EP3524917B1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP3524917B1
EP3524917B1 EP16918274.8A EP16918274A EP3524917B1 EP 3524917 B1 EP3524917 B1 EP 3524917B1 EP 16918274 A EP16918274 A EP 16918274A EP 3524917 B1 EP3524917 B1 EP 3524917B1
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EP
European Patent Office
Prior art keywords
air
heat exchanger
vortex generator
fan
heat transfer
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.)
Active
Application number
EP16918274.8A
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English (en)
French (fr)
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EP3524917A1 (de
EP3524917A4 (de
Inventor
Shinya Higashiiue
Akira Ishibashi
Tsuyoshi Maeda
Daisuke Ito
Shin Nakamura
Ryota AKAIWA
Akira YATSUYANAGI
Yuta KOMIYA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP3524917A1 publication Critical patent/EP3524917A1/de
Publication of EP3524917A4 publication Critical patent/EP3524917A4/de
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Publication of EP3524917B1 publication Critical patent/EP3524917B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • F25B39/02—Evaporators
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the present invention relates to a refrigeration cycle apparatus in which the heat exchange performance of a heat exchanger is improved, according to claim 1.
  • the fin-and-tube heat exchanger includes heat transfer tubes through which refrigerant flows, and heat transfer fins connected to the heat transfer tubes.
  • a fin-and-tube heat exchanger whose heat exchange performance is improved is proposed.
  • Patent Literature 1 describes a fin-and-tube heat exchanger including a plurality of rectangular heat transfer fins and a plurality of heat transfer tubes.
  • the plurality of heat transfer fins are disposed such that their longitudinal direction coincides with a vertical direction.
  • the plurality of heat transfer fins are arranged side by side at predetermined intervals in a lateral direction substantially perpendicular to the flow direction of air which is sent by a fan.
  • the heat transfer tubes are arranged side by side at predetermined intervals in the vertical direction (the longitudinal direction of the heat transfer fins) and extend through the heat transfer fins in the direction in which the fins are arranged side by side.
  • each of heat transfer fins of the heat exchanger described in Patent Literature 1 a plurality of triangular cut and raised pieces which are called winglets are formed in part of each heat transfer fin which is located in the vicinity of an end portion located on an upstream side in the flow direction of air.
  • winglets a plurality of triangular cut and raised pieces which are called winglets are formed in part of each heat transfer fin which is located in the vicinity of an end portion located on an upstream side in the flow direction of air.
  • US4607689A discloses a reheater for a steam power plant generally comprises a tube plate, a header including a high-temperature chamber and a low-temperature chamber defined outwardly of the tube plate, and a number of heat-exchanger tubes bent into U-shapes, both ends of which are secured to the tube plate.
  • the reheater further comprises nozzle members, each having a flange portion, inserted into the upstream ends of the heat-exchanger tubes, respectively, and a bellmouth plate having a number of holes, secured detachably to the tube plate such that the holes align with the nozzle members.
  • the flange portions of the nozzle members are secured firmly between the bellmouth plate and the tube plate.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. Hei 11-108575
  • a fin-and-tube heat exchanger of a refrigeration cycle apparatus is used as an evaporator which cools air flowing into the heat exchanger using refrigerant flowing through heat transfer tubes.
  • the heat transfer tubes and heat transfer fins are cooled by the refrigerant flowing through the heat transfer tubes to a temperature lower than that of the air flowing into the heat exchanger. Therefore, the air flowing into the heat exchanger is cooled by the heat transfer tubes and the heat transfer fins having the temperature lower than that of the air.
  • dew condensation occurs on surfaces of the heat transfer tubes and the heat transfer fins.
  • the vicinity of an end portion of the heat transfer fin that is located on an upstream side in the flow direction of air is a region from which cooling of the air flowing into the heat exchanger is started. Therefore, dew condensation easily occurs at this region. Furthermore, when the temperature of the air flowing into the heat exchanger is low, the temperature of the heat transfer fin is far lower than that of the air. Therefore, dews adhering to the vicinity of the end portion of the heat transfer fin that is located on the upstream side in the flow direction of air are frozen to form frost in the vicinity of the end portion.
  • winglets which function as vortex generating units are formed at respective heat transfer fins.
  • the vortex generating units and the heat transfer fins are formed integrally with each other. Therefore, in the case where the heat exchanger described in Patent Literature 1 is used as the evaporator, the winglets functioning as the vortex generating units are cooled by the refrigerant flowing through the heat transfer tubes to a temperature equal to that of part of the heat transfer fins which is other than part of the heat transfer fins in which the winglets are formed.
  • the part of the heat transfer fins in which the winglets are formed is the vicinity of end portions of the heat transfer fins that are located on an upstream side in the flow direction of air, that is, a region in which dew condensation easily occurs. Therefore, in the case where the heat exchanger described in Patent Literature 1 is used as the evaporator under a condition in which the temperature of the air flowing into the heat exchanger is low, frost is formed on the winglets functioning as the vortex generating units. Thus, it is hard to generate a vortex with the winglets. Accordingly, the heat exchanger described in Patent Literature 1 cannot improve the heat exchange performance in the case where the heat exchanger is used as the evaporator. That is, the conventional refrigeration cycle apparatus cannot improve the heat exchange performance of the evaporator.
  • an object of the invention is to obtain a refrigeration cycle apparatus in which the heat exchange performance of an evaporator can be improved.
  • the vortex generator functioning as a vortex generating unit is formed independently of the evaporator. Therefore, cooling of the vortex generator by refrigerant flowing through the heat transfer tubes of the evaporator can be reduced compared with the conventional heat exchanger. That is, in the refrigeration cycle apparatus according to the embodiment of the present invention, formation of frost on the vortex generator can be reduced compared with the conventional heat exchanger.
  • an air flow with vortexes generated at the vortex generator can be supplied to the evaporator even the temperature of air flowing into the evaporator is low. Therefore, the heat exchange performance of the evaporator can be improved compared with the conventional heat exchanger.
  • a refrigeration cycle apparatus according to the present invention will be described by referring to by way of example an air-conditioning apparatus which is a refrigeration cycle apparatus.
  • Fig. 1 is a refrigerant circuit diagram illustrating an air-conditioning apparatus 100 according to embodiment 1 of the present invention. It should be noted that outlined arrows in Fig. 1 indicate the flow direction of air.
  • the air-conditioning apparatus 100 includes a compressor 1, a heat exchanger 2 functioning as an indoor heat exchanger, a fan 2a which sends indoor air to the heat exchanger 2, an expansion device 3, a heat exchanger 10 functioning as an outdoor heat exchanger, a fan 30 which sends outdoor air to the heat exchanger 10, a flow switching device 4, etc.
