WO2018003123A1 - 熱交換器及び冷凍サイクル装置 - Google Patents
熱交換器及び冷凍サイクル装置 Download PDFInfo
- Publication number
- WO2018003123A1 WO2018003123A1 PCT/JP2016/069707 JP2016069707W WO2018003123A1 WO 2018003123 A1 WO2018003123 A1 WO 2018003123A1 JP 2016069707 W JP2016069707 W JP 2016069707W WO 2018003123 A1 WO2018003123 A1 WO 2018003123A1
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- WIPO (PCT)
- Prior art keywords
- heat exchanger
- water
- drainage
- fin
- heat transfer
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- 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
-
- 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
-
- 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
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
-
- 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
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from 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
- 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
- F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
- F28D2021/0064—Vaporizers, e.g. evaporators
-
- 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
- F28F2215/08—Fins with openings, e.g. louvers
-
- 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
- F28F2215/12—Fins with U-shaped slots for laterally inserting conduits
-
- 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
- F28F2265/14—Safety or protection arrangements; Arrangements for preventing malfunction for preventing damage by freezing, e.g. for accommodating volume expansion
-
- 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
- F28F2265/22—Safety or protection arrangements; Arrangements for preventing malfunction for draining
Definitions
- the present invention relates to a fin tube type heat exchanger and a refrigeration cycle apparatus including the heat exchanger.
- a fin tube comprising a plurality of plate-like fins arranged with a predetermined fin pitch interval and a plurality of flat heat transfer tubes (hereinafter referred to as flat tubes) having a horizontal width larger than a vertical width.
- a type of heat exchanger is known.
- a fin tube type heat exchanger using a flat tube is referred to as a flat tube heat exchanger.
- the flat tube heat exchanger can secure a large heat transfer area in the tube and can suppress the ventilation resistance of the heat exchange fluid. Can be improved.
- drainage when a heat exchanger using a flat tube is used as an evaporator due to its cross-sectional shape, water drops tend to remain on the tube surface (flat surface) of the flat tube. It is inferior compared.
- a flat tube heat exchanger is used as a heat source side heat exchanger mounted on an outdoor unit of an air conditioner that is an example of a refrigeration cycle apparatus
- moisture in the air that is a heat exchange fluid is condensed during heating operation. Then, it adheres to the heat source side heat exchanger and becomes frost.
- an air conditioner In order to prevent an increase in ventilation resistance due to frost formation, a decrease in heat transfer performance, and damage to a heat exchanger, an air conditioner generally has a defrosting operation mode.
- water droplets remain in the heat source side heat exchanger, the water droplets freeze again and grow into larger frosts. Therefore, when the drainage property of the heat source side heat exchanger is poor, it is necessary to lengthen the time for the defrosting operation, resulting in a decrease in comfort and a decrease in average heating capacity.
- Patent Document 1 states that in a fin-and-tube heat exchanger in which a flat tube is inserted into a vertical flat fin having a plurality of notches from the side, the flat tube is inserted from the downstream direction of the air flow.
- a fin-and-tube heat exchanger is disclosed in which notches are provided on the fin surface so that the cross section of the flat tube is inclined upward with respect to the air flow.
- the flat tube is inclined with respect to the air flow, so that the condensed water staying on the upper surface of the flat tube is easily discharged by the action of gravity. Therefore, according to the heat exchanger disclosed in Patent Document 1, it is possible to suppress the dew jumping and to reduce the defrosting time. On the other hand, in order to obtain such an effect sufficiently, it is necessary to increase the inclination angle of the flat tube. When the inclination angle of the flat tube is increased, the air flowing into the heat exchanger is peeled off at the front edge of the flat tube, thereby impairing the heat transfer performance, which is an advantage of the flat tube.
- the dew condensation water tends to stay on the upper and lower surfaces of the flat tube. If the drainage of the condensed water is poor, the condensed water staying on the upper and lower surfaces of the flat tube causes corrosion of the fins and tubes. Corrosion of the fins and tubes leads to a decrease in the reliability of the heat exchanger.
- the present invention has been made against the background of the above problems, and provides a heat exchanger that achieves both improved drainage and secures heat transfer performance, and a refrigeration cycle apparatus including the heat exchanger.
- the purpose is to do.
- the heat exchanger according to the present invention includes fins extending in the direction of gravity and a plurality of heat transfer tubes mounted so as to intersect the fins, and the plurality of heat transfer tubes are arranged in parallel in the direction of gravity.
