EP3524915B1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP3524915B1
EP3524915B1 EP16918265.6A EP16918265A EP3524915B1 EP 3524915 B1 EP3524915 B1 EP 3524915B1 EP 16918265 A EP16918265 A EP 16918265A EP 3524915 B1 EP3524915 B1 EP 3524915B1
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EP
European Patent Office
Prior art keywords
heat exchanger
generating device
vortex generating
refrigeration cycle
cycle apparatus
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
EP16918265.6A
Other languages
English (en)
French (fr)
Other versions
EP3524915A1 (de
EP3524915A4 (de
Inventor
Yuta KOMIYA
Akira Ishibashi
Shinya Higashiiue
Daisuke Ito
Tsuyoshi Maeda
Shin Nakamura
Ryota AKAIWA
Akira YATSUYANAGI
Eiji HIHARA
Chaobin DANG
Jiyang Li
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
University of Tokyo NUC
Original Assignee
Mitsubishi Electric Corp
University of Tokyo NUC
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Publication of EP3524915A1 publication Critical patent/EP3524915A1/de
Publication of EP3524915A4 publication Critical patent/EP3524915A4/de
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Publication of EP3524915B1 publication Critical patent/EP3524915B1/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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F28D1/0233—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 air flow channels
    • F28D1/024—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 air flow channels with an air driving element
    • 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
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • 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
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/02—Safety or protection arrangements; Arrangements for preventing malfunction in the form of screens or covers

Definitions

  • the present invention relates to a refrigeration cycle apparatus provided with a fin-less heat exchanger including no fins.
  • Patent Literature 1 discloses a multi-flow heat exchanger in which "a plurality of flat heat exchange tube portions extending in a vertical direction are disposed parallel to each other in a lateral direction, a pair of corrugated fins bent into a corrugated shape in the vertical direction are disposed between the heat exchange tube portions while overlapping each other, and a drainage corrugated plate bent into a corrugated shape in a forward/backward direction is interposed between the corrugated fins".
  • Patent Literature 2 discloses a fin-less heat exchanger "which includes a plurality of heat exchange tubes each configured to cause heat exchange to be carried out between a first fluid flowing through the heat exchange tube and a second fluid flowing along the outer peripheral surface, and in which each heat exchange tube is formed to linearly extend in a direction where the second fluid flows, the heat exchange tubes are arranged at intervals in a direction orthogonal to the direction where the second fluid flows, and space between each heat exchange tube and a heat exchange tube adjacent thereto is larger on an upstream side than on a downstream side in the direction in which the second fluid flows".
  • JPS5556366U discloses a first condenser equipped with a variable capacity compressor, which is used when the compressor is operated with a large capacity, and a second condenser which is used when the compressor is operated with a small capacity And a condenser disposed in parallel with each other, wherein piping from said second condenser is connected to an intermediate portion of said evaporator.
  • the two evaporators are arranged in two rows of two heat exchangers, and the piping from the second condenser is provided in the heat exchanger disposed in the two rows of the evaporator, on the side closer to the compressor.
  • JPS54139356U discloses that in a heat exchanger equipped with a fin-equipped heat exchanger in which a plurality of fins are mounted on the outer peripheral wall of a heat transfer tube, a plurality of turbulent flow forming A screen is provided on the heat medium inflow side of the fin and these screens are configured to disturb the flow of the heat medium to the fins by driving the screens so that their through hole positions are varied with each other.
  • JPS58167824U discloses a cooler having a toffin and having a leeward side cooling pipe and an upwind side cooling pipe inserted through the plate fins and having a slit cutout formed in the windward side fin region where the windward side cooling pipe is located, Wherein the cooler is disposed on the dew receiving tray so that the windward fin region is inclined so as to be located above the leeward fin region where the leeward side cooling cove is positioned.
  • JPS58165570U discloses that a cross fin type heat exchanger in which a plurality of fins are intersected with each other, the suction side end faces of the fins are alternately shifted and the upper side is inclined so as to be positioned on the suction side Exchanger.
  • JPS6336887U discloses a heat exchanger.
  • JP2013019596A provides a heat exchanger which can improve drainage of water condensed by a fan.
  • JP2007040611A provides a vapor compression type refrigeration cycle device improved in cooling performance by characteristically constituting a refrigerant passage within an evaporator.
  • JPS57134698A provides a heat exchanger device enable to obtain high heat exchange efficiency in the heat exchanging device by a method wherein vortex generating elements are provided at the inlet parts of respective primary and secondary flow passages in order to improve the heat transfer between air and heat exchanging plate due to the generation of turbulent flow.
  • JP2002115934A provides a vaporizer to reduce an influence on a freezing capability of a vaporizer due to frosting.
  • JP2009079795A provides a heat exchanger according to the preamble of claim 1 capable of preventing deterioration of a heat exchange amount at a downstream side in the flowing direction of a second medium.
  • the fin-less heat exchangers including the fin-less heat exchanger described in Patent Literature 2 has the following problems.
  • the present invention has been made in view of the above problems, and an object of the invention is to provide a refrigeration cycle apparatus including a fin-less heat exchanger which is not made larger, and has an improved heat exchange performance.
  • a refrigeration cycle apparatus includes a first heat exchanger which is a fin-less heat exchanger, and includes a plurality of heat transfer tubes extending in a gravity direction, a fan configured to send air to the first heat exchanger, and a vortex generating device provided upstream of the first heat exchanger and configured to cause the air to be sent to the first heat exchanger by the air-sending device to change into a vortex flow.
  • the refrigeration cycle apparatus comprises a spacer provided between the first heat exchanger and the vortex generating device, wherein the vortex generating device is spaced from the first heat exchanger by first space.
  • the vortex generating device is provided upstream of the first heat exchanger.
  • air which flows into the first heat exchanger can be changed into a vortex flow, and the heat exchange performance of the first heat exchanger is improved.
  • Embodiments 1 to 4 of the present invention will be described with reference to the accompanying drawings. It should be noted that in the drawings including Fig. 1 which will be referred to, the relationship in size between components may differ from an actual one. Also, in the drawings including Fig. 1 , components which are the same as or similar to those previously illustrated are denoted by the same reference signs. The same is true of the entire text of the specification. Furthermore, the forms of components described in the entire text of the specification are merely examples, that is, they are not limited to those described in the text.
  • Fig. 1 is a schematic circuit diagram illustrating an example of the refrigerant circuit configuration of a refrigeration cycle apparatus according to embodiment 1 of the present invention (which will be hereinafter referred to as refrigeration cycle apparatus 100).
  • the refrigeration cycle apparatus 100 will be described with reference to Fig. 1 .
  • an air-conditioning apparatus will be described as an example of the refrigeration cycle apparatus 100.
  • the flow of refrigerant during a heating operation is indicated by dashed arrows
  • the flow of refrigerant during a cooling operation is indicated by solid arrows
  • the flow of air in a first heat exchanger 30 is indicated by an outlined arrow.
  • the refrigeration cycle apparatus 100 includes a compressor 10, a flow switching device 20, the first heat exchanger 30, an expansion device 40, a second heat exchanger 50, a first fan 31, a second fan 51 and a vortex generating device 60. Furthermore, the compressor 10, the first heat exchanger 30, the expansion device 40 and the second heat exchanger 50 are connected by refrigerant pipes 70, whereby a refrigerant circuit is formed.
  • the compressor 10 compresses refrigerant which circulates in the refrigerant circuit, and discharges the refrigerant.
  • the refrigerant compressed by the compressor 10 is discharged and sent to the first heat exchanger 30.
  • a rotary compressor, a scroll compressor, a screw compressor or a reciprocating compressor can be used as the compressor 10.
  • the first heat exchanger 30 functions as an evaporator, and during the cooling operation, the first heat exchanger 30 functions as a condenser.
  • the first heat exchanger 30 causes heat exchange to be performed between low-temperature and low-pressure refrigerant having flowed out of the expansion device 40 and air supplied by the first fan 31, as a result of which low-temperature and low-pressure liquid refrigerant or two-phase refrigerant is evaporated.
  • the first heat exchanger 30 When functioning as the condenser, the first heat exchanger 30 causes heat exchange to be performed between high-temperature and high-pressure refrigerant discharged from the compressor 10 and air supplied by the first fan 31, as a result of high-temperature and high-pressure gas refrigerant is condensed.
  • the first heat exchanger 30 includes heat transfer tubes (circular tubes or flat tubes) containing refrigerant passages through which refrigerant flows. It should be noted that the first heat exchanger 30 is not provided with fins which would be orthogonally connected to the heat transfer tubes. That is, the first heat exchanger 30 is a so-called fin-less heat exchanger.