  • the compressor 1, the heat exchanger 2, the expansion device 3, the heat exchanger 10 and the flow switching device 4 are connected to each other by refrigerant pipes, whereby a refrigerant circuit is formed.
  • the compressor 1 compresses refrigerant.
  • the refrigerant compressed by the compressor 1 is discharged, and sent to the flow switching device 4.
  • a rotary compressor, a scroll compressor, a screw compressor or a reciprocating compressor can be applied as the compressor 1, a rotary compressor, a scroll compressor, a screw compressor or a reciprocating compressor can be applied.
  • the heat exchanger 2 is an indoor heat exchanger; and functions as a condenser during a heating operation, and functions as an evaporator during a cooling operation.
  • the heat exchanger 2 is a fin-and-tube heat exchanger.
  • the expansion device 3 expands refrigerant having flowed out of the heat exchanger 2 or the heat exchanger 10 to reduce the pressure of the refrigerant.
  • an electric expansion valve which can adjust the flow rate of the refrigerant is used. It should be noted that not only the electric expansion valve but for example, a mechanical expansion valve that employs a diaphragm as a pressure receiving portion or a capillary tube can be applied as the expansion device 3.
  • the heat exchanger 10 is an outdoor heat exchanger; and functions as an evaporator during the heating operation, and functions as a condenser during the cooling operation.
  • the heat exchanger 10 is a fin-and-tube heat exchanger, and a detailed configuration thereof will be described later.
  • the flow switching device 4 is a four-way valve, and switches the refrigerant passage to be used, between a refrigerant passage for the heating operation and that for the cooling operation. More specifically, during the heating operation, the flow switching device 4 switches the refrigerant passage in such a way as to connect a discharge port of the compressor 1 to the heat exchanger 2 and connect a suction port of the compressor 1 to the heat exchanger 10. During the cooling operation, the flow switching device 4 switches the refrigerant passage in such a way as to connect the discharge port of the compressor 1 to the heat exchanger 10 and connect the suction port of the compressor 1 to the heat exchanger 2.
  • the fan 2a is located close to the heat exchanger 2, and sends indoor air to the heat exchanger 2 as described above.
  • the fan 30 is located close to the heat exchanger 10, and sends outdoor air to the heat exchanger 10 as described above.
  • fans such as a propeller fan, a cross-flow fan, a sirocco fan and a turbofan can be used as the fan 2a and the fan 30.
  • the air-conditioning apparatus 100 is provided with a vortex generator 20 which is located upstream of the heat exchanger 10 in the flow direction of air which is sent to the heat exchanger 10 by the fan 30.
  • a detailed configuration of the vortex generator 20 will be described later together with that of the heat exchanger 10.
  • the above components of the air-conditioning apparatus 100 are provided in an outdoor unit 101 or an indoor unit 102.
  • the compressor 1, the expansion device 3, the flow switching device 4, the heat exchanger 10, the vortex generator 20 and the fan 30 are provided in the outdoor unit 101.
  • the heat exchanger 2 and the fan 2a are provided in the indoor unit 102.
  • Fig. 2 is a side view illustrating the heat exchanger 10 and the vortex generator 20 of the air-conditioning apparatus 100 according to embodiment 1 of the present invention.
  • Fig. 3 is a view taken as seen from a direction indicated by an arrow A in Fig. 2 .
  • Fig. 4 is a view taken as seen from a direction indicated by an arrow B in Fig. 2 . It should be noted that outlined arrows in Figs. 2 and 4 indicate flow directions of air (outdoor air) which is sent by the fan 30.
  • the heat exchanger 10 is a fin-and-tube heat exchanger, and includes a plurality of heat transfer tubes 12 through which the refrigerant flows, and a plurality of heat transfer fins 11 connected to the heat transfer tubes 12.
  • the heat transfer fins 11 are rectangular plate-shaped elements.
  • the plurality of heat transfer fins 11 are provided such that their longitudinal direction coincides with a vertical direction.
  • the plurality of heat transfer fins 11 are arranged side by side at predetermined intervals in a lateral direction substantially perpendicular to the flow direction of air from the fan 30.
  • through holes are provided in the heat transfer fins 11, and allow the heat transfer tubes 12 to be inserted through the through holes. It should be noted that each heat transfer fin 11 may be formed into a corrugated shape to enhance the strength of each heat transfer fin 11.
  • the plurality of heat transfer tubes 12 are circular tubes.
  • the heat transfer tubes 12 are inserted into the through holes formed in the heat transfer fins 11.
  • the heat transfer tubes 12 extend through the heat transfer fins 11 in the direction in which the heat transfer fins 11 are arranged side by side. That is, each of the heat transfer tubes 12 and an outer edge of the through hole of an associated one of the heat transfer fins 11 are connected to each other.
  • the heat transfer tubes 12 are not limited to the circular tubes.
  • flat tubes having elongated cross sections may be used as the heat transfer tubes 12.
  • the elongated cross section is a cross section which is long in a lateral direction and short in a vertical direction, for example, an oval cross section.
  • Fig. 5 is a side view illustrating another example of the heat exchanger 10 of the air-conditioning apparatus 100 according to embodiment 1 of the present invention.
  • cut and raised pieces called slits, louvers, winglets or the like are formed at heat transfer fins to improve the heat exchange performance.
  • cut and raised pieces are not formed at the heat transfer fins 11 of the heat exchanger 10 according to embodiment 1. There is because the heat exchange performance of the heat exchanger 10 is improved by providing the vortex generator 20 as described later, and cut and raised pieces thus do not need to be formed at the heat transfer fins 11.
  • the vortex generator 20 is located upstream of the heat exchanger 10 in the flow direction of air which is sent from the fan 30 to the heat exchanger 10.
  • the vortex generator 20 is formed independently of the heat exchanger 10. More specifically, as illustrated in Figs. 2 and 4 , the vortex generator 20 has a plurality of protrusions 22.
  • a plurality of protrusions 22 are formed by cutting and raising respective portions of each of plate-shaped bases 21. That is, the protrusions 22 are cut and raised pieces.
  • the bases 21 each formed to include protrusions 22 are provided side by side at predetermined intervals, thereby forming the vortex generator 20.
  • the vortex generator 20 is provided in contact with the heat transfer fins 11 of the heat exchanger 10.