- the fin has a water transfer region disposed above and below each of the plurality of heat transfer tubes, and a drain region disposed on one side of each of the plurality of heat transfer tubes,
- the water conveyance area has a water conveyance structure for guiding water to the drainage area, and the drainage area has a drainage structure for guiding water in the direction of gravity.
- the refrigeration cycle apparatus includes a refrigerant circuit in which a compressor, a first heat exchanger, a throttling device, and a second heat exchanger are connected by a refrigerant pipe, and the heat exchanger is connected to the first heat exchange. And at least one of the second heat exchanger.
- the fin water guiding region has a water guiding structure that guides water to the draining region, and the fin draining region has a draining structure that guides water in the direction of gravity.
- the drained water can easily flow downward from the drainage area, the drainage performance is improved, and the air ventilation path is not blocked by water icing or the like, so that heat transfer performance can be secured.
- the refrigeration cycle apparatus according to the present invention uses the above-described heat exchanger, the drainage of water droplets generated by the heat exchanger is greatly improved, so that heat transfer performance can be secured in the same manner.
- FIG. 1 It is sectional drawing which shows schematically a part of structural example of the finned-tube type heat exchanger which concerns on Embodiment 1 of this invention. It is the schematic diagram which looked at a part of example of composition of a fin tube type heat exchanger concerning Embodiment 1 of the present invention from three directions. It is a side view which shows roughly the structural example of the fin which comprises the finned-tube type heat exchanger which concerns on Embodiment 1 of this invention. It is sectional drawing which shows roughly the structural example of the heat exchanger tube which comprises the finned-tube type heat exchanger which concerns on Embodiment 1 of this invention. BRIEF DESCRIPTION OF THE DRAWINGS FIG.
- FIG. 1 is a schematic perspective view illustrating an example of an overall appearance configuration of a finned tube heat exchanger according to Embodiment 1 of the present invention. It is a block diagram which shows an example of the specific structural example of the fin which comprises the finned-tube type heat exchanger which concerns on Embodiment 1 of this invention. It is a block diagram which shows another example of the specific structural example of the fin which comprises the finned-tube type heat exchanger which concerns on Embodiment 1 of this invention. It is a block diagram which shows another example of the specific structural example of the fin which comprises the finned-tube type heat exchanger which concerns on Embodiment 1 of this invention.
- FIG. 1 is a cross-sectional view schematically showing a part of a configuration example of a finned tube heat exchanger (hereinafter referred to as a heat exchanger 500) according to Embodiment 1 of the present invention.
- FIG. 2 is a schematic view of a part of the configuration example of the heat exchanger 500 as viewed from three directions.
- FIG. 3 is a side view schematically showing a configuration example of the fin 1 constituting the heat exchanger 500.
- FIG. 4 is a cross-sectional view schematically showing a configuration example of the heat transfer tube 2 constituting the heat exchanger 500.
- FIG. 5 is a schematic perspective view showing an example of the overall appearance configuration of the heat exchanger 500. The heat exchanger 500 will be described with reference to FIGS.
- FIG. 1 also shows a schematic view of the fin 1 in a top view and a side view.
- (a) is a side view of the heat exchanger 500 as viewed from the air flow direction
- (b) is a side view of the heat exchanger 500 as viewed from the extending direction of the heat transfer tube 2.
- c) is a top view of the heat exchanger 500 as viewed from above.
- the flow of air is indicated by white arrows.
- the heat exchanger 500 includes a plurality of plate-like fins 1 that are arranged at a predetermined interval and through which a fluid such as air flows, and a plurality of heat transfer tubes 2 that are inserted into the fins 1 in the axial direction. Yes.
- the plurality of fins 1 are formed of a plate-like member that is extended so that the direction of gravity is long.
- the plurality of fins 1 are arranged with a predetermined fin pitch Fp in a direction (arrow Y direction) perpendicular to the air flow direction and perpendicular to the gravity direction.
- the plurality of heat transfer tubes 2 are arranged so as to extend in the arrow Y direction and cross the plurality of fins 1.
- the plurality of fins 1 and the plurality of heat transfer tubes 2 are in close contact with each other by brazing.
- the fin 1 has a water guide region 1 a disposed above and below the heat transfer tube 2 and a drain region 1 b disposed on a side portion of the heat transfer tube 2.