  • the expansion device 40 expands refrigerant having flowed out of the first heat exchanger 30 or the second heat exchanger 50 to reduce the pressure of the refrigerant.
  • an electric expansion valve capable of adjusting the flow rate of refrigerant may be used. It should be noted that not only the electric expansion valve, but a mechanical expansion valve which employs a diaphragm as a pressure receiving portion or a capillary tube can be applied as the expansion device 40.
  • the second heat exchanger 50 functions as the condenser, and during the cooling operation, the second heat exchanger 50 functions as the evaporator.
  • the second heat exchanger 50 causes heat exchange to be performed between high-temperature and high-pressure refrigerant discharged from the compressor 10 and air supplied by the second fan 51, as a result of which high-temperature and high-pressure gas refrigerant is condensed.
  • the second heat exchanger 50 When functioning as the evaporator, the second heat exchanger 50 causes heat exchange to be performed between low-temperature and low-pressure refrigerant having flowed from the expansion device 40 and air supplied by the second fan 51, as a result of which low-temperature and low-pressure liquid refrigerant or two-phase refrigerant is evaporated.
  • a fin-less heat exchanger may be used as in the first heat exchanger 30, or another type of heat exchanger such as a fin-and-tube heat exchanger may be used. It suffices that the type of the second heat exchanger 50 is determined in accordance with targets to be subjected to heat exchange.
  • the flow switching device 20 is provided on a discharge side of the compressor 10, and switches the flow of refrigerant between the flow of refrigerant for the heating operation and that for the cooling operation. To be more specific, during the cooling operation, the flow switching device 20 performs switching to connect the compressor 10 to the first heat exchanger 30, and during the heating operation, the flow switching device 20 perform switching to connect the compressor 10 to the second heat exchanger 50.
  • a four-way valve may be used. However, a combination of two-way valves or three-way valves may be adopted as the flow switching device 20.
  • the first fan 31 is provided close to the first heat exchanger 30, and sends air to the first heat exchanger 30.
  • the first fan 31 is rotated by a motor 32 for the first fan to send air to the first heat exchanger 30.
  • various types of fans such as a propeller fan, a cross-flow fan, a sirocco fan and a turbofan can be used.
  • the first fan 31 is provided downstream of the first heat exchanger 30.
  • the sirocco fan or the turbofan is used as the first fan 31, it is appropriate that the first fan 31 is provided upstream of the first heat exchanger 30.
  • the first fan 31 corresponds to "fan” of the present invention.
  • the second fan 51 is provided close to the second heat exchanger 50, and sends air to the second heat exchanger 50.
  • the second fan 51 is rotated by a motor 52 for the second fan to send air to the second heat exchanger 50.
  • various types of fan such as a propeller fan, a cross-flow fan, a sirocco fan and a turbofan can be used.
  • the fin-less heat exchanger is used as the second heat exchanger 50, as in the first heat exchanger 30, and the propeller fan or the cross-flow fan is used as the second fan 51, it is appropriate that the second fan 51 is provided downstream of the second heat exchanger 50.
  • the fin-less heat exchanger is used as the second heat exchanger 50, as in the first heat exchanger 30, and the sirocco fan or the turbofan is used as the second fan 51, it is appropriate that the second fan 51 is provided as upstream of the second heat exchanger 50.
  • the vortex generating device 60 is provided on an upstream side in the flow of air in the first heat exchanger 30, and changes the flow of air from a laminar flow to a vortex flow (turbulent flow).
  • the operations of the refrigeration cycle apparatus 100 will be described along with the flow of refrigerant.
  • the operations of the refrigeration cycle apparatus 100 will be described by referring to by way of example the case where a fluid which is subjected to heat exchange is air, and a fluid which performs heat exchange is refrigerant, and where the first heat exchanger 30 is used as a heat source-side heat exchanger mounted on a heat source-side unit, and the second heat exchanger 50 is used as a use-side heat exchanger mounted on a use-side unit. That is, when the refrigeration cycle apparatus 100 starts the operation, air conditioned by the second heat exchanger 50 is supplied to a target space to be air-conditioned.
  • the compressor 10 when the compressor 10 is driven, high-temperature and high-pressure gas refrigerant is discharged from the compressor 10. Then, the refrigerant flows as indicated by the solid line arrows. To be more specific, the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the first heat exchanger 30, which functions as the condenser, via the flow switching device 20.
  • the first heat exchanger 30 causes heat exchange to be performed between the high-temperature and high-pressure gas refrigerant having flowed into the first heat exchanger 30 and air supplied by the first fan 31, as a result of which the high-temperature and high-pressure gas refrigerant is condensed into high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant sent from the first heat exchanger 30 is changed into two-phase refrigerant including low-pressure gas refrigerant and liquid refrigerant by the expansion device 40.
  • the two-phase refrigerant flows into the second heat exchanger 50 which functions as the evaporator.
  • the second heat exchanger 50 causes heat exchange to be performed between the two-phase refrigerant having flowed into the second heat exchanger 50 and air supplied by the second fan 51, as a result of which liquid refrigerant included in the two-phase refrigerant is evaporated into low-pressure gas refrigerant.
  • the low-pressure gas refrigerant sent from the second heat exchanger 50 flows into the compressor 10 via the flow switching device 20, and is compressed into high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant is redischarged from the compressor 10. Then, this cycle is repeated.
  • the compressor 10 when the compressor 10 is driven, high-temperature and high-pressure gas refrigerant is discharged from the compressor 10. Then, the refrigerant flows as indicated by the dashed arrows. To be more specific, the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the second heat exchanger 50, which functions as the condenser, via the flow switching device 20.
  • the second heat exchanger 50 causes heat exchange to be performed between the high-temperature and high-pressure gas refrigerant having flowed into the second heat exchanger 50 and air sent by the second fan 51, as a result of which the high-temperature and high-pressure gas refrigerant is condensed into high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant sent from the second heat exchanger 50 is changed into two-phase refrigerant including low-pressure gas refrigerant and liquid refrigerant by the expansion device 40.
  • the two-phase refrigerant flows into the first heat exchanger 30 which functions as the evaporator.
  • the first heat exchanger 30 causes heat exchange to be performed between the two-phase refrigerant having flowed into the first heat exchanger 30 and air sent by the first fan 31, as a result of which the liquid refrigerant included in the two-phase refrigerant is evaporated into low-pressure gas refrigerant.
  • the low-pressure gas refrigerant sent from the first heat exchanger 30 flows into the compressor 10 via the flow switching device 20, and is compressed into high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant is discharged from the compressor 10 again. Then, this cycle is repeated.
  • Fig. 2 is a perspective view illustrating an example of the configurations of the first heat exchanger 30 and the vortex generating device 60 provided in the refrigeration cycle apparatus 100.
  • Fig. 3 is a side view illustrating the example of the configurations of the first heat exchanger 30 and the vortex generating device 60 provided in the refrigeration cycle apparatus 100.
  • Fig. 4 is a cross-sectional view illustrating an example of the configuration of flow passages of each of flat tubes 33 of the first heat exchanger 30 provided in the refrigeration cycle apparatus 100.
  • the first heat exchanger 30 and the vortex generating device 60 provided in the refrigeration cycle apparatus 100 will be described in detail with reference to Figs. 2 to 4 .
  • Fig. 3 schematically illustrates generation of vortex flows in a region located downstream of the vortex generating device 60.
  • An arrow X in Fig. 2 indicates a direction in which the flat tubes 33 are arranged.
  • the direction in which the flat tubes 33 are arranged will be hereinafter referred to as an X direction.
  • An arrow Y in Figs. 2 and 3 indicates a flow direction of air.
  • the flow direction of air will be hereinafter referred to as a Y direction.
  • An arrow Z in Figs. 2 and 3 indicates a longitudinal direction of each flat tube 33.
  • the longitudinal direction of each flat tube 33 will be hereinafter referred to as a Z direction.
  • the X direction, the Y direction and the Z direction are the directions defined above.
  • the following description is made referring to by way of example the case where referring to Figs. 2 and 3 , the X direction and the Y direction are orthogonal to the Z direction, the X direction is also orthogonal to the Y direction, and the first heat exchanger 30 is mounted on the refrigeration cycle apparatus 100 such that the X direction and the Y direction are parallel to a horizontal plane, and the Z direction is parallel to a gravity direction.
  • the first heat exchanger 30 includes a first header 34 containing a fluid passage through which fluid (for example, refrigerant) flows, a second header 35 containing a fluid passage through which the fluid flows, and the flat tubes 33 containing fluid passages. That is, the first heat exchanger 30 does not have fins as components.