  • the vortex generator 20 having the above configuration, vortexes are generated when air sent by the fan 30 flows into space between the bases 21 and impinges on the protrusions 22. Moreover, in embodiment 1, the thickness of the vortex generator 20 is smaller than that of the heat exchanger 10 in the flow direction of air which is sent by the fan 30. Since the vortex generator 20 and the heat exchanger 10 are formed as described above, the air-conditioning apparatus 100 can be made compact.
  • the configuration of the vortex generator 20 is not limited to the above configuration.
  • the cut and raised protrusions 22 may be each formed in a shape other than the triangular shape.
  • protrusions 22 are formed by cutting and raising each base 21 from the upstream side toward the downstream side in the flow direction of air which is sent by the fan 30.
  • the direction in which the protrusions 22 are cut and raised is not limited to such a direction.
  • the protrusions 22 may be formed by cutting and raising the base 21 from the downstream side to the upstream side in the flow direction of air from the fan 30.
  • the method for forming the protrusions 22 is not limited to the above cutting and raising.
  • components formed independently of the base 21 may be attached to the base 21 by welding or the like, and used as protrusions 22.
  • the direction in which the plurality of bases 21 are arranged side by side coincides with the direction in which the heat transfer fins 11 are arranged side by side.
  • these directions may differ from each other.
  • the plurality of bases 21 may be disposed in a lattice pattern.
  • the vortex generator 20 may include a plurality of wires 23 disposed at predetermined intervals, instead of using the protrusions 22.
  • the plurality of wires 23 are arranged in a lattice pattern.
  • the vortex generator 20 may be formed of wires 23a or wires 23b arranged at predetermined intervals in a single direction. This is because vortexes are generated when air sent by the fan 30 impinges on the wires 23. That is, it suffices that the vortex generator 20 has a structure in which vortexes can be generated when air sent by the fan 30 passes through the vortex generator 20. It should be noted that Fig.
  • FIG. 6 is a side view illustrating another example of the vortex generator 20 of the air-conditioning apparatus 100 according to embodiment 1 of the present invention, and also that Fig. 6 illustrates the example of the vortex generator 20 as seen in the flow direction of the air which is sent from the fan 30 to the vortex generator 20. That is, the direction from which the above example of the vortex generator 20 is seen in Fig. 6 is a direction in which the example of the vortex generator 20 is seen from a left side in Fig. 2 .
  • the air-conditioning apparatus 100 performs the heating operation
  • the flow switching device 4 switches the refrigerant passage to be used to a refrigerant passage indicated by solid lines in Fig. 1 .
  • the compressor 1, the fan 2a and the fan 30 are driven to start the heating operation.
  • high-temperature and high-pressure gas refrigerant is discharged from the compressor 1.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 flows into the heat exchanger 2 which is the indoor heat exchanger, via the flow switching device 4.
  • the heat exchanger 2 functions as the condenser. Therefore, in the heat exchanger 2, the high-temperature and high-pressure gas refrigerant flowing in the heat exchanger 2 heats indoor air sent by the fan 2a, thereby heating a target space to be air-conditioned, for example, the inner space of a room. Further, when the high-temperature and high-pressure gas refrigerant flowing in the heat exchanger 2 exchanges heat with the indoor air sent by the fan 2a, the refrigerant is condensed into high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant having flowed out of the heat exchanger 2 is changed into low-temperature and low-pressure two-phase gas-liquid refrigerant by the expansion device 3.
  • the low-temperature and low-pressure two-phase gas-liquid refrigerant flows into the heat exchanger 10 which is the outdoor heat exchanger.
  • the heat exchanger 10 functions as the evaporator. Therefore, in the heat exchanger 10, the refrigerant flowing in the heat transfer tubes 12 of the heat exchanger 10 removes heat from outdoor air sent by the fan 30. In other words, the refrigerant flowing in the heat transfer tubes 12 of the heat exchanger 10 cools the outdoor air sent by the fan 30.
  • the refrigerant flowing in the heat transfer tubes 12 of the heat exchanger 10 exchanges heat with the outdoor air sent by the fan 30, the refrigerant is evaporated into low-pressure gas refrigerant. Then, the low-pressure gas refrigerant having flowed out of the heat exchanger 10 is sucked into the compressor 1 via the flow switching device 4, and is compressed into high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant is re-discharged from the compressor 1.
  • the vortex generator 20 is located upstream of the heat exchanger 10 in the flow direction of air which is sent from the fan 30 to the heat exchanger 10. Therefore, vortexes are generated when the air sent by the fan 30 flows into the vortex generator 20 and impinges on the protrusions 22. Thus, an air flow with the vortexes generated at the vortex generator 20 can be supplied to the heat exchanger 10. Accordingly, an air flow in the vicinity of the surfaces of the heat transfer fins 11 and the heat transfer tubes 12 of the heat exchanger 10 is disturbed. As a result, the heat exchange performance of the heat exchanger 10 can be improved.
  • vortex generating units are formed by, for example, cutting and raising heat transfer fins, that is, they are formed integrally with the heat transfer fins, to improve the heat exchange performance.
  • the vortex generating units are formed integrally portions of the heat transfer tubes are adjacent to end portions thereof which are located on an upstream side in the flow direction of air.
  • the heat exchange performance cannot be improved by the vortex generating units.
  • the heat transfer tubes and the heat transfer fins are cooled by refrigerant flowing through the heat transfer tubes to a temperature lower than that of air flowing into the evaporator. Therefore, the air flowing into the evaporator is cooled by the heat transfer tubes and the heat transfer fins having the temperature lower than that of the air.
  • the air flowing into the evaporator is cooled to a temperature lower than or equal to a dew-point temperature, dew condensation occurs on surfaces of the heat transfer tubes and the heat transfer fins. That is, the portions of the heat transfer fins that are adjacent to the end portions thereof on the upstream side in the flow direction of air are regions from which cooling of the air flowing into the heat exchanger is started.
  • the vortex generating units is cooled by refrigerant flowing through the heat transfer tubes to a temperature equal to that of part of the heat transfer fins which is other than part of the heat transfer fins in which the vortex generating units are located.
  • the portion of the above heat transfer fin in which the associated vortex generating unit is located is a portion of the heat transfer fin which is adjacent to an end portion thereof which is located on an upstream side in the flow direction of air, that is, a region where dew condensation easily occurs.
  • frost is formed on the vortex generating units under a condition in which the temperature of air flowing into the heat exchanger is low. It is therefore hard to generate a vortex using the vortex generating units. Accordingly, in the conventional heat exchanger in which the vortex generating units are formed integrally with the heat transfer fins, the heat exchange performance cannot be improved.