- the water guide region 1a is a region in which a plurality of notches 10 are arranged in the longitudinal direction of the fin 1 that is the direction of gravity, and is a region where the heat transfer tube 2 is inserted and adhered. That is, the water conveyance area
- the fin 1 has a notch 10 cut out in a shape along the outer diameter of the heat transfer tube 2 from one side (the left side in FIG. 3) to the other side (the right side in FIG. 3). Have. An end on the other side of the notch 10 is referred to as a back portion 10a, and an end on one side of the notch 10 is referred to as an insertion portion 10b.
- the back portion 10a has a fillet shape as shown in FIG.
- the shape of the back portion 10a is not limited to the fillet shape, and may be an elliptical shape. That is, the inner portion 10 a only needs to be formed according to the shape of the heat transfer tube 2.
- a straight line in the direction of gravity passing through the extreme end of the back portion 10a is a boundary line between the water guide region 1a and the drainage region 1b (a chain line A shown in FIG. 3).
- the insertion portion 10b has a shape that widens from the other side of the fin 1 toward the one side. By making the insertion part 10b into such a shape, the heat transfer tube 2 can be easily inserted into the notch part 10.
- the distance in the gravity direction between the notches 10 adjacent to each other in the vertical direction is constant at the step pitch Dp.
- the fin 1 is made of, for example, aluminum or aluminum alloy.
- the plurality of heat transfer tubes 2 are attached to the plurality of notches 10 of the fin 1 and intersect the fin 1. Since the plurality of heat transfer tubes 2 are attached to the notches 10 of the fins 1, they are arranged in parallel in the direction of gravity. As shown in FIG. 1, the heat transfer tube 2 is configured in a shape in which the horizontal width (cross-sectional major axis direction) is larger than the vertical width (cross-sectional minor axis direction). That is, the plurality of heat transfer tubes 2 are arranged such that the direction of the long axis is the flow direction of the fluid flowing between the fins 1 and spaced in the step direction (vertical direction in the drawing) perpendicular to the flow direction.
- the long axis of the heat transfer tube 2 that is, the portion extending in the width direction of the fin 1 may be referred to as the width of the heat transfer tube 2.
- the heat transfer tube 2 is a flat tube will be described as an example.
- the heat transfer tube 2 does not have to be strictly configured in a flat shape, and the heat transfer tube 2 has a width that is greater than the vertical width. If it is.
- the heat transfer tube 2 includes an upper surface 2a including a flat upper portion, a lower surface 2c including a flat lower portion, and one end in the width direction (the left end in FIG. 4).
- the side portion 2d and the other side portion 2b including the other end portion in the width direction (the end portion on the right side in FIG. 4) are included.
- 4 shows an example of the heat transfer tube 2 in which the upper surface 2a and the lower surface 2c are parallel, but the upper surface 2a or the lower surface 2c is inclined so that the upper surface 2a and the lower surface 2c are not parallel. Also good.
- each of the one side portion 2d and the other side portion 2b is an arc shape, that is, a fillet shape.
- the other side 2 b is located on the back 10 a side of the notch 10 formed in the fin 1, and the one side 2 d is formed on the fin 1.
- the notch 10 is located on the insertion portion 10b side.
- the distance in the gravity direction between the heat transfer tubes 2 adjacent in the vertical direction is constant at the step pitch Dp.
- the heat transfer tube 2 is made of, for example, aluminum or aluminum alloy.
- a plurality of partition walls 2A are formed inside the heat transfer tube 2, and a plurality of refrigerant channels 20 are formed inside the heat transfer tube 2 by the partition walls 2A.
- a groove or a slit may be formed on the surface of the partition wall 2 ⁇ / b> A and the inner wall surface of the heat transfer tube 2.
- the heat transfer tube 2 is formed so that the upper surface 2a and the lower surface 2c are substantially symmetric with respect to a vertical line passing through the center portion in the width direction. Thereby, it becomes easy to ensure the manufacturability when the heat transfer tube 2 is extruded.
- FIG. 6 is a configuration diagram illustrating an example of a specific configuration example of the fins 1 constituting the heat exchanger 500.
- One specific example of the configuration of the fin 1 will be described in detail with reference to FIGS.
- the air circulation direction is indicated by an arrow X
- the direction in which the fins 1 are arranged is indicated by an arrow Y
- the direction of gravity is indicated by an arrow Z.
- the part into which the four heat exchanger tubes 2 are inserted in the fin 1 is expanded and shown.
- the fin 1 has a water introduction region 1a and a drainage region 1b. And the fin 1 has the water guide structure which guide
- the water guide structure is formed in at least a part of the water guide region 1a. Specifically, the water guide structure is formed by forming a part of the members constituting the fin 1 into a corrugated shape in which the ridge line is parallel to the X-axis direction.