  • fluid for example, refrigerant
  • first header 34 and the second header 35 are provided in pairs, with the flat tubes 33 interposed between these headers. That is, as illustrated in Figs. 2 and 3 , one of two ends of each of the flat tubes 33 (which is a lower end in the Z direction) is connected to the first header 34, and the other (an upper end in the Z direction) is connected to the second header 35.
  • the first header 34 is an elongated element extending in the X direction, and contains a fluid passage through which the fluid flows. To the first header 34, one of the ends of each flat tube 33 is connected.
  • the first header 34 is used as an inflow-side header into which fluid supplied from, for example, the compressor 10 or the expansion device 40 flows.
  • the first header 34 is located parallel to the horizontal direction. It should be noted that the first header 34 may be used as an outflow-side header. In this case, the second header 35 is used as the inflow-side header.
  • the second header 35 is an elongated element extending in the X direction, and contains a fluid passage through which the fluid flows. To the second header 35, the other end of each flat tube 33 is connected. For example, fluid which has flowed through the first header 34 and the flat tubes 33 is supplied to the second header 35.
  • the second header 35 is used as the outflow-side header.
  • the second header 35 is located parallel to the horizontal direction. It should be noted that the second header 35 may be used as the inflow-side header. In this case, the first header 34 is used as the outflow-side header.
  • the flat tubes 33 are arranged parallel to each other such that the fluid flows in the Z direction, and air sent from the first fan 31 passes through space between adjacent flat tubes 33.
  • the flat tubes 33 extend in the gravity direction, and are arranged in parallel. That is, the first heat exchanger 30 is provided in a unit in which the flat tubes 33 are mounted such that the longitudinal direction of each flat tube 33 is parallel to the gravity direction.
  • each flat tube 33 is a heat transfer tube which is elongated such that a horizontal length A2 is greater than a vertical height A1. Further, each flat tube 33 contains a plurality of fluid passages 33a through which the fluid flows, as illustrated in, for example, Fig. 4 .
  • a direction along the vertical height A1 is referred to as the direction of the minor axis of the cross section, and a direction along the horizontal length A2 is referred to as the direction of the major axis of the cross section.
  • the number of flat tubes 33 and the longitudinal length of each flat tube 33 are not particularly limited. It suffices that they are determined in accordance with, for example, the output of the refrigeration cycle apparatus 100 in which the first heat exchanger 30 is mounted or the purpose of use of the refrigeration cycle apparatus 100.
  • the flat tube 33 is made of, for example, aluminum or an aluminum alloy.
  • the first heat exchanger 30 may be made up of circular tubes (heat transfer tubes each having a circular cross section). In this case also, it is assumed that the circular tubes are disposed such that the fluid flows in the Z direction.
  • the vortex generating device 60 is configured such that air sent from the first fan 31 passes through the vortex generating device 60, and the flow of air which is a laminar flow before the flow of air passes through the vortex generating device 60 is changed to a vortex flow (turbulent flow) after the flow of air passes through the vortex generating device 60. That is, as illustrated in Fig. 3 , a vortex flow is generated in the flow of air after the flow of air passes through the vortex generating device 60.
  • the vortex generating device 60 is made of resin or metal.
  • the vortex generating device 60 disturbs the flow of air which is a laminar flow, whereby the flow of air changes to a vortex flow.
  • This flow of air that is, the vortex flow
  • the vortex generating device 60 upstream of the first heat exchanger 30, the flow of air is changed to a vortex flow on a windward side of the first heat exchanger 30, and the heat exchange between the air and the flat tubes 33 of the first heat exchanger 30 is promoted, thus improving the heat exchange performance.
  • first heat exchanger 30 and the vortex generating device 60 may be provided as a single unit, and provided in, for example, the heat source-side unit (outdoor unit) of the refrigeration cycle apparatus 100.
  • first heat exchanger 30 and the vortex generating device 60 may be provided as separate components.
  • the vortex generating device 60 will be described in detail.
  • Fig. 5A is a front view illustrating an example of the configuration of the vortex generating device 60 provided in the refrigeration cycle apparatus 100.
  • Fig. 5B is a schematic for explaining a vane structure 600 of the vortex generating device 60 as illustrated in Fig. 5A .
  • Fig. 5C is a schematic for explaining a vane body 602 of the vane structure 600 of the vortex generating device 60 as illustrated in Fig. 5B .
  • the vortex generating device 60 is provided, for example, upstream of the flow of air in the first heat exchanger 30 and located to face the first heat exchanger 30. As illustrated in Fig. 5A , the vortex generating device 60 includes a plurality of vane bodies 602, first support bodies 601 to which the vane bodies 602 are fixed, and second support bodies 603 provided to intersect the first support bodies 601.
  • the first support bodies 601 are provided parallel to the Z direction.
  • the first support bodies 601 are arranged in the X direction and separated from each other by space where the vane bodies 602 are provided.
  • the first support body 601 is a plate-shaped element.
  • the plurality of vane bodies 602 are fixed to the first support bodies 601 and arranged in the Z direction. For example, referring to Fig. 5A , ten vane bodies 602 are fixed to the rightmost one of the first support bodies 601 and arranged in the Z direction.
  • the vortex generating device 60 may be configured such that vane bodies 602 are fixed to respective first support bodies 601. If this is applied to the first support bodies 601 as illustrated in Fig. 5A , each of the first support bodies 601 parallel to the Z direction is divided into ten pieces. As a result, in the vortex generating device as illustrated in Fig. 5A in which twenty-one first support bodies 601 are arranged in the X direction, each of the twenty-one first support bodies 601 is divided into ten, as a result of which two hundred ten (10 ⁇ 21) support bodies are provided. It should be noted that the above division number is not limited to 10, that is, it may be set as appropriate. For example, the division number may be set to 2 in order that five vane bodies 602 be fixed to each first support body 601.
  • the vortex generating device 60 includes two second support bodies 603.
  • the second support bodies 603 are located parallel to the X direction.
  • One of the second support bodies 603 is fixed to upper ends of the first support bodies 601, and the other is fixed to lower ends of the first support bodies 601.
  • the second support bodies 603 are plate-shaped elements.
  • the second support bodies 603 support the plurality of first support bodies 601 to maintain the shape of the vortex generating device 60.
  • each of the plurality of flat tubes 33 of the first heat exchanger 30 located to face the vortex generating device 60 is linearly shaped.
  • the plurality of flat tubes 33 are arranged in a predetermined arrangement direction.
  • the arrangement direction is a direction parallel to the X direction.
  • the vane bodies 602 are arranged in an axial direction of each of the flat tubes 33 and also in the arrangement direction of the flat tubes 33.
  • the axial direction is a direction parallel to the Z direction.
  • the vane bodies 602 are arranged in the above manner, vortex flows evenly flow into the space between the flat tubes 33, the heat exchange performance can be improved.
  • the vortex generating device 60 includes two hundred (10 ⁇ 20) vane bodies 602.
  • FIG. 5B (a) is a perspective view of the vane structure 600, (b) is a top view of the vane structure 600, (c) is a side view of the vane structure 600 as seen from a location close to a second support portion 601B, and (d) is a front view of the vane structure 600.
  • FIG. 5C (a) is a top view of the vane body 602, and (b) is a side view of the vane body 602 as seen from a location close to the second support portion 601B.
  • openings CL second spaces through which air flows is provided between each of the first support bodies 601 and an associated one of the plurality of vane bodies 602.
  • Each of the vane bodies 602 has one end P1 in the flow direction of air, and the other end P2 in the flow direction of air, and also surfaces extending from the one end P1 to the other end P2 along the flow direction of air.
  • the surfaces extending along the flow direction of air correspond to a first surface S1 and a second surface S2 which will be described later. It should be noted that the flow direction of air does not necessarily coincide with the Y direction.
  • the vortex generating device 60 includes a plurality of vane structures 600.
  • the vane structures 600 each include a first support portion 601A, the second support portion 601B, a first vane 602A and a second vane 602B.
  • the first support portion 601A and the second support portion 601B are components included in an associated first support body 601. Each of the first support portion 601A and the second support portion 601B is one of constituent components of the first support body 601. A plurality of first support portions 601A and a plurality of second support portions 601B form the first support bodies 601. Each of the second support portions 601B is spaced from an associated one of the first support portions 601A by a predetermined first distance, and faces the associated first support portion 601A.
  • the vane bodies 602 each include the first vane 602A which is a plate-shaped element, and the second vane 602B which is a plate-shaped element and paired with the first vane 602A.