  • the vortex generator 20 is formed independently of the heat exchanger 10. Therefore, although the vortex generator 20 is in contact with the heat transfer fins 11 of the heat exchanger 10, the rate of heat transfer between the heat transfer fins 11 and the vortex generator 20 is lower than that between the heat transfer fins and the vortex generating units of the conventional heat exchanger. That is, cooling of the vortex generator 20 by the refrigerant flowing through the heat transfer tubes 12 of the heat exchanger 10, which occurs when the heat exchanger 10 is used as the evaporator, can be reduced compared with the conventional heat exchanger. That is, in the air-conditioning apparatus 100 according to embodiment 1, formation of frost on the vortex generator 20 can be reduced as compared with the conventional heat exchanger.
  • cut and raised pieces are not formed. If cut and raised pieces are formed at a heat transfer fin 11, the space between the heat transfer fin 11 having the cut and raised pieces and a heat transfer fin 11 adjacent to the heat transfer fin 11 is reduced. Therefore, if cut and raised pieces are formed at the heat transfer fin 11, the space between the adjacent heat transfer fins 11 is easily clogged by formed frost. In other words, in the heat exchanger 10 according to embodiment 1, it is possible to prevent or reduce clogging of the space between adjacent heat transfer fins 11, which would be caused by formed frost, because cut and raised pieces are not formed at the heat transfer fins 11.
  • the heat exchanger 10 according to embodiment 1 because of formation of no cut and raised pieces, dews adhering to the heat transfer fins 11 slide downward without being retained by surface tension or the like, and are thus easily discharged from the heat exchanger 10. On this point as well, in the heat exchanger 10 according to embodiment 1, it is possible to prevent or reduce clogging of the space between the adjacent heat transfer fins 11, which would be caused by formation of frost. Thus, the heat exchange performance of the heat exchanger 10 according to embodiment 1 can further be improved because cut and raised pieces are not formed at the heat transfer fins 11.
  • the flow switching device 4 switches the refrigerant passage to be used, to a refrigerant passage indicated by broken lines as indicated in Fig. 1 .
  • the compressor 1, the fan 2a and the fan 30 are driven to start the cooling operation.
  • high-temperature and high-pressure gas refrigerant is discharged from the compressor 1.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 flows into the heat exchanger 10 which is the outdoor heat exchanger, via the flow switching device 4.
  • the heat exchanger 2 functions as the condenser. Therefore, in the heat exchanger 10, the refrigerant flowing in the heat transfer tubes 12 of the heat exchanger 10 transfers heat to outdoor air sent by the fan 30. Furthermore, when the high-temperature and high-pressure gas refrigerant flowing in the heat transfer tubes 12 of the heat exchanger 10 exchanges heat with the outdoor air sent by the fan 30, the refrigerant is condensed into high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant having flowed out of the heat exchanger 10 is changed into low-temperature and low-pressure two-phase gas-liquid refrigerant by the expansion device 3.
  • the low-temperature and low-pressure two-phase gas-liquid refrigerant flows into the heat exchanger 2 which is the indoor heat exchanger.
  • the heat exchanger 2 functions as the evaporator. Therefore, in the heat exchanger 2, the low-temperature and low-pressure two-phase gas-liquid refrigerant flowing in the heat exchanger 2 cools the indoor air sent by the fan 2a, thereby cooling the target space to be air-conditioned, such as the inner space of the room.
  • the refrigerant flowing in the heat exchanger 2 exchanges heat with indoor air sent by the fan 2a
  • the refrigerant is evaporated into low-pressure gas refrigerant.
  • the low-pressure gas refrigerant having flowed out of the heat exchanger 2 is sucked into the compressor 1 via the flow switching device 4 and is compressed into high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant is re-discharged from the compressor 1.
  • the vortex generator 20 is located upstream of the heat exchanger 10 in the flow direction of air which is sent from the fan 30 to the heat exchanger 10 from the fan 30. Therefore, vortexes are generated when the air sent by the fan 30 flows into the vortex generator 20 and impinges on the protrusions 22. Thus, an air flow with the vortexes generated at the vortex generator 20 can be supplied to the heat exchanger 10. Accordingly, an air flow in the vicinity of the surfaces of the heat transfer fins 11 and the heat transfer tubes 12 of the heat exchanger 10 is disturbed, as a result of which the heat exchange performance of the heat exchanger 10 can be improved during the cooling operation as well.
  • the air-conditioning apparatus 100 includes: the heat exchanger 10 which includes the heat transfer tubes 12 through which the refrigerant flows and the heat transfer fins 11 connected to the heat transfer tubes 12, and functions as the evaporator; the fan 30 which sends air to the heat exchanger 10; and the vortex generator 20 formed independently of the heat exchanger 10 located upstream of the heat exchanger 10 in the flow direction of air from the fan 30. Therefore, in the air-conditioning apparatus 100 according to embodiment 1, it is possible to reduce cooling of the vortex generator 20 by the refrigerant flowing in the heat transfer tubes 12 of the heat exchanger 10, which occurs when the heat exchanger 10 is used as the evaporator, as compared with the conventional heat exchanger. That is, in the air-conditioning apparatus 100 according to embodiment 1, it is possible to reduce formation of frost on the vortex generator 20 as compared with the conventional heat exchanger.
  • the air-conditioning apparatus 100 when the heat exchanger 10 is used as the evaporator, an air flow with vortexes generated at the vortex generator 20 can be supplied to the heat exchanger 10 continuously and stably even when the temperature of air flowing into the heat exchanger 10 is low. Therefore, the heat exchange performance of the heat exchanger 10 can be improved as compared with the conventional heat exchanger. In other words, the air-conditioning apparatus 100 according to embodiment 1 can be operated while saving energy because the heat exchange performance of the heat exchanger 10 which functions as the evaporator can be improved.
  • the heat exchanger 10 is used as the outdoor heat exchanger, but may be used as the indoor heat exchanger. If it is used as the indoor heat exchanger, it suffices that the heat exchanger 2 is used as the outdoor heat exchanger. That is, it suffices that the heat exchanger 10, the vortex generator 20 and the fan 30 are provided in the indoor unit 102, and the heat exchanger 2 and the fan 2a are provided in the outdoor unit 101 instead. Furthermore, the vortex generator 20 may be located upstream of both the heat exchanger 2 and the heat exchanger 10 in the flow direction of air.
  • the air-conditioning apparatus 100 according to embodiment 1 is merely an example of the refrigeration cycle apparatus according to the present invention.