- the corrugated water guide structure is referred to as a corrugated water guide structure 1a-1.
- the number of corrugated water conveyance structures 1a-1 is not particularly limited.
- the peaks of the corrugated peaks and troughs of the corrugated water guiding structure 1a-1 may be configured with an angle, or may be configured with curved surfaces as the R portion.
- the corrugated ridgeline of the corrugated water guiding structure 1a-1 does not have to be strictly parallel to the X-axis direction, and may be inclined with respect to the X-axis direction. If the corrugated ridgeline of the corrugated water guiding structure 1a-1 is inclined downward toward the drainage region 1b, it becomes easier to guide water to the drainage region 1b (see FIG. 9).
- the drainage structure is formed in at least a part of the drainage region 1b. Specifically, the drainage structure is formed by making a part of the members constituting the fin 1 corrugated so that the ridge line is parallel to the Z-axis direction.
- the corrugated drainage structure is referred to as corrugated drainage structure 1b-1.
- the number of corrugated corrugated drainage structures 1b-1 is not particularly limited. Further, the tops of the corrugated peaks and troughs of the corrugated drainage structure 1b-1 may be configured with an angle, or may be configured with curved surfaces as the R portion. 1 and 6 show an example in which the corrugated drainage structure 1b-1 is separated at the position where the notch 10 is formed, but as shown in FIG. 2, the corrugated drainage structure 1b- All of 1 may be connected.
- FIG. 1 and 6 show an example in which the wave-type water conveyance structure 1a-1 and the wave-type drainage structure 1b-1 are separated from each other.
- the present invention is not limited to this, and FIG. As shown, the wave-type water guiding structure 1a-1 and the wave-type drainage structure 1b-1 may be connected. In the case where the corrugated water guiding structure 1a-1 and the corrugated drainage structure 1b-1 are separated from each other, the distance between them is not particularly limited.
- a slit in which a part of the fin 1 is cut and raised may be formed in the fin 1.
- the slit functions to promote heat transfer between the air flowing through the ventilation path between the fins 1 and the fins 1 by reducing resistance associated with heat transfer.
- the formation position is not particularly limited.
- the slit is formed in at least a part of the water conveyance region 1a (that is, the wave-type water conveyance structure 1a-1) or the drainage region 1b (that is, the wave-type drainage structure 1b -1) can be formed at least in part, or can be formed in at least part of each of both.
- FIG. 7 is a configuration diagram showing another example of a specific configuration example of the fins 1 constituting the heat exchanger 500. Based on FIG. 7, one specific configuration example of the fin 1 will be described in detail.
- the air flow direction is indicated by an arrow X
- the direction in which the fins 1 are arranged is indicated by an arrow Y
- the direction of gravity is indicated by an arrow Z.
- the part into which the four heat exchanger tubes 2 are inserted in the fin 1 is shown expanding.
- the water guide structure may be formed by forming a part of the members constituting the fin 1 into a dimple shape.
- the dimple-shaped water guide structure is referred to as a dimple water guide structure 1a-2.
- the number of dimples in the dimple water guiding structure 1a-2 is not particularly limited. Further, the dimple depth of the dimple water guide structure 1a-2 and the distance between the dimples are not particularly limited. Further, the top of the dimple of the dimple water guiding structure 1a-2 may be configured with an angle, or may be configured with a curved surface as the R portion. Further, the size of each dimple constituting the dimple water guiding structure 1a-2 does not need to be uniform, and may be all different or may be partially different.
- the drainage structure may be formed by forming a part of the members constituting the fin 1 into a dimple shape.
- the dimple-shaped drainage structure is referred to as a dimple drainage structure 1b-2.
- the number of dimples in the dimple drainage structure 1b-2 is not particularly limited. Further, the dimple depth of the dimple drainage structure 1b-2 and the distance between the dimples are not particularly limited. In addition, the top of the dimple of the dimple drainage structure 1b-2 may be configured with an angle, or may be configured with a curved surface as the R portion. Further, the size of each dimple constituting the dimple drainage structure 1b-2 does not have to be uniform, and may be all different or partially different.
- the dimples of the dimple water conveyance structure 1a-2 and the dimples of the dimple drainage structure 1b-2 may be the same, or the density state may be changed.
- the density By changing the density, the surface tension can be adjusted, and it is easy to create a flow of water from the water guiding region 1a toward the drainage region 1b. That is, by making a shape difference between the shape of the water conveyance region 1a and the shape of the drainage region 1b, a water flow from the water conveyance region 1a toward the drainage region 1b is easily formed.