  • the first vane 602A is located between the first support portion 601A and the second support portion 601B.
  • the second vane 602B is also located between the first support portion 601A and the second support portion 601B.
  • the second vane 602B is a vane paired with the first vane 602A.
  • the first vane 602A includes a first end E1 corresponding to the one end P1, a second end E2 corresponding to the other end P2, a third end E3 connected to the first support portion 601A, the first surface S1 corresponding to one of the surfaces along the flow direction of air, and a first opposite surface S10 located opposite to the first surface S1.
  • the second vane 602B includes a fourth end E4 corresponding to the one end P1, a fifth end E5 corresponding to the other end P2, a sixth end E6 connected to the second support portion 601B, the second surface S2 corresponding to the other of the surfaces along the flow direction of air, and a second opposite surface S20 formed opposite to the second surface S2.
  • first direction Dr1 the direction from the first end E1 toward the second end E2 at the first surface S1
  • second direction Dr2 the direction from the fourth end E4 of toward the fifth end E5 at the second surface S2
  • first surface S1 and the second surface S2 are formed such that the first direction Dr1 and the second direction Dr2 intersect each other.
  • the vane body 602 is seen side-on as illustrated in Figs. 5B , (c) and 5C , (b)
  • the vane body 602 is located such that the first vane 602A and the second vane 602B intersect each other.
  • first direction Dr1 and the second direction Dr2 correspond to the above flow direction of air at the vane body 602.
  • the first vane 602A is triangular. That is, the first surface S1 is shaped in the form of a triangle tapering from the first end E1 toward the second end E2.
  • the second vane 602B is also triangular. That is, the second surface S2 is shaped in the shape of a triangle tapering from the fifth end E5 toward the fourth end E4.
  • the first vane 602A and the second vane 602B are tapered in opposite directions.
  • Fig. 5D is a schematic for explaining an example of the dimensions of the first heat exchanger 30 and the dimensions of the flat tube 33 provided in the refrigeration cycle apparatus 100.
  • (a) is a front view of the first heat exchanger 30, and (b) is a sectional view of the flat tube 33.
  • dimensions are indicated by way of example, and the dimensions in the embodiment are not limited to the indicated dimensions.
  • the distance from the first header 34 to the second header 35 is 200 (mm).
  • the width of the flat tube 33 in the direction of the minor axis of the cross section thereof is 0.6 (mm).
  • the length of the flat tube 33 in the direction of the major axis of the cross section thereof is 17.8 (mm).
  • Each of the longitudinal length of the first header 34 and the longitudinal length of the second header 35 is 200 (mm).
  • a pitch DP of the flat tubes 33 is 2.5 (mm).
  • Fig. 5E is a schematic for explaining the dimensions of the vortex generating device 60 and the vane structure 600 provided in the refrigeration cycle apparatus 100.
  • (a) is a front view of the vortex generating device 60
  • (b) is a top view of the vane structure 600
  • (c) is a side view of the vane structure 600 as seen from a location close to the second support portion 601B.
  • dimensions are indicated by way of example, and the dimensions in the embodiment are not limited to the indicated dimensions.
  • the width of the vortex generating device 60 in the Z direction is 200 (mm).
  • the width of the vortex generating device 60 in the X direction is 200 (mm).
  • the dimension of the first support portion 601A in the Y direction is 5 (mm).
  • the width (thickness) of the first support portion 601A in the X direction is 0.6 (mm).
  • the dimension of the third end E3 of the first vane 602A in the Y direction is 3.5 (mm).
  • the width of the first end E1 of the first vane 602A is 1.8 (mm).
  • the dimension of the second support portion in the Y direction is 5 (mm).
  • the width (thickness) of the second support portion in the X direction is 0.6 (mm).
  • the dimension of the sixth end E6 of the second vane 602B in the Y direction is 3.5 (mm).
  • the width of the fourth end E4 of the second vane 602B is 1.8 (mm).
  • the first distance between the first support portion 601A and the second support portion is 1.9 (mm).
  • the vertex angle of the triangular shape of the first surface S1 of the first vane 602A is 27 degrees.
  • the vertex angle of the triangular shape of the second surface S2 of the second vane 602B is also 27 degrees.
  • An angle ⁇ 1 at which the first surface S1 inclines to the Y direction is 135 degrees.
  • An angle ⁇ 2 at which the second surface S2 inclines to the Y direction is 45 degrees.
  • first surface S1 and the second surface S2 orthogonally intersect each other.
  • the first heat exchanger 30 includes first flat tubes 33A and second flat tubes 33B as respective pairs of adjacent flat tubes 33.
  • Each of the second flat tubes 33B is linearly shaped.
  • the second flat tube 33B is separated from the first flat tube 33A by a predetermined second distance.
  • the second flat tube 33B is located parallel to the first flat tube 33A, and also located to face the first flat tube 33A.
  • associated ones of the vane bodies 602 of the vortex generating device 60 are provided. Since the vane bodies 602 are provided in such a manner, vortex flows evenly flow into the space corresponding to the space between the flat tubes 33, thus improving the heat exchange performance. It is therefore possible to reduce the pressure losses at the vortex generating device 60 and the first heat exchanger 30.
  • the first distance between the first support portion 601A and the second support portion and the distance (second distance) between adjacent flat tubes 33 are both 1.9 (mm); that is, they are equal to each other.
  • the thickness of the first support portion 601A, the thickness of the second support portion 601B, and the width of the flat tube 33 in the direction of the minor axis of the cross section are all 0.6 (mm); that is, they are all equal to each other.
  • the vane body 602 is located within the space corresponding to the space between the first flat tube 33A and the second flat tube 33B.
  • the vane body 602 is provided within the space corresponding to the space between the first flat tube 33A and the second flat tube 33B.
  • a plurality of vane bodies 602 arranged in an axial direction of an associated one of the first flat tubes 33A are defined as a vane body group WG
  • a single vane body group WG is provided between the associated first flat tube 33A and an associated one of the second flat tubes 33B.
  • the configuration of the embodiment is not limited to the configuration in which the single vane body group WG is provided in the space corresponding to the space between the associated first flat tube 33A and second flat tube 33B.
  • a plurality of vane body groups WG may be provided the space corresponding to the space between the associated first flat tube 33A and second flat tube 33B such that they are arranged in a direction from the associated first flat tube 33A toward the associated second flat tube 33B.
  • vane body groups WG of n rows may be arranged in the space corresponding to the space between the associated first flat tube 33A and second flat tube 33B, where n is a natural number.
  • the first flat tube 33A and the second flat tube 33B are located in front of the first support bodies 601 associated with the vane bodies 602 located at both ends in the X direction. That is, with respect to the first support portion 601A associated with the vane body 602 located at one end in the X direction, the first flat tube 33A is located in front of the first support portion 601A in the Y direction. Further, with respect to the second support portion associated with the vane body 602 located at the other end in the X direction, the second flat tube 33B is located in front of the second support portion in the Y direction.
  • Fig. 5F is a schematic for explaining modification 1 of the vortex generating device 60 provided in the refrigeration cycle apparatus 100.
  • (a) illustrates the arrangement of the plurality of vane bodies 602 of the vortex generating device 60 as described above
  • (b) illustrates modification 1 of the vortex generating device 60 and illustrates an example of the arrangement of the vane bodies 602 (first vane bodies) described above and vane bodies (second vane bodies 602SY) which are different in shape from the vane bodies 602.
  • the vortex generating device 60 includes two types of vane bodies which have different shapes. That is, the vortex generating device 60 includes the vane bodies 602 (which will also be referred to as first vane bodies) and the second vane bodies 602SY Each of the first vane bodies and an associated one of the second vane bodies are symmetrical. Each second vane body 602SY is formed in such a shape that the first vane 602A and the second vane 602B of the first vane body are shifted symmetrically with respect to an imaginary plane which passes through an intermediate position between the first support portion 601A and the second support portion 601B, and which is also parallel to the first support portion 601A.
  • the first vane bodies and the second vane bodies 602SY are arranged in a staggered manner. Thereby, it is possible to more efficiently disturb the flow of air which is a laminar flow, and change the flow of air into a vortex flow.
  • Fig. 5G is a schematic for explaining modification 2 of the vortex generating device 60 provided in the refrigeration cycle apparatus 100.
  • the number of vanes included in each of the vane bodies is one.
  • FIG. 5G (a) is a perspective view of the vane structure 600 according to modification 2
  • (b) is a top view of the vane structure 600 according to modification 2
  • (c) is a side view of the vane structure 600 according to modification 2 as seen from a location close to the second support portion 601B
  • (d) is a front view of the vane structure 600 according to modification 2.