  • the present invention can be adopted in general refrigeration cycle apparatuses each including a fin-and-tube heat exchanger as an evaporator. That is, the present invention can be put to practical use by providing the vortex generator 20 upstream of the fin-and-tube evaporator in the flow direction of air.
  • the vortex generator 20 is in contact with the heat transfer fins 11 of the heat exchanger 10.
  • the arrangement of the vortex generator 20 and the heat exchanger 10 is not limited to such arrangement.
  • the vortex generator 20 and the heat transfer fins 11 of the heat exchanger 10 may be provided, with space provided between the vortex generator 20 and the heat transfer fins 11.
  • Fig. 7 is a side view illustrating the vicinity of the heat exchanger 10 and the vortex generator 20 of the air-conditioning apparatus 100 according to embodiment 2 of the present invention.
  • Fig. 8 is a diagram illustrating the temperatures of the heat transfer fins 11 of the heat exchanger 10 and the vortex generator 20 when the heat exchanger 10 of the air-conditioning apparatus 100 according to embodiment 2 of the present invention is used as the evaporator. It should be noted that outlined arrows in Figs. 7 and 8 indicate flow directions of air from the fan 30.
  • spaces 41 each having a width L are provided between the heat transfer fins 11 in the heat exchanger 10 and the vortex generator 20.
  • the heat transfer fins 11 of the heat exchanger 10 are cooled by the refrigerant flowing through the heat transfer tubes 12 connected to the heat transfer fins 11. Furthermore, air which is sent by the fan 30 to the spaces between the heat transfer fins 11 is cooled thereby, and the temperature of the air thus decreases as the air flows toward the downstream side. That is, the temperature of each heat transfer fin 11 varies from one location to another such that the closer part of the heat transfer fin 11 to the downstream side in the flow of air from the fan 30, the lower the temperature of the part of the heat transfer fin 11, since the part of the heat transfer fin 11 is harder to heat with the air as the part of the heat transfer fin 11 is closer to the downstream side.
  • a straight line C indicated by a solid line in Fig. 8 the surface temperature of the heat transfer fin 11 decreases from the upstream side to the downstream side in the flow direction of air from the fan 30.
  • the temperature of the vortex generating unit is close to or equal to that of the other portion of the heat transfer fin. That is, the vortex generating unit is cooled by the refrigerant flowing through the heat transfer tubes, and as shown by a straight line D indicated by a two-dot chain line in Fig. 8 , the temperature of the vortex generating unit decreases from the upstream side to the downstream side in the flow direction of air, and the straight line D connects the straight line C.
  • the space 41 is provided between each of the heat transfer fins 11 of the heat exchanger 10 and the vortex generator 20. Therefore, the vortex generator 20 is hardly cooled by the refrigerant flowing through the heat transfer tubes 12.
  • the temperature of the vortex generator 20 is equal to an outdoor air temperature (the temperature of air to be sent to the heat exchanger 10 by the fan 30, that is, that of air which has not yet flowed into the heat exchanger 10).
  • the width L of each space 41 should be 1 mm to 5 mm. This is because if the width L is excessively long, a vortex flow generated at the vortex generator 20 does not reach the heat exchanger 10, and if the width L is excessively short, dews adhering to the heat transfer fin 11 of the heat exchanger 10 may adhere to the vortex generator 20.
  • the temperature of the vortex generator 20 is a temperature between the temperature of the vortex generator 20 in embodiment 2 (straight line E in Fig. 8 ) and the temperature of each of the vortex generating units of the conventional heat exchanger (straight line D in Fig. 8 ). That is, in the air-conditioning apparatus 100 according to embodiment 2, when the heat exchanger 10 is used as the evaporator, frost is not easily formed on the vortex generator 20, as compared with that of embodiment 1.
  • an air flow with vortexes generated at the vortex generator 20 can be supplied to the heat exchanger 10 continuously and stably for a longer period than in embodiment 1. Therefore, the heat exchange performance of the heat exchanger 10 can be further improved.
  • the air-conditioning apparatus 100 includes spacers 40 which are provided between the heat transfer fins 11 of the heat exchanger 10 and the vortex generator 20, and are formed independent of the heat transfer fin 11 and the vortex generator 20.
  • the spaces 41 are provided between the heat transfer fins 11 of the heat exchanger 10 and the vortex generator 20 by interposing the spacers 40 between the heat transfer fins 11 of the heat exchanger 10 and the vortex generator 20.
  • the spacers 40 be made of material such as a resin, which have a lower thermal conductivity than those of the heat transfer fins 11 of the heat exchanger 10 and the vortex generator 20. It should be noted that that the number and shapes of the spacers 40 are not particularly limited.
  • the width L of each of the spaces 41 can be more easily managed because the spaces 41 are provided by interposing the spacers 40 between the heat transfer fins 11 of the heat exchanger 10 and the vortex generator 20.
  • the dimension of each of the spaces 41 can be prevented from differing from a set value due to, for example, an error in provision of the heat exchanger 10 and the vortex generator 20.
  • the width L of each of the spaces 41 between the heat transfer fins 11 of the heat exchanger 10 and the vortex generator 20 is accurately set, whereby an air flow disturbed in a desired state by the vortex generator 20 can be supplied to the heat exchanger 10.
  • the heat exchange performance of the heat exchanger 10 can be further improved.
  • the heat exchanger 10 when used as the evaporator, the cooling of the vortex generator 20 by the heat transfer fins 11 is reduced via the spacers 40, since the spacers 40 are made of material having a lower thermal conductivity than those of the heat transfer fins 11 of the heat exchanger 10 and the vortex generator 20. Therefore, frost is not easily formed on the vortex generator 20 as compared with embodiment 1 even if the heat transfer fins 11 are thermally connected to the vortex generator 20 via the spacers 40, as compared with embodiment 1.
  • an air flow with vortexes generated at the vortex generator 20 can be supplied to the heat exchanger 10 continuously and stably for a longer time period than in embodiment 1. Accordingly, the heat exchange performance of the heat exchanger 10 can be further improved.
  • each of the spacers 40 may be formed integral with the vortex generator 20.
  • end portions of the bases 21 in the vortex generator 20 that are closer to the heat exchanger 10 may be partially projected toward the heat exchanger 10, and be used as the spacers 40.
  • the spacers 40 may be formed integral with the respective heat transfer fins 11 of the heat exchanger 10. That is, end portions of the heat transfer fins 11 that are located closer to the vortex generator 20 may be partially projected toward the heat exchanger 10, and used as the spacers 40.
  • Fig. 9 is a side view illustrating another example of the vortex generator 20 of the air-conditioning apparatus 100 according to embodiment 2 of the present invention.