- the density state can be changed by adjusting the distance between the dimples in the dimple water guide structure 1a-2 and the distance between the dimples in the dimple drainage structure 1b-2.
- the density state may be changed by adjusting the height of each dimple in the dimple water guiding structure 1a-2 and the height of each dimple in the dimple drainage structure 1b-2.
- the dimple height refers to the height from the fin 1 to the top of the dimple when the fin 1 is viewed as the bottom surface.
- FIG. 1 and 7 show an example in which the dimple water guiding structure 1a-2 and the dimple draining structure 1b-2 are separated from each other, but the present invention is not limited to this, and the dimple water guiding structure 1a- 2 and the dimple drainage structure 1b-2 may be connected.
- the distance between the two is not particularly limited.
- a slit in which a part of the fin 1 is cut and raised may be formed in the fin 1.
- the slit functions to promote heat transfer between the air flowing through the ventilation path between the fins 1 and the fins 1.
- the formation position is not particularly limited.
- the slit is formed in at least a part of the water conveyance region 1a (that is, the dimple water conveyance structure 1a-2) or the drainage region 1b (that is, the dimple drainage structure 1b-2). It is possible to form at least a part of each of them or at least a part of each of both.
- FIG. 8 is a configuration diagram showing still another example of a specific configuration example of the fin 1 constituting the heat exchanger 500. Based on FIG. 8, one specific configuration example of the fin 1 will be described in detail.
- the air flow direction is indicated by an arrow X
- the direction in which the fins 1 are arranged is indicated by an arrow Y
- the direction of gravity is indicated by an arrow Z.
- the part into which the four heat exchanger tubes 2 are inserted in the fin 1 is expanded and shown.
- a water guide structure may be configured by forming a slit in a part of the members constituting the fin 1.
- the water guide structure in which the slit is formed is referred to as a slit water guide structure 1a-3.
- the number of slits in the slit water guiding structure 1a-3 is not particularly limited. Further, the size and shape of the slit of the slit water guiding structure 1a-3 are not particularly limited. Further, the size of each slit of the slit water guiding structure 1a-3 does not have to be uniform, and may be all different or may be partially different. Furthermore, although the case where the slit water guiding structure 1a-3 is inclined with respect to the X-axis direction is shown as an example, the present invention is not limited to this, and the slit water guiding structure 1a-3 may not be inclined with respect to the X-axis direction.
- the drainage structure may be configured by forming a slit in a part of the members constituting the fin 1.
- the drainage structure in which the slit is formed is referred to as a slit drainage structure 1b-3.
- the number of slits in the slit drainage structure 1b-3 is not particularly limited. Further, the size and shape of the slit of the slit drainage structure 1b-3 are not particularly limited. Further, the sizes of the slits of the slit drainage structure 1b-3 do not have to be uniform, and may be all different or may be partially different.
- Specific examples of the combination of the water conveyance structure and the drainage structure include a wave-type water conveyance structure 1a-1, a wave-type drainage structure 1b-1, a dimple conveyance structure 1a-2, a dimple drainage structure 1b-2, and a slit conveyance structure 1a-3.
- the slit drainage structure 1b-3 has been described above, the combination of these can be changed as appropriate.
- the corrugated water conveyance structure 1a-1 and the dimple drainage structure 1b-2 can be combined, or the dimple water conveyance structure 1a-2 and the corrugated drainage structure 1b-1 can be combined. Further, these combinations may include the slit water guiding structure 1a-3 and the slit drainage structure 1b-3.
- FIG. 9 is a configuration diagram showing still another example of a specific configuration example of the fin 1 constituting the heat exchanger 500.
- FIG. 10 is a diagram showing the relationship between the inclination angle ⁇ of the heat transfer tube 2 of the heat exchanger 500, the heat transfer performance, and the drainage performance.
- One specific configuration example of the fin 1 will be described in detail with reference to FIGS. 9 and 10.
- the air flow direction is indicated by an arrow X
- the direction in which the fins 1 are arranged is indicated by an arrow Y
- the direction of gravity is indicated by an arrow Z.
- the portion where the four heat transfer tubes 2 are inserted into the fins 1 is shown in an enlarged manner.
- the vertical axis indicates the heat transfer performance and the drainage performance
- the horizontal axis indicates the inclination angle ⁇ .