  • each of vane bodies 702 includes a single vane which is a plate-shaped element. More specifically, each vane body 702 does not include a vane corresponding to the second vane 602B of the vane body 602.
  • the vane of each vane body 702 has the same configuration as the first vane 602A, and its description will thus be omitted. It should be noted that as a matter of convenience for explanation, the vane of the vane body 702 is also illustrated as the first vane 602A in the figures, because the vane of the vane body 702 has the same configuration as the first vane 602A.
  • the vane of the vane body 702, as well as the first vane 602A, includes the first end E1 associated with the one end P1, the second end E2 associated with the other end P2, the third end E3 connected to the first support portion 61A, the first surface S1 corresponding to a surface extending along the flow direction of air, and the first opposite surface S10 located opposite to the first surface S1.
  • Fig. 5H is a schematic for explaining modification 3 of the vortex generating device 60 provided in the refrigeration cycle apparatus 100.
  • the vanes included in the vane bodies are quadrangular, not triangular.
  • FIG. 5H (a) is a perspective view of the vane structure 600 according to modification 3, (b) is a top view of the vane structure 600 according to modification 3, (c) is a side view of the vane structure 600 according to modification 3 as seen from a location close to the second support portion 601B, and (d) is a front view of the vane structure 600 according to modification 3.
  • a vane body 802 of modification 3 includes a first vane 802A and a second vane 802B, which are both quadrangular.
  • the first vane 802A and the second vane 802B are different from the second vane 602A and the second vane 602B on the point that the first vane 802A and the second vane 802B are quadrangular; however, the other configurations of the first vane 802A and the second vane 802B are the same as or similar to those of the first vane 602A and the second vane 602B, and their explanations will thus be omitted.
  • modification 3 can be combined with modification 2. That is, the first vane 602A of the vane body 702 may be quadrangular.
  • the compressor 10, the first heat exchanger 30, the expansion device 40 and the second heat exchanger 50 form the refrigerant circuit, and the vortex generating device 60 is located upstream of the first heat exchanger 30. It is therefore possible to improve the heat exchange performance of the first heat exchanger 30 which is a fin-less heat exchanger.
  • the first heat exchanger 30 is not provided with fins. Therefore, a thermal contact resistance is not present between the heat transfer tubes and fins, or a resistance is not made by thermal conduction which would be caused by fins themselves. Therefore, the heat exchange performance is improved.
  • the first heat exchanger 30 functions as the evaporator, dew water flows and drops down along the flat tubes 33 disposed parallel to the gravity direction.
  • the drainage characteristic of the refrigeration cycle apparatus 100 is improved. By virtue of improvement of the drainage characteristic, it is possible reduce accumulation of ice at a lower portion of the first heat exchanger 30 even while the refrigeration cycle apparatus 100 is performing, for example, a defrosting operation.
  • the refrigeration cycle apparatus 100 a water heater, a refrigerating machine and an integrated air-conditioner and water-heater system are present. In any case, the heat exchange performance of the first heat exchanger 30 can be improved.
  • the refrigerant for use in the refrigeration cycle apparatus 100 is not particularly limited.
  • R410A, R32 and HFO1234yf can be used as the refrigerant.
  • air and refrigerant are described above as examples of fluids between which heat exchange is performed in the second heat exchanger 50, the fluids are not limited to air and refrigerant. That is, the fluids for such heat exchange in the second heat exchanger 50 vary in accordance with the form of the second heat exchanger 50.
  • any refrigerating machine oil such as mineral oil, alkylbenzene oil, ester oil, ether oil or fluorine oil can be used for the refrigeration cycle apparatus 100 regardless whether the oil is soluble in refrigerant or not.
  • the refrigeration cycle apparatus 100 is described above by referring to by way of example the case where the flow of refrigerant can be changed by the flow switching device 20, the refrigeration cycle apparatus 100 may be configured, without including the flow switching device 20, to function as a heating-only apparatus in which the first heat exchanger 30 functions only as the evaporator.
  • the first heat exchanger 30 but the second heat exchanger 50 may be formed as the fin-less heat exchanger, and the vortex generating device 60 may be provided upstream of the second heat exchanger 50.
  • Fig. 6 is a side view illustrating an example of the configurations of a first heat exchanger 30 and a vortex generating device 60 provided in a refrigeration cycle apparatus according to embodiment 2 of the present invention.
  • Fig. 7 is a diagram schematically illustrating the temperatures of the first heat exchanger 30 and the vortex generating device 60 in the case where the first heat exchanger 30 provided in the refrigeration cycle apparatus according to embodiment 2 of the present invention is used as the evaporator.
  • the first heat exchanger 30 and the vortex generating device 60 provided in the refrigeration cycle apparatus according to embodiment 2 of the present invention will be described in detail with reference to Figs. 6 and 7 . It should be noted that in Figs. 6 and 7 , the flow of air is indicated by an outlined arrow.
  • the basic configuration of the refrigeration cycle apparatus according to embodiment 2 of the present invention is the same as or similar to that of the refrigeration cycle apparatus 100 according to embodiment 1 of the invention. Furthermore, embodiment 2 will be described mainly by referring to the differences between embodiments 1 and 2, and elements which are the same as or similar to those of embodiment 1 will be denoted by the same reference signs, and their descriptions will thus be omitted.
  • Embodiment 1 is described above by referring to by way of example the case where the vortex generating device 60 is provided upstream of the first heat exchanger 30.
  • embodiment 2 will be described by referring to by way of example the case where the vortex generating device 60 is provided upstream of the first heat exchanger 30, and also separated therefrom by first space 41 corresponding to a distance x. That is, the vortex generating device 60 is provided in non-contact with the first heat exchanger 30.
  • 6 and 7 represents the thickness of the vortex generating device 60 (the width of the vortex generating device 60 in the Y direction) and L2 represents the width of the flat tube 33 in the direction of the major axis of the cross section (the width of the flat tube 33 in the Y direction).
  • first heat exchanger 30 and the vortex generating device 60 are provided such that they are separated from each other by the first space 41 corresponding to the distance x, when the first heat exchanger 30 is used as the evaporator, the temperatures of the flat tube 33 of the first heat exchanger 30 and the vortex generating device 60 are illustrated in Fig. 7 .
  • the temperature of refrigerant flowing through the flat tube 33 decreases to a value lower than an outdoor air temperature. Furthermore, air sent to the first heat exchanger 30 by the first fan 31 is cooled by the flat tube 33, as a result of which the temperature of the air decreases as the air flows toward the downstream side. It should be noted that the surface temperature of the flat tube 33 is approximately equal to the temperature of the refrigerant flowing through the flat tube 33. Further, at locations in the flow direction of air from the first fan 31 (Y direction), the temperature of the refrigerant hardly changes. Therefore, the surface temperature of the flat tube 33 is constant in the flow direction of air from the first fan 31 (Y direction) (straight line C in Fig. 7 ).
  • the surface temperature of the vortex generating device 60 is close to the surface temperature of the flat tube 33 since a surface of the vortex generating device 60 is in contact with the flat tube 33, and the surface temperature of the vortex generating device 60 changes toward the upstream side in the flow of air due to thermal conduction.
  • part of the flat tube 33 has a temperature OOlower than a dew-point temperature of air. Then, water droplets (dew) adhere to the surface of the flat tube 33, though the first heat exchanger 30 is the fin-less heat exchanger. It should be noted that the water droplets adhering to the surface of the flat tube 33 will be referred to as dew water.
  • the temperature of the refrigerant flowing through the flat tube 33 decreases to a value lower than the outdoor air temperature.
  • the surface temperature of the flat tube 33 decreases to a value lower than the dew-point temperature of air.
  • water droplets (dew) adhere to the surface of the flat tube 33, though the first heat exchanger 30 is the fin-less heat exchanger. It should be noted that the water droplets adhering to the surface of the flat tube 33 will be referred to as dew water.
  • the dew water adhering to the surface of the flat tube 33 is frozen and frost is formed. If dew condensation and frost formation occur, the flow of air in the first heat exchanger 30 is blocked. If the flow of air is blocked, the heat exchange performance of the first heat exchanger 30 is reduced.
  • the vortex generating device 60 is provided upstream of the first heat exchanger 30. It should be noted that in the case where the flat tube 33 of the first heat exchanger 30 and the vortex generating device 60 are in contact with each other, that is, the distance x is zero, the temperature of the vortex generating device 60 becomes close to the temperature of the flat tube 33 because of the thermal conduction.