  • Fig. 10 is a side view illustrating another example of the heat exchanger 10 of the air-conditioning apparatus 100 according to embodiment 2 of the present invention.
  • the width L of each of the spaces 41 between the heat transfer fins 11 of the heat exchanger 10 and the vortex generator 20 can be set accurately.
  • an air flow disturbed in a desired state by the vortex generator 20 can be supplied to the heat exchanger 10, thus further improving the heat exchange performance of the heat exchanger 10.
  • the heat transfer fins 11 of the heat exchanger 10 are in contact with the vortex generator 20 at locations corresponding to the spacers 40.
  • the contact area between each of the heat transfer fins 11 and the vector generator 20 is smaller than that in embodiment 1.
  • the vortex generator 20 is not easily cooled by the heat transfer fins 11 of the heat exchanger 10, as compared with embodiment 1. That is, frost is not easily formed on the vortex generator 20.
  • the air-conditioning apparatus 100 according to embodiment 2 even in the case where the spacers 40 are formed as illustrated in Fig. 9 or Fig. 10 , an air flow with vortexes generated at the vortex generator 20 can be supplied to the heat exchanger 10 continuously and stably for a longer time period than in embodiment 1. Accordingly, the heat exchange performance of the heat exchanger 10 can be further improved.
  • fans such as a propeller fan, a cross-flow fan, a sirocco fan and a turbofan
  • the fan 30 which sends air to the heat exchanger 10 and the vortex generator 20 as described above with respect to embodiments 1 and 2.
  • more stable vortexes can be generated at the vortex generator 20 by sending a comparatively regulated air flow to the vortex generator 20, and as a result the heat exchange performance of the heat exchanger 10 can be improved.
  • embodiment 3 an example of a preferred arrangement of the heat exchanger 10 and the vortex generator 20, which varies in accordance with the type of the fan 30, will be described. It should be noted that with respect to embodiment 3, matters which are not particularly described are the same as or similar to those of embodiment 1 or 2, and functions and components which are identical to those of embodiment 1 or 2 will be denoted by the same reference signs.
  • Fig. 11 is a side view illustrating an example of the air-conditioning apparatus 100 according to embodiment 3 of the present invention. It should be noted that an outlined arrow in Fig. 11 indicates the flow direction of air from the fan 30.
  • the air-conditioning apparatus 100 as illustrated in Fig. 11 employs a propeller fan 31 as the fan 30.
  • An air flow on an outlet side of the propeller fan 31 flows while swirling about a rotation axis of the propeller fan 31.
  • an air flow on an inlet side of the propeller fan 31 is regulated, as compared with the air flow on the outlet side. Therefore, in the case where the propeller fan 31 is employed as the fan 30, it is preferable that the propeller fan 31 be provided downstream of the heat exchanger 10 in the flow direction of air from the propeller fan 31.
  • a comparatively regulated air flow can be supplied to the vortex generator 20, as a result of which stable vortexes can be generated at the vortex generator 20, and the heat exchange performance of the heat exchanger 10 can be improved.
  • Fig. 12 is a view additionally illustrating a velocity distribution of an air flow flowing to the vortex generator 20 in the air-conditioning apparatus 100 as illustrated in Fig. 11 .
  • a comparatively regulated air flow can be supplied to the vortex generator 20.
  • the velocity of the flow of air flowing to the vortex generator 20 varies from one location to another in the vortex generator 20.
  • the velocity of an air flow is lower at an area of the vortex generator 20 where an air flow to be sucked toward the outer periphery of the propeller fan 31 passes than at an area of the vortex generator 20 where an air flow to be sucked toward the center of the propeller fan 31 passes. Furthermore, a vortex is not easily generated in the area where the air velocity is low, as compared with in the area where the air velocity is higher than that of the area where the air velocity is low.
  • the number of generated vortexes is small in an air flow which passes through the area of the vortex generator 20 where the air velocity is low, and in an area of the heat exchanger 10 where the above air flow passes, the heat exchange performance is decreased, as compared with an area of the heat exchanger 10 where an air flow passes at a high velocity.
  • a large number of protrusions 22 may be provided in a given area of the vortex generator 20 than in an area where the air velocity is higher than that at the given area.
  • vortexes equivalent to vortexes which can be generated even in the area of the vortex generator 20 where the air velocity is high can be generated in the area of the vortex generator 20 where the air velocity is low.
  • the heat exchange performance of the heat exchanger 10 can be further improved. It should be noted that in the case where the vortex generator 20 is formed of wires 23 as illustrated in Fig.
  • Fig. 13 is a side view illustrating another example of the air-conditioning apparatus 100 according to embodiment 3 of the present invention. It should be noted that outlined arrows in Fig. 13 indicate flow directions of air which is sent by the fan 30.
  • the air-conditioning apparatus 100 as illustrated in Fig. 13 employs a cross-flow fan 32 as the fan 30.
  • the air-conditioning apparatus 100 as illustrated in Fig. 13 includes a housing 50 having an air outlet 51.
  • the cross-flow fan 32 is provided in the housing 50 in such a way as to cover a region located above the air outlet 51.
  • air is taken from an upper portion of the cross-flow fan 32, and is blown out of a lower portion of the cross-flow fan 32 toward the air outlet 51.
  • an air flow on an inlet side of the cross-flow fan 32 is regulated comparatively.
  • the cross-flow fan 32 be provided downstream of the cross-flow fan 32 in the flow direction of air from the cross-flow fan 32. Because of provision of the cross-flow fan 32 in this manner, a comparatively regulated air flow can be supplied to the vortex generator 20, as a result of which stable vortexes can be generated at the vortex generator 20, and the heat exchange performance of the heat exchanger 10 can thus be improved.
  • the velocity of an air flow which flows to the vortex generator 20 varies from one location to another at the vertex generator 20. Therefore, also in the air-conditioning apparatus 100 as illustrated in Fig. 13 , it is preferable that a larger number of protrusions 22 or wires 23 be provided in a given area of the vortex generator 20 than in an area where the air velocity is higher than at this given area.
  • vortexes equivalent to vortexes which can be generated at the area of the vortex generator 20 where the air velocity is high can be generated even in the area of the vortex generator 20 where the air velocity is low, and the heat exchange performance of the heat exchanger 10 can thus be further improved.
  • Fig. 14 is a plan view illustrating a further example of the air-conditioning apparatus 100 according to embodiment 3 of the present invention.