- FIG. 6 illustrates an example in which the major axis of the notch 10 and the ridgeline of the wave-type water conveyance structure 1a-1 are parallel to the X-axis direction.
- An example in which the ridgeline of the wave-type water guiding structure 1a-1 is inclined with respect to the X-axis direction is shown. That is, the heat transfer tube 2 is attached to the fin 1 with the long axis inclined downward toward the drainage region 1b. By doing so, the water staying on the upper surface 2a of the heat transfer tube 2 and the water adhering to the wave-type water guiding structure 1a-1 can be more easily moved to the drainage region 1b, and the drainage performance is further improved.
- the inclined wave-type water conveyance structure is illustrated as the gradient wave-type water conveyance structure 1a-4.
- the heat exchanger 500 is configured, for example, by arranging two combinations of the fins 1 shown in FIG. 3 and the heat transfer tubes 2 shown in FIG. 4 at intervals in a direction parallel to the fluid flow direction.
- the combination of the fins 1 shown in FIG. 3 and the heat transfer tubes 2 shown in FIG. 4 may be arranged in two rows as an upwind heat exchanger 500A and a downwind heat exchanger 500B as shown in FIG. That is, the windward side heat exchanger 500A and the leeward side heat exchanger 500B are similarly configured by a combination of the fins 1 shown in FIG. 3 and the heat transfer tubes 2 shown in FIG.
- the combination of the fin 1 shown in any of FIGS. 6 to 9 and the heat transfer tube 2 shown in FIG. 4 is arranged in two rows as an upwind heat exchanger 500A and a leeward heat exchanger 500B as shown in FIG.
- the heat exchanger 500 may be configured.
- the windward side heat exchanger 500A is configured by a combination of the fin 1 shown in FIG. 7 and the heat transfer tube 2 shown in FIG. 4, and the leeward side heat exchanger 500B is shown in FIG. 8 and the fin 1 shown in FIG. A combination with the heat transfer tube 2 may be used.
- the heat exchanger 500 includes, for example, an upwind header collecting pipe 503, a leeward header collecting pipe 504, and an inter-column connection member 505 in addition to the upwind heat exchanger 500A and the leeward heat exchanger 500B. .
- FIG. 11 is a schematic diagram for explaining the flow of water generated in the heat exchanger 500. Based on FIG. 11, the operation of the heat exchanger 500 will be described. In FIG. 11, water generated in the heat exchanger 500 is illustrated as a water droplet W.
- FIG. 11 shows an example of a heat exchanger 500 that employs a wave-type water-conducting structure 1a-1 as a water-conducting structure and a wave-type water-draining structure 1b-1 as a drainage structure.
- the air blowing means is composed of, for example, a propeller fan, a motor, and a control device, and is arranged on the upstream side or the downstream side of the heat exchanger 500 so that the rotation shaft of the propeller fan is substantially horizontal.
- the air flow direction may flow into the heat exchanger 500 from the water conveyance region 1a side, or may flow into the heat exchanger 500 from the drainage region 1b side.
- the air flows between the plurality of fins 1 from the water conveyance area 1a side or the drainage area 1b side.
- the air that flows in from the water conveyance area 1a flows out from the drainage area 1b side.
- the air that flows in from the drainage area 1b flows out from the water conveyance area 1a side.
- the air that has reached the front edge of the heat transfer tube 2 is divided into two hands, an upper surface 2a and a lower surface 2c.
- the one side portion 2 d becomes the front edge of the heat transfer tube 2.
- the other side portion 2 b becomes the front edge of the heat transfer tube 2.
- the flow of air on the upper surface 2a will be described. Since the upper surface 2a is parallel to the air flow direction, air can flow along the upper surface 2a in almost the entire width direction of the heat transfer tube 2, and the air and the heat transfer tube 2 can be formed without causing large separation. Heat exchange with the surface can be facilitated. Moreover, ventilation resistance can be reduced.
- the water droplets W that have reached the upper surface 2a of the heat transfer tube 2 stay on the upper surface 2a of the heat transfer tube 2 and grow.
- the grown water droplets W are guided in the direction of the other side portion 2b and the one side portion 2d due to the shape of the heat transfer tube 2 when the size becomes a certain size or more.
- region 1b is discharged
- the water droplet W swells downward as it grows, and the influence of gravity increases. Then, when the gravity applied to the water drop W exceeds the force above the gravitational direction (arrow Z direction) such as the surface tension, the water drop W is not affected by the surface tension and detached from the lower surface 2c of the heat transfer tube 2, Fall down.
