant as described above in the case of the evaporator. That is, gas refrigerant having flowed into the upper heat exchanger 12U from a gas header through eight refrigerant paths passes through two columns of the leeward-side heat exchange units 29, 30 in the upper heat exchanger 12U, and thereafter, passes through the first-column heat exchange unit 28 in the upper heat exchanger 12U through four refrigerant paths converged from eight refrigerant paths by the three-pronged joints 23.
  • the refrigerant having passed through the first-column heat exchange unit 28 in the upper heat exchanger 12U passes through two refrigerant paths converged from four refrigerant paths by the three-pronged joints 23, and flows into the lower heat exchanger 12B through two path connection pipes 26.
  • the refrigerant flows out of liquid-side refrigerant outlet ports 25 to a liquid refrigerant distributor through two refrigerant paths.
  • the same number of refrigerant paths as that of the liquid-side refrigerant inlet/outlet ports is formed across the entirety of the lower heat exchanger 12B, and therefore, a region where the flow speed of refrigerant is high is expanded and a subcooling amount is more easily ensured.
  • a cooling capacity can be improved in such a manner that the number of refrigerant paths is not increased in the lower heat exchanger, as described above.
  • Fig. 12 shows refrigerant paths of the present embodiment.
  • the number of refrigerant paths is increased using the three-pronged joints 23 in the lower heat exchanger 12B.
  • a configuration is proposed, in which the number of refrigerant paths is increased using three-pronged joints 23 in a lower heat exchanger 12B and is subsequently changed back to an initial number and each refrigerant path is branched into two paths by a three-pronged joint 23 at a position before a first-column heat exchange unit 28 in an upper heat exchanger 12U such that the number of refrigerant paths is increased.
  • a two-phase flow of refrigerant having passed through an expansion valve is first distributed by way of a liquid refrigerant distributor, and thereafter, slightly passes through a small-diameter pipe for distribution adjustment and flows into two liquid-side refrigerant inlet/outlet ports 25.
  • the refrigerant path is branched using the three-pronged joint 23 as already described above.
  • the refrigerant having passed through the third-column heat exchange unit 30 flows into one refrigerant path converged from two refrigerant paths by a three-pronged joint 23, and reaches the upper heat exchanger 12U through a path connection pipe 26.
  • the refrigerant path is branched into two paths again by a three-pronged joint 23, and the refrigerant flows into the first-column heat exchange unit 28 in the upper heat exchanger 12U through these two branched refrigerant paths.
  • Each refrigerant path is further branched into two paths by a three-pronged joint 23 between the first-column heat exchange unit 28 and the second-column heat exchange unit 20 in the upper heat exchanger 12U such that the number of refrigerant paths is increased.
  • the gasified refrigerant flows into a gas header 24 from eight (all) refrigerant paths of the third-column heat exchange unit 30 in the upper heat exchanger 12U.
  • the number of path connection pipes in the middle can be two which is the half of that in the case of the refrigerant paths described in the first embodiment, and therefore, an increase in a manufacturing cost can be restrained.
  • a lower refrigerant path in which the wind speed is low is connected to an upper refrigerant path in which the wind speed is high.
  • the air volume received by one refrigerant path is relatively uniform between the upper and lower portions of the heat exchanger.
  • a refrigerant distribution amount is relatively uniform among the refrigerant paths, and therefore, the heating performance can be improved.
  • the small-diameter pipe is provided between the liquid refrigerant distributor and the liquid-side refrigerant path to adjust the distribution amount by, e.g., the length of the small-diameter pipe. For this reason, it is difficult to constantly adjust a distribution ratio to an optimal distribution ratio according to each refrigerant circulation amount. However, if the distribution ratio can be adjusted substantially uniformly, adjustment for each refrigerant path by the small-diameter pipe is not necessary. Even if the refrigerant circulation amount changes, performance close to an optimal level can be provided.
  • the liquid-side refrigerant outlet in the lower heat exchanger is on the lower side of the U-shaped heat transfer pipe of the first-column heat exchange unit in the direction of the force of gravity. This is effective for enhancing drainability of liquid refrigerant from the heat transfer pipe by action of the force of gravity as much as possible and improving cooling performance when the heat exchanger is used as the condenser in the cooling operation.
  • the number of refrigerant paths (e.g., eight refrigerant paths) formed by the U-shaped heat transfer pipes of the upper heat exchanger 12U connected to the gas header 24 is preferably four times as many as the number of refrigerant paths (e.g., two refrigerant paths) formed by the U-shaped heat transfer pipes of the lower heat exchanger 12B connected to the liquid refrigerant distributor.
  • the heating capacity and the cooling performance can be improved as described above.
  • the present invention is not limited to the above-described embodiments, and includes various modifications.
  • the embodiments have been described above in detail in order to simply describe the present invention, and are not limited to those having all configurations described above.
  • part of the configuration of a certain embodiment can be replaced with the configuration of another embodiment, and the configuration of a certain embodiment can be added to the configuration of another embodiment.
  • addition/omission/replacement of other configurations can be made to part of the configuration of each embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)
EP20940548.9A 2020-06-15 2020-06-15 Unité extérieure pour dispositif de climatisation Pending EP4166858A4 (fr)

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JPH09196507A (ja) * 1996-01-19 1997-07-31 Yanmar Diesel Engine Co Ltd 空調用熱交換器
WO2013084432A1 (fr) * 2011-12-06 2013-06-13 パナソニック株式会社 Appareil de conditionnement d'air et dispositif à cycle de réfrigération
JP5951475B2 (ja) 2012-12-27 2016-07-13 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 空気調和装置及びそれに用いられる室外熱交換器
CN105283718B (zh) * 2013-06-13 2017-10-24 三菱电机株式会社 空调装置
CN105283712B (zh) * 2013-06-14 2017-12-12 三菱电机株式会社 空调的室外机和空调的室外机的制造方法
JP2015087074A (ja) * 2013-10-31 2015-05-07 ダイキン工業株式会社 空気調和装置の室外ユニット
JP6179414B2 (ja) * 2014-01-30 2017-08-16 ダイキン工業株式会社 冷凍装置の熱源ユニットの熱交換器、および、それを備えた熱源ユニット
JP6573484B2 (ja) * 2015-05-29 2019-09-11 日立ジョンソンコントロールズ空調株式会社 熱交換器
JP6681991B2 (ja) * 2016-08-09 2020-04-15 三菱電機株式会社 熱交換器及びこの熱交換器を備えた冷凍サイクル装置

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JP7374321B2 (ja) 2023-11-06
CN115298486A (zh) 2022-11-04
WO2021255780A1 (fr) 2021-12-23
JPWO2021255780A1 (fr) 2021-12-23

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