  • Fig. 15 is a side view of the air-conditioning apparatus 100 illustrated in Fig. 14 . It should be noted that outlined arrows in Figs. 14 and 15 indicate flow directions of the air which is sent by the fan 30. Furthermore, Figs. 14 and 15 each illustrate a cross section of a casing 52 in which a sirocco fan 33 is provided.
  • the air-conditioning apparatus 100 as illustrated in Figs. 14 and 15 employs the sirocco fan 33 as the fan 30.
  • the sirocco fan 33 is provided in, for example, the casing 52.
  • an air inlet 53 is formed at a position where the air inlet 53 faces a rotation shaft of the sirocco fan 33.
  • an air outlet 54 is formed to face an outer peripheral surface of the sirocco fan 33.
  • an air flow on an outlet side of the sirocco fan 33 is regulated comparatively. Therefore, in the case where the sirocco fan 33 is employed as the fan 30, it is preferable that the sirocco fan 33 be located upstream of the vortex generator 20 in the flow direction of air which is sent by the sirocco fan 33.
  • the sirocco fan 33 By providing the sirocco fan 33 in this manner, a comparatively regulated air flow can be supplied to the vortex generator 20, and stable vortexes can thus be generated at the vortex generator 20. Therefore, the heat exchange performance of the heat exchanger 10 can be improved.
  • the velocity of an air flow flowing to the vortex generator 20 varies from one location to another at the vortex generator 20. Therefore, also in the air-conditioning apparatus 100 as illustrated in Figs. 14 and 15 , it is preferable that a larger number of protrusions 22 or wires 23 be provided in a given area of the vortex generator 20 than in an area where the air velocity is higher than that at the given area. Thereby, vortexes equivalent to vortexes which can be generated at the area of the vortex generator 20 where the air velocity is high can be generated even in the area of the vortex generator 20 where the air velocity is low. Therefore, the heat exchange performance of the heat exchanger 10 can be further improved.
  • Fig. 16 is a plan view illustrating still another example of the air-conditioning apparatus 100 according to embodiment 3 of the present invention.
  • Fig. 17 is a side view of the air-conditioning apparatus 100 as illustrated in Fig. 16 . It should be noted that outlined arrows in Figs. 16 and 17 indicate flow directions of air from the fan 30.
  • the air-conditioning apparatus 100 as illustrated in Fig. 16 and Fig. 17 employs a turbofan 34 as the fan 30.
  • the turbofan 34 takes in air in a rotation axial direction of the turbofan 34. Further, the turbofan 34 sends air toward the outer periphery of the turbofan 34. At this time, an air flow on an outlet side of the turbofan 34 is regulated comparatively. Therefore, in the case where the turbofan 34 is employed as the fan 30, it is preferable that the turbofan 34 be located upstream of the vortex generator 20 in the flow direction of air which is sent by the turbofan 34. Therefore, in the air-conditioning apparatus 100 as illustrated in Figs.
  • the vortex generator 20 is provided to surround the outer periphery of the turbofan 34. Further, the heat exchanger 10 is provided to surround the outer periphery of the vortex generator 20.
  • the turbofan 34 By providing the turbofan 34 in this manner, a comparatively regulated flow of air can be supplied to the vortex generator 20, and stable vortexes can thus be generated at the vortex generator 20.
  • the heat exchange performance of the heat exchanger 10 can be improved.
  • the velocity of an air flow flowing to the vortex generator 20 varies from one location to another at the vortex generator 20. Therefore, also in the air-conditioning apparatus 100 as illustrated in Figs. 16 and 17 , it is preferable that a larger number of protrusions 22 or wires 23 be provided in a given area of the vortex generator 20 than in an area where the air velocity is higher than that at the given area.
  • vortexes equivalent to vortexes which can be generated in the area of the vortex generator 20 where the air velocity is high can be generated even in the area of the vortex generator 20 where the air velocity is low. Therefore, the heat exchange performance of the heat exchanger 10 can be further improved.
  • each of the air-conditioning apparatuses 100 according to embodiments 1 to 3 one heat exchanger 10 and one vortex generator 20 are arranged in the flow direction of air which is sent by the fan 30.
  • the arrangement of these components is not limited to such arrangement.
  • a plurality of heat exchangers 10 and a plurality of vortex generators 20 may be arranged in the flow direction of air from the fan 30 in each of the air-conditioning apparatuses 100 according to embodiments 1 to 3. It should be noted that in embodiment 4, matters which are not particularly described are the same as or similar to those of embodiment 1, and functions and components which are identical to those of embodiment 1 will be denoted by the same reference signs.
  • Fig. 18 is a side view illustrating an example of arrangement of the heat exchangers 10 and the vortex generators 20 of the air-conditioning apparatus 100 according to embodiment 4 of the present invention. It should be noted that in Fig. 18 , the flow direction of air which is sent by the fan 30 is indicated by solid arrows. Also, Fig. 18 schematically shows vortexes indicated by scroll patterns are generated on a downstream side of the vortex generator 20.
  • a plurality of groups each consisting of one heat exchanger 10 and one vortex generator 20 are arranged in a row in the flow direction of air which is sent by the fan 30. That is, in each group consisting of a heat exchanger 10 and a vortex generator 20, the vortex generator 20 is located upstream of the heat exchanger 10.
  • a single group consisting of a heat exchanger 10 and a vortex generator 20 is defined as a heat exchange portion, and a heat exchange portion 80A and a heat exchange portion 80B are arranged in this order from a windward side.
  • the heat exchange portions are collectively referred to as a heat exchange unit 80.
  • the flow of air converted into the vortex flow is supplied to the heat exchange portion 80B after passing through the heat exchanger 10 of the heat exchange portion 80A.
  • air which passes through the heat exchange portion 80A passes through the heat exchanger 10, it is regulated, and the vortex flow shrinks or disappears.
  • improvement in the heat exchange performance by the vortex generator 20 cannot be achieved.
  • the vortex generator 20 is provided upstream of the heat exchanger 10, and air flowing from the heat exchange portion 80A is converted into a vortex flow by the vortex generator 20.
  • the entire heat exchange unit 80 Since the above operation is performed by the entire heat exchange unit 80, improvement of the heat exchange performance by the vortex generators 20 can be promoted by the entire heat exchange unit 80. That is, even in the case where the heat exchange unit 80 is configured that a plurality of heat exchange portions each including a combination of a heat exchanger 10 and a vortex generator 20 are arranged in a row, it is possible to improve the heat exchange performance because the vortex generators 20 are provided in the respective heat exchange portions, that is, respective groups.
  • Fig. 19 is a side view illustrating another example of arrangement of the heat exchangers 10 and the vortex generators 20 of the air-conditioning apparatus 100 according to embodiment 4 of the present invention.