- the water droplet W separated from the lower surface 2c of the heat transfer tube 2 again flows downward along the water guide region 1a and reaches the upper surface 2a of the lower heat transfer tube 2.
- the water droplet W separated from the lower surface 2c of the heat transfer tube 2 flows to the other side 2b side, is guided to the drainage region 1b, is discharged to the lower side of the heat exchanger 500 through the drainage region 1b. That is, the water droplet W repeats the same behavior from the top to the bottom, and is finally drained from the bottom of the heat exchanger 500.
- the “water conveyance structure” is formed in the water conveyance area 1a, and the “drainage structure” is formed in the drainage area 1b. Therefore, the water droplet W adhering to the water guide region 1a is easily moved to the drainage region 1b side, and drainage performance is improved. Specifically, the water droplets W adhering to the water guide region 1a flow along the ridge line direction of the water guide structure formed in a corrugated shape, and therefore easily reach the drainage region 1b.
- the “water conveyance structure” is formed in the water conveyance area 1a and the “drainage structure” is formed in the drainage area 1b, so that the drainage performance is improved. Accordingly, in the heat exchanger 500, a portion serving as an air ventilation path is not blocked by icing or the like of the water droplets W, and the heat transfer performance can be significantly suppressed from being deteriorated. Moreover, according to the heat exchanger 500, since the “water conveyance structure” is formed in the water conveyance area 1a and the “drainage structure” is formed in the drainage area 1b, the surface areas of the water conveyance area 1a and the drainage area 1b are increased. Also, the heat transfer performance will be improved.
- the heat transfer tube 2 has been described as an example of a flat shape having a horizontal width larger than the vertical width.
- the heat transfer tube 2 is not limited to this, and a circular tube is adopted as the heat transfer tube 2. May be.
- the heat exchanger provided with the several fin 1 was demonstrated to the example, it is not limited to this, The fin 1 may be one.
- FIG. FIG. 12 is a circuit configuration diagram schematically showing an example of a refrigerant circuit configuration of the refrigeration cycle apparatus 100 according to Embodiment 2 of the present invention.
- the refrigeration cycle apparatus 100 will be described based on FIG. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.
- an air conditioner will be described as an example of the refrigeration cycle apparatus 100.
- cooling operation is shown by the broken line arrow
- coolant flow at the time of heating operation is shown by the solid line arrow.
- the refrigeration cycle apparatus 100 includes a compressor 33, a flow path switching device 39, a first heat exchanger 34, a throttling device 35, a second heat exchanger 36, and a blower 37.
- the compressor 33, the 1st heat exchanger 34, the expansion apparatus 35, and the 2nd heat exchanger 36 are connected by the refrigerant
- the blower 37 is attached to the first heat exchanger 34 and the second heat exchanger 36 and supplies air to the first heat exchanger 34 and the second heat exchanger 36.
- the blower 37 is rotated by a blower motor 38.
- the compressor 33 compresses the refrigerant.
- the refrigerant compressed by the compressor 33 is discharged and sent to the first heat exchanger 34.
- the compressor 33 can be comprised by a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor etc., for example.
- the first heat exchanger 34 functions as a condenser during heating operation and functions as an evaporator during cooling operation. That is, when functioning as a condenser, the first heat exchanger 34 exchanges heat between the high-temperature and high-pressure refrigerant discharged from the compressor 33 and the air supplied by the blower 37, and the high-temperature and high-pressure gas refrigerant condenses. . On the other hand, when functioning as an evaporator, the first heat exchanger 34 exchanges heat between the low-temperature and low-pressure refrigerant that has flowed out of the expansion device 35 and the air supplied by the blower 37, and the low-temperature and low-pressure liquid refrigerant or two-phase The refrigerant evaporates.
- the expansion device 35 expands and depressurizes the refrigerant that has flowed out of the first heat exchanger 34 or the second heat exchanger 36.
- the throttling device 35 may be constituted by, for example, an electric expansion valve that can adjust the flow rate of the refrigerant.
- an electric expansion valve that can adjust the flow rate of the refrigerant.
- the expansion device 35 not only an electric expansion valve but also a mechanical expansion valve employing a diaphragm for a pressure receiving portion, a capillary tube, or the like can be applied.