  • the temperature of the vortex generating device 60 is reduced by the refrigerant flowing through the flat tube 33, as a result of which the closer a portion of the vortex generating device 60 to the upstream end in the flow direction of air, the higher the temperature of the portion of the vortex generating device 60 because of the thermal conduction, as shown by a straight line D represented by a two-dot chain line in Fig. 7 .
  • a straight line D represented by a two-dot chain line in Fig. 7 .
  • the first heat exchanger 30 and the vortex generating device 60 are provided not in contact with each other in order that the temperature of the flat tube 33 of the first heat exchanger 30 should not be transferred to the vortex generating device 60 by the thermal conduction. That is, since the space 41 is provided, the vortex generating device 60 is hardly cooled by the refrigerant flowing through the flat tube 33. Thus, the temperature of the vortex generating device 60 is close to the outdoor air temperature as indicated by a solid line E in Fig. 7 , and the dew condensation and frost formation do not easily occur at the vortex generating device 60.
  • the distance x is determined in consideration of the particle diameter of dew or frost that is assumed to be formed on the surface of the flat tube 33 or the vortex generating device 60. For example, preferably, the distance x should fall within the range of 1 mm to 5 mm. This is because if the distance x is excessively great, the vortex flow may fail to reach the first heat exchanger 30, and if the distance x is excessively small, the dew water generated at the first heat exchanger 30 may adhere to the vortex generating device 60.
  • first heat exchanger 30 and the vortex generating device 60 are separated from each other by the distance x at, for example, a mounting surface (mounting surface 81 as illustrated in Fig. 6 ) of a unit on which the first heat exchanger 30 and the vortex generating device 60 are mounted.
  • the first heat exchanger 30 and the vortex generating device 60 are provided as a unit using a common frame for the first heat exchanger 30 and the vortex generating device 60, space corresponding to the distance x may be provided in the frame.
  • the frame is formed of a material, for example, resin, which has a lower thermal conductivity than those of the flat tube 33 of the first heat exchanger 30 and the vortex generating device 60.
  • a spacer (for example, a projection or a protrusion) which is a component separate from the first heat exchanger 30 and the vortex generating device 60 may be provided on at least one of facing surfaces of the first heat exchanger 30 and the vortex generating device 60 in order to provide space corresponding to the distance x. That is, the first space 41 is provided between the first heat exchanger 30 and the vortex generating device 60 by interposing the spacer between the first heat exchanger 30 and the vortex generating device 60.
  • the spacer is made of a material, for example, resin, which has a lower thermal conductivity than the flat tube 33 of the first heat exchanger 30 and the vortex generating device 60.
  • the spacer which is a component separate from the first heat exchanger 30 and the vortex generating device 60 the number of spacers, the size of the spacer or spacers, the material thereof, etc., are not particularly limited.
  • a spacer formed in the shape of a square ring may be provided on at least one of the facing surfaces of the first heat exchanger 30 and the vortex generating device 60 in order to provide space corresponding to the distance x.
  • the first space 41 is provided by interposing the spacer between the first heat exchanger 30 and the vortex generating device 60. That is, it is possible to prevent the size of the first space 41 from differing from a set value due to, for example, errors in provision of the first heat exchanger 30 and the vortex generating device 60. Furthermore, a flow of air disturbed in a desired state by the vortex generating device 60 can be supplied to the first heat exchanger 30 by accurately setting the distance x, which corresponds to the space 41, between the first heat exchanger 30 and the vortex generating device 60. Thus, the heat exchange performance of the first heat exchanger 30 can be further improved.
  • the first heat exchanger 30 when used as the evaporator, it is possible to reduce cooling of the vortex generating device 60 via the spacer, since the spacer is formed of a material having a lower thermal conductivity than the first heat exchanger 30 and the vortex generating device 60. Therefore, frost formation does not easily occur at the vortex generating device 60 even if the first heat exchanger 30 and the vortex generating device 60 are thermally connected to each other by the spacer.
  • the flow of air with vortexes generated by the vortex generating device 60 can be supplied to the first heat exchanger 30 continuously and stably for a longer time period. Therefore, the heat exchange performance of the first heat exchanger 30 can be further improved.
  • the spacer may be provided as a product molded integrally with the vortex generating device 60. For example, portions of an end of the vortex generating device 60 that is located closer to the first heat exchanger 30 may be projected toward the first heat exchanger 30 and be applied as spacers. Also, for example, the spacer may be provided as a product molded integrally with the first heat exchanger 30. That is, portions of an end of the first heat exchanger 30 that is located closer to the vortex generating device 60 may be projected toward the vortex generating device 60 and be applied as spacers.
  • the spacer is formed in the above manner, it is possible to accurately set the distance x, which corresponds to the first space 41, between the first heat exchanger 30 and the vortex generating device 60.
  • a flow of air disturbed in a desired state by the vortex generating device 60 can be supplied to the first heat exchanger 30, and as a result the heat exchange performance of the first heat exchanger 30 can be further improved.
  • the first heat exchanger 30 and the vortex generating device 60 are in contact with each other at the portions which are used as the spacers. In this case, since several locations can be determined as contact locations, the vortex generating device 60 is not easily cooled. That is, frost formation does not easily occur at the vortex generating device 60.
  • Fig. 8 is a perspective view illustrating an example of the configurations of a first heat exchanger 30 and a vortex generating device 60 provided in a refrigeration cycle apparatus according to embodiment 3 of the present invention.
  • Fig. 9 is a side view illustrating the example of the configurations of the first heat exchanger 30 and the vortex generating device 60 provided in the refrigeration cycle apparatus according to embodiment 3 of the present invention.
  • the example of the first heat exchanger 30 and the vortex generating device 60 provided in the refrigeration cycle apparatus according to embodiment 3 of the present invention will be described in detail with reference to Figs. 8 and 9 .
  • Fig. 9 schematically shows that vortex flows are generated in a region located downstream of the vortex generating device 60.
  • the basic configuration of the refrigeration cycle apparatus according to embodiment 3 of the present invention is the same as or similar to that of the refrigeration cycle apparatus 100 according to embodiment 1 of the invention.
  • Embodiment 3 will be described mainly by referring to differences between embodiment 3 and embodiments 1 and 2; and elements which are the same as those of embodiments 1 and 2 will be denoted by the same reference signs, and their descriptions will thus be omitted.
  • Embodiment 2 is described above by referring to by way of example the case where the vortex generating device 60 is provided upstream of the first heat exchanger 30, and separated therefrom by the first space 41 (distance x).
  • a plurality of groups each consisting of a single first heat exchanger 30 and a single vortex generating device 60 are arranged in a row in the flow direction of air. That is, in each of these groups, the vortex generating device 60 is located upstream of the first heat exchanger 30.
  • a heat exchange portion 80A and a heat exchange portion 80B are illustrated in this order from a windward side, and each of these heat exchange portions correspond to a single group consisting of the first heat exchanger 30 and the vortex generating device 60.
  • the first heat exchanger 30 and the vortex generating device 60 which form the heat exchange portion 80A are illustrated as a first heat exchanger 30A and a vortex generating device 60A, respectively
  • the first heat exchanger 30 and the vortex generating device 60 which form the heat exchange portion 80B are illustrated as a first heat exchanger 30B and a vortex generating device 60B, respectively.
  • heat exchange portion 80A and the heat exchange portion 80B are correctively referred to as a heat exchange unit 80.
  • the first fan 31 When the first fan 31 is rotated, air is sent to the heat exchange unit 80.
  • the air is first supplied to the heat exchange portion 80A.
  • the air sent by the first fan 31 passes through the vortex generating device 60A before flowing into the first heat exchanger 30A.
  • the vortex generating device 60A changes the flow of air that is a laminar flow into a turbulent flow.
  • the flow of air having changed into a vortex flow is supplied to the heat exchange portion 80B after passing through the first heat exchanger 30A.
  • the air passing through the heat exchange portion 80A passes through the first heat exchanger 30A, it is regulated, and the vortex flow shrinks or disappears.
  • the vortex generating device 60B is provided upstream of the first heat exchanger 30B in the heat exchange portion 80B as well, and air flowing from the heat exchange portion 80A is changed into a vortex flow by the vortex generating device 60B.
  • the above operation is performed by the entire heat exchange unit 80, whereby the heat exchange performance to be achieved by the vortex generating device 60 can be promoted by the entire heat exchange unit 80. That is, in the heat exchange unit 80, even in the case where a plurality of heat exchange portions each consisting of the first heat exchanger 30 and the vortex generating device 60 are arranged in a row, it is possible to promote the heat exchange performance because of provision of the vortex generating device 60 in each group.