  • one group consisting of a heat exchanger 10 and a vortex generator 20 is defined as a heat exchange portion, and a heat exchange portion 80A, a heat exchange portion 80B ... and a heat exchange portion 80N are arranged in this order from a windward side. That is, three or more groups of heat exchange portions each including a heat exchanger 10 and a vortex generator 20 may be provided. To be more specific, three or more heat exchange portions each including a heat exchanger 10 and a vortex generator 20 may be arranged in a row in the flow direction of air which is sent by the fan 30.
  • the vortex generator 20 is located upstream of the heat exchanger 10, as a result of which the heat exchange performance of the entire heat exchange unit 80 can be improved by the vortex generators 20.
  • the widths L in all the heat exchange portions may be set to the same value, or the widths L in all the heat exchange portions may be set such that the closer the heat exchange portion to the downstream side, the greater (or smaller) the width L in the heat exchange portion. That is, the widths L in all the heat exchange portions may be set equal to or different from each other, or the widths L in some of all the heat exchange portions may be set equal to each other.
  • all the vortex generators 20 are located upstream of the respective heat exchangers 10. It suffices that at least two of the vortex generator 20 are located upstream of respective at least two of the heat exchangers 10.

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Claims (11)

  1. Kältekreislaufvorrichtung (100), umfassend:
    einen Verdampfer (2, 10), aufweisend Wärmeübertragungsleitungen (12), durch die Kältemittel strömt, und Wärmeübertragungsrippen (11), die mit den Wärmeübertragungsleitungen (12) verbunden sind, wobei der Verdampfer (2, 10) eingerichtet ist, Luft mit dem Kältemittel zu kühlen;
    einen Wirbelgenerator (20), der unabhängig von dem Verdampfer (2, 10) ausgebildet ist und stromaufwärts des Verdampfers (2, 10) in einer Strömungsrichtung der Luft vorgesehen ist; und Abstandshalter (40), die zwischen den Wärmeübertragungsrippen (11) des Verdampfers (2, 10) und dem Wirbelgenerator (20) vorgesehen sind, um Platz zwischen den Wärmeübertragungsrippen (11) und dem Wirbelgenerator (20) bereitzustellen,
    wobei die Abstandshalter (40) unabhängig von dem Verdampfer (2, 10) und dem Wirbelgenerator (20) ausgebildet sind, und dadurch gekennzeichnet, dass die Kältekreislaufvorrichtung ferner einen Lüfter (2a, 30) umfasst, der eingerichtet ist, die Luft dem Verdampfer (2, 10) zuzuführen, und wobei
    die Abstandshalter (40) aus einem Material ausgebildet sind, aufweisend eine geringere Wärmeleitfähigkeit als die der Wärmeübertragungsrippen (11) des Verdampfers (2, 10) und des Wirbelgenerators (20).
  2. Kältekreislaufvorrichtung (100) nach Anspruch 1, wobei die Wärmeübertragungsrippen (11) keine geschnittenen und erhabenen Teile aufweisen.
  3. Kältekreislaufvorrichtung (100) nach Anspruch 1 oder 2, wobei eine Vielzahl von Wärmeaustauschabschnitten (80A, 80B, 80N) in einer Reihe in der Strömungsrichtung der Luft vorgesehen sind und jeder der Wärmeaustauschabschnitte (80A, 80B, 80N) eine Kombination aus dem Verdampfer (2, 10) und dem Wirbelgenerator (20) enthält.
  4. Kältekreislaufvorrichtung (100) nach einem der Ansprüche 1 bis 3,
    wobei der Lüfter (2a, 30) ein Propellerlüfter (31) ist, und
    wobei der Propellerlüfter (31) stromabwärts des Verdampfers (2, 10) in der Strömungsrichtung der Luft vorgesehen ist.
  5. Kältekreislaufvorrichtung (100) nach einem der Ansprüche 1 bis 3,
    wobei der Lüfter (2a, 30) ein Querstromlüfter (32) ist, und
    wobei der Querstromlüfter (32) stromabwärts des Verdampfers (2, 10) in der Strömungsrichtung der Luft vorgesehen ist.
  6. Kältekreislaufvorrichtung (100) nach einem der Ansprüche 1 bis 3,
    wobei der Lüfter (2a, 30) ein Schirokko-Lüfter (33) ist, und
    wobei der Schirokko-Lüfter (33) stromaufwärts des Wirbelgenerators (20) in der Strömungsrichtung der Luft vorgesehen ist.
  7. Kältekreislaufvorrichtung (100) nach einem der Ansprüche 1 bis 3,
    wobei der Lüfter (2a, 30) ein Turbolüfter (34) ist, und
    wobei der Turbolüfter (34) stromaufwärts des Wirbelgenerators (20) in der Strömungsrichtung der Luft vorgesehen ist.
  8. Kältekreislaufvorrichtung (100) nach einem der Ansprüche 1 bis 7, wobei der Wirbelgenerator (20) Basen (21) aufweist, die jeweils eine Vielzahl von Vorsprüngen (22) aufweisen.
  9. Kältekreislaufvorrichtung (100) nach Anspruch 8, wobei ein Teil des Wirbelgenerators (20) eine größere Anzahl von Vorsprüngen (22) aufweist, die in den Vorsprüngen (22) der Basen (21) enthalten sind, als ein anderer Teil des Wirbelgenerators (20), wo eine Luftgeschwindigkeit höher ist als an dem Teil des Wirbelgenerators (20).
  10. Kältekreislaufvorrichtung (100) nach einem der Ansprüche 1 bis 7, wobei der Wirbelgenerator (20) eine Vielzahl von Drähten (23, 23a, 23b) aufweist, die in vorherbestimmten Abständen angeordnet sind.
  11. Kältekreislaufvorrichtung (100) nach Anspruch 10, wobei ein Teil des Wirbelgenerators (20) eine größere Anzahl von Drähten (23, 23a, 23b) der Vielzahl von Drähten (23, 23a, 23b) aufweist als ein anderer Teil des Wirbelgenerators (20), an dem eine Luftgeschwindigkeit höher ist als an dem Teil des Wirbelgenerators (20).
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ES2969072T3 (es) * 2019-12-25 2024-05-16 Mitsubishi Electric Corp Unidad de intercambiador de calor y dispositivo de ciclo de refrigeración

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EP3524917A4 (de) 2019-09-18
WO2018066075A1 (ja) 2018-04-12
JPWO2018066075A1 (ja) 2019-06-24

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