  • Fig. 10 is a perspective view illustrating another example of the configurations of the first heat exchanger 30 and the vortex generating device 60 provided in the refrigeration cycle apparatus according to embodiment 3 of the present invention.
  • Fig. 11 is an exploded perspective view illustrating a further example of the configurations of the first heat exchanger 30 and the vortex generating device 60 provided in the refrigeration cycle apparatus according to embodiment 3 of the present invention.
  • Fig. 12 is a side view illustrating the further example of the configurations of the first heat exchanger 30 and the vortex generating device 60 provided in the refrigeration cycle apparatus according to embodiment 3 of the present invention.
  • the examples of the first heat exchanger 30 and the vortex generating device 60 provided in the refrigeration cycle apparatus according to embodiment 3 of the present invention will be described in detail with reference to Figs. 10 to 12 .
  • Figs. 8 and 9 illustrate by way of example the case in which the heat exchange unit 80 includes two groups of heat exchange portions in a row.
  • Figs. 10 to 12 illustrate by way of example the case where the heat exchange unit 80 includes three or more groups of heat exchange portions in a row.
  • a heat exchange portion 80A, a heat exchange portion 80B ... and a heat exchange portion 80N are illustrated in this order from a windward side, and each of these heat exchange portions is provided as a single group consisting of the first heat exchanger 30 and the vortex generating device 60.
  • the first heat exchanger 30 and the vortex generating device 60 which form the heat exchange portion 80N are illustrated as a first heat exchanger 30N and a vortex generating device 60N, respectively. That is, any number of heat exchange portions may be provided between the heat exchange portion 80B and the heat exchange portion 80N.
  • the heat exchange unit 80 includes three or more groups of heat exchange portions in a row, it is possible to promote the heat exchange performance of the entire heat exchange unit 80 because of provision of the vortex generating devices 60, since in each of heat exchange portions, the vortex generating device 60 is located upstream of the first heat exchanger 30 in each heat exchange portion.
  • measures against dew condensation or frost formation at the vortex generating device 60 are taken by setting the distance x, which is described with respect to embodiment 2, between the first heat exchanger 30 and the vortex generating device 60.
  • the first heat exchanger 30 and the vortex generating device 60 of each of the heat exchange portions which form the heat exchange unit 80 are provided not in contact with each other in order that the temperature of the flat tube 33 of the first heat exchanger 30 should not be transferred to the vortex generating device 60 by the thermal conduction.
  • the distances x in all the heat exchange portions may be set to the same value, or it may be set that the closer an exchange portion to the downstream end, the greater (smaller) the distance x in the exchange portion. That is, the distances x in all the heat exchange portions may be set to the same value or different values, or some of the distances x may be set to the same value.
  • the vortex generating devices 60 of the heat exchange unit need to be provided upstream of the respective first heat exchangers 30. It suffices that in each of at least the first two of all the heat exchange portions from the upstream end, the vortex generating device 60 is provided upstream of the first heat exchanger 30.
  • various types of fans such as a propeller fan, a cross-flow fan, a sirocco fan and a turbofan can be used as the first fan 31 which sends air to the first heat exchanger 30 and the vortex generating device 60.
  • a comparatively regulated flow of air is supplied to the vortex generating device 60, more stable vortexes can be generated at the vortex generating device 60, and the heat exchange performance of the first heat exchanger 30 is improved.
  • a preferable example of the arrangement of the first heat exchanger 30 and the vortex generating device 60 which varies in accordance with the type of the fan used as the first fan 31, will be described.
  • Fig. 13 is a side view illustrating an example of the configuration of a refrigeration cycle apparatus according to embodiment 4 of the present invention.
  • an outlined arrow indicates the flow direction of air which is sent by the first fan 31, and the refrigeration cycle apparatus according to embodiment 4 of the present invention is illustrated as a refrigeration cycle apparatus 100A.
  • the refrigeration cycle apparatus 100A as illustrated in Fig. 13 employs a propeller fan 31A as the first fan 31.
  • a flow of air on a blowing side of the propeller fan 31A flows while swirling about a rotation axis of the propeller fan 31A.
  • a flow of air on a suction side of the propeller fan 31A is regulated, as compared with the flow of air on the blowing side.
  • the propeller fan 31A be provided downstream of the first heat exchanger 30 in the flow direction of air which is sent by the propeller fan 31A.
  • the propeller fan 31A By disposing the propeller fan 31A in this manner, a comparatively regulated flow of air can be supplied to the vortex generating device 60, and as a result, stable vortexes can be generated at the vortex generating device 60.
  • the heat exchange performance of the first heat exchanger 30 can be improved.
  • Fig. 14 is a diagram additionally illustrating a velocity distribution of a flow of air which flows into the vortex generating device 60 in the refrigeration cycle apparatus 100A as illustrated in Fig. 13 .
  • the propeller fan 31A is provided downstream of the first heat exchanger 30 in the flow direction of air which is sent by the propeller fan 31A, a comparatively regulated flow of air can be supplied to the vortex generating device 60.
  • the velocity of the flow of air which flows into the vortex generating device 60 varies in accordance with which part of the vortex generating device 60 the flow of air flows into.
  • the velocity of a flow of air is lower at part of the vortex generating device 60 where a flow of air to be sucked toward the outer periphery of the propeller fan 31A passes than in part of the vortex generating device 60 where a flow of air to be sucked toward a center portion of the propeller fan 31A passes.
  • the air velocity is low, vortexes are not easily generated, as compared with part of the vortex generating device 60 where the air velocity is high.
  • the number of vortexes generated is small, and the heat exchange performance is lower at the part of the first heat exchanger 30 where the above flow of air passes than in part of the first heat exchanger 30 where a flow of air having a high air velocity passes.
  • a larger number of vane structures 600 may be provided in part of the vortex generating device 60 than at part thereof where the air velocity is higher than that at the above former part.
  • Fig. 15 is a side view illustrating another example of the configuration of the refrigeration cycle apparatus according to embodiment 4 of the present invention. It should be noted that outlined arrows in Fig. 15 indicate flow directions of air which is sent by the first fan 31. In Fig. 15 , the refrigeration cycle apparatus according to embodiment 4 of the present invention is illustrated as a refrigeration cycle apparatus 100B.
  • the refrigeration cycle apparatus 100B as illustrated in Fig. 15 employs a cross-flow fan 31B as the first fan 31.
  • the refrigeration cycle apparatus 100B as illustrated in Fig. 15 includes a housing 90 having an air outlet 91.
  • the cross-flow fan 31B is provided in the housing 90 in such a way as to cover a region located above the air outlet 91.
  • air is sucked from an upper portion of the cross-flow fan 31B and is blown out from a lower portion of the cross-flow fan 31B toward the air outlet 91.
  • a flow of air at an inlet of the cross-flow fan 31B is regulated comparatively.
  • the cross-flow fan 31B be employed as the first fan 31, it is preferable that the cross-flow fan 31B be provided downstream of the first heat exchanger 30 in the flow direction of air which is sent by the cross-flow fan 31B.
  • the cross-flow fan 31B is provided in such a manner, a comparatively regulated flow of air can be supplied to the vortex generating device 60, and as a result stable vortexes can be generated at the vortex generating device 60. It is therefore possible to improve the heat exchange performance of the first heat exchanger 30.
  • the velocity of the flow of air which flows into the vortex generating device 60 varies in accordance with which part of the vortex generating device 60 the flow of air flows into. Therefore, also in the refrigeration cycle apparatus 100B as illustrated in Fig. 15 , it is preferable that a larger number of vane structures 600 be provided in part of the vortex generating device 60 than at part thereof where the air velocity of the flow of air is higher than that at the former part.
  • Fig. 16 is a plan view illustrating a further example of the configuration of the refrigeration cycle apparatus according to embodiment 4 of the present invention.
  • Fig. 17 is a side view illustrating the further example of the configuration of the refrigeration cycle apparatus according to embodiment 4 of the present invention as is illustrated in Fig. 16 .
  • outlined arrows in Figs. 16 and 17 indicate flow directions of air which is sent by the first fan 31.
  • Figs. 16 and 17 illustrate a cross section of a casing 95 in which a sirocco fan 31C is provided.
  • the refrigeration cycle apparatus according to embodiment 4 of the present invention is illustrated as a refrigeration cycle apparatus 100C.
  • the refrigeration cycle apparatus 100C as illustrated in Figs. 16 and 17 employs the sirocco fan 31C as the first fan 31.
  • the sirocco fan 31C is provided in, for example, the casing 95.
  • an air inlet 93 is formed at a position where the air inlet 93 faces a rotation axis of the sirocco fan 31C.
  • an air outlet 94 is formed to face an outer circumferential surface of the sirocco fan 31C.
  • the sirocco fan 31C be provided upstream of the vortex generating device 60 in the flow direction of air which is sent by the sirocco fan 31C.
  • the sirocco fan 31C is provided in such a manner, a comparatively regulated flow of air can be supplied to the vortex generating device 60, and as a result stable vortexes can be generated at the vortex generating device 60.
  • the heat exchange performance of the first heat exchanger 30 can be improved.
  • the velocity of the flow of air which flows into the vortex generating device 60 varies in accordance with which part of the vortex generating device 60 the flow of air flows into. Therefore, also in the refrigeration cycle apparatus 100C as illustrated in Figs. 16 and 17 , it is preferable that a larger number of vane structures 600 be provided at part of the vortex generating device 60 than at part thereof where the air velocity is higher than that at the above former part.
  • Fig. 18 is a plan view illustrating a still another example of the configuration of the refrigeration cycle apparatus according to embodiment 4 of the present invention.
  • Fig. 19 is a side view illustrating the still another configuration of the refrigeration cycle apparatus according to embodiment 4 of the present invention as illustrated in Fig. 18 .
  • outlined arrows in Figs. 18 and 19 indicate flow directions of air which is sent by the first fan 31.
  • the refrigeration cycle apparatus according to embodiment 4 of the present invention is illustrated as a refrigeration cycle apparatus 100D.
  • the refrigeration cycle apparatus 100D as illustrated in Figs. 18 and 19 employs a turbofan 31D as the first fan 31.
  • a turbofan 31D as the first fan 31.
  • air is sucked in the direction of the rotational axis of the turbofan 31D.
  • air is blown out toward an outer periphery of the turbofan 31D.
  • a flow of air at an outlet of the turbofan 31D is regulated comparatively.
  • the turbofan 31D be employed as the first fan 31, it is preferable that the turbofan 31D be provided upstream of the vortex generating device 60 in the flow direction of air which is sent by the turbofan 31D. Therefore, in the refrigeration cycle apparatus 100D as illustrated in Figs. 18 and 19 , the vortex generating device 60 is located to surround the outer periphery of the turbofan 31D. Furthermore, the first heat exchanger 30 is located to surround the outer periphery of the vortex generating device 60. Because of this location of the turbofan 31D, a comparatively regulated flow of air can be supplied to the vortex generating device 60 and as a result, stable vortexes can be generated at the vortex generating device 60. Thus, the heat exchange performance of the first heat exchanger 30 can be improved.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)

Claims (14)

  1. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D), umfassend:
    einen ersten Wärmetauscher (30, 30A, 30B, 30N), der ein rippenloser Wärmetauscher ist und eine Vielzahl von Wärmeübertragungsleitungen (33, 33A, 33B) aufweist, die sich in einer Schwerkraftrichtung erstrecken;
    einen Lüfter (31), der eingerichtet ist, Luft zu dem ersten Wärmetauscher (30, 30A, 30B, 30N) zu senden;
    eine Wirbelerzeugungseinrichtung (60, 60A, 60B, 60N), die stromaufwärts des ersten Wärmetauschers (30, 30A, 30B, 30N) vorgesehen ist und eingerichtet ist, die Luft, die durch den Lüfter (31) zum ersten Wärmetauscher (30, 30A, 30B, 30N) gesendet werden soll, zu veranlassen, sich in eine Wirbelströmung zu verändern;
    gekennzeichnet durch einen Abstandshalter, der zwischen dem ersten Wärmetauscher (30, 30A, 30B, 30N) und der Wirbelerzeugungseinrichtung (60, 60A, 60B, 60N) vorgesehen ist, so dass die Wirbelerzeugungseinrichtung (60, 60A, 60B, 60N) von dem ersten Wärmetauscher (30, 30A, 30B, 30N) durch einen ersten Raum (41) beabstandet ist.
  2. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach Anspruch 1, wobei der Abstandshalter eine von dem ersten Wärmetauscher (30) und der Wirbelerzeugungseinrichtung (60, 60A, 60B, 60N) getrennte Komponente ist.
  3. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach Anspruch 1 oder Anspruch 2, wobei der Abstandshalter aus einem Material hergestellt ist, das eine geringere Wärmeleitfähigkeit als der erste Wärmetauscher (30, 30A, 30B, 30N) und die Wirbelerzeugungseinrichtung (60, 60A, 60B, 60N) aufweist.
  4. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach Anspruch 1, wobei der Abstandshalter ein Produkt ist, das einstückig mit der Wirbelerzeugungseinrichtung (60, 60A, 60B, 60N) geformt ist.
  5. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach Anspruch 1, wobei der Abstandshalter ein Produkt ist, das einstückig mit dem ersten Wärmetauscher (30, 30A, 30B, 30N) geformt ist.
  6. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach einem der Ansprüche 1 bis 3, wobei der Abstandshalter in Form eines quadratischen Rings ausgebildet ist und auf mindestens einer von einander zugewandten Oberflächen des ersten Wärmetauschers (30, 30A, 30B, 30N) und der Wirbelerzeugungseinrichtung (60, 60A, 60B, 60N) vorgesehen ist.
  7. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach einem der Ansprüche 1 bis 6, wobei der erste Abstandshalter (41) eingestellt ist, in einen Bereich von 1 mm bis 5 mm zu fallen.
  8. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach einem der Ansprüche 1 bis 7, wobei eine Vielzahl von Wärmetauschabschnitten (80A, 80B, 80N) in einer Reihe in einer Strömungsrichtung von Luft angeordnet sind, wobei jeder der Wärmetauschabschnitte (80A, 80B, 80N) den ersten Wärmetauscher (30, 30A, 30B, 30N) und die Wirbelerzeugungseinrichtung (60, 60A, 60B, 60N) als eine einzige Gruppe aufweist.
  9. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach einem der Ansprüche 1 bis 8,
    wobei die Wärmeübertragungsleitungen (33, 33A, 33B) flache Leitungen (33, 33A, 33B) sind, die jeweils einen länglichen Querschnittsbereich aufweisen, und
    wobei die flachen Leitungen (33, 33A, 33B) so angeordnet sind, dass eine Richtung einer Hauptachse des länglichen Querschnittsbereichs jeder der flachen Leitungen parallel zur Strömungsrichtung von Luft ist.
  10. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach einem der Ansprüche 1 bis 9,
    wobei die Wirbelerzeugungseinrichtung (60, 60A, 60B, 60N) umfasst:
    Stützkörper (601, 603); und
    Schaufelkörper (602, 702), die an den Stützkörpern (601, 603) vorgesehen sind, und wobei zwischen den Stützkörpern (601, 603) und den Schaufelkörpern (602, 702) entsprechende zweite Räume (CL) vorgesehen sind, um der von dem Lüfter (31, 31A, 31B, 31C, 31D) gesendeten Luft zu ermöglichen, dort hindurch zu dem ersten Wärmetauscher (30, 30A, 30B, 30N) zu strömen.
  11. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach einem der Ansprüche 1 bis 10, wobei der Lüfter (31) stromaufwärts oder stromabwärts des ersten Wärmetauschers (30, 30A, 30B, 30N) vorgesehen ist.
  12. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach Anspruch 11, wobei der Lüfter (31) ein Propellerlüfter (31A) oder ein Querstromlüfter (31B) ist und stromabwärts des ersten Wärmetauschers (30, 30A, 30B, 30N) vorgesehen ist.
  13. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach Anspruch 11, wobei der Lüfter (31) ein Sirocco-Lüfter (31C) oder ein Turbolüfter (31D) ist und stromaufwärts des ersten Wärmetauschers (30, 30A, 30B, 30N) vorgesehen ist.
  14. Kältekreislaufvorrichtung (100, 100A, 100B, 100C, 100D) nach einem der Ansprüche 1 bis 13, ferner umfassend einen Kältemittelkreislauf, in dem ein Verdichter (10), der erste Wärmetauscher (30, 30A, 30B, 30N), eine Expansionseinrichtung (40) und ein zweiter Wärmetauscher (50) durch Kältemittelleitungen (70) verbunden sind, und
    wobei der erste Wärmetauscher (30, 30A, 30B, 30N) als ein Verdampfer verwendet wird.
EP16918265.6A 2016-10-04 2016-10-04 Kältekreislaufvorrichtung Active EP3524915B1 (de)

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WO2018066066A1 (ja) 2018-04-12

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