- the second heat exchanger 36 functions as an evaporator during heating operation and functions as a condenser during cooling operation. That is, when functioning as an evaporator, the second heat exchanger 36 exchanges heat between the low-temperature and low-pressure refrigerant that has flowed out of the expansion device 35 and the air supplied by the blower 37, and the low-temperature and low-pressure liquid refrigerant or two-phase The refrigerant evaporates. On the other hand, when functioning as a condenser, the second heat exchanger 36 exchanges heat between the high-temperature and high-pressure refrigerant discharged from the compressor 33 and the air supplied by the blower 37, and the high-temperature and high-pressure gas refrigerant condenses. .
- the flow path switching device 39 switches the refrigerant flow between the heating operation and the cooling operation. That is, the flow path switching device 39 is switched so as to connect the compressor 33 and the first heat exchanger 34 during the heating operation, and switched so as to connect the compressor and the second heat exchanger 36 during the cooling operation. It is done.
- the flow path switching device 39 may be constituted by a four-way valve, for example. However, a combination of a two-way valve or a three-way valve may be adopted as the flow path switching device 39.
- the heat exchanger 500 according to Embodiment 1 is used for the first heat exchanger 34 or the second heat exchanger 36, or both the first heat exchanger 34 and the second heat exchanger 36. it can. That is, the refrigeration cycle apparatus 100 includes the heat exchanger 500 according to Embodiment 1 as at least one of the first heat exchanger 34 and the second heat exchanger 36. However, as described in the first embodiment, it is desirable to use the heat exchanger 500 as the second heat exchanger 36.
- a high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 33.
- the refrigerant flows according to the broken line arrows.
- the high-temperature and high-pressure gas refrigerant (single phase) discharged from the compressor 33 flows into the second heat exchanger 36 functioning as a condenser via the flow path switching device 39.
- the second heat exchanger 36 heat exchange is performed between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the blower 37, and the high-temperature and high-pressure gas refrigerant is condensed to a high-pressure liquid refrigerant ( Single phase).
- the high-pressure liquid refrigerant sent out from the second heat exchanger 36 becomes a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant by the expansion device 35.
- the two-phase refrigerant flows into the first heat exchanger 34 that functions as an evaporator.
- heat exchange is performed between the refrigerant flowing in the two-phase state and the air supplied by the blower 37, and the liquid refrigerant evaporates out of the two-phase state refrigerant to reduce the pressure.
- the low-pressure gas refrigerant sent out from the first heat exchanger 34 flows into the compressor 33 via the flow path switching device 39, is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 33 again. Thereafter, this cycle is repeated.
- a high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 33.
- the refrigerant flows according to solid arrows.
- the high-temperature and high-pressure gas refrigerant (single phase) discharged from the compressor 33 flows into the first heat exchanger 34 functioning as a condenser via the flow path switching device 39.
- the first heat exchanger 34 heat exchange is performed between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the blower 37, and the high-temperature and high-pressure gas refrigerant is condensed to a high-pressure liquid refrigerant ( Single phase).
- the high-pressure liquid refrigerant sent out from the first heat exchanger 34 is converted into a two-phase refrigerant consisting of a low-pressure gas refrigerant and a liquid refrigerant by the expansion device 35.
- the two-phase refrigerant flows into the second heat exchanger 36 that functions as an evaporator.
- heat exchange is performed between the refrigerant flowing in the two-phase state and the air supplied by the blower 37, and the liquid refrigerant evaporates out of the two-phase state refrigerant to reduce the pressure.
- the low-pressure gas refrigerant sent out from the second heat exchanger 36 flows into the compressor 33 via the flow path switching device 39, is compressed to become a high-temperature high-pressure gas refrigerant, and is discharged from the compressor 33 again. Thereafter, this cycle is repeated.
- the second heat exchanger 36 functions as an evaporator. Therefore, in the second heat exchanger 36, when heat is exchanged between the air supplied from the blower 37 and the refrigerant flowing inside the heat transfer tubes constituting the second heat exchanger 36, Moisture in the air is condensed, and water droplets are generated on the surface of the second heat exchanger 36. Water droplets generated in the second heat exchanger 36 flow downward and are discharged through a drainage channel (the drainage region 1b described in the first embodiment) configured with fins and heat transfer tubes.
- a drainage channel the drainage region 1b described in the first embodiment
- the second heat exchanger 36 when the second heat exchanger 36 is accommodated in an outdoor unit (not shown) of the refrigeration cycle apparatus 100 and functions as an evaporator by heating operation of the refrigeration cycle apparatus 100, moisture in the air is converted into the second heat exchanger. 36 may frost. Therefore, in an air conditioner or the like capable of heating operation, the “defrosting operation” for removing frost is usually performed when the outside air becomes a certain temperature (for example, 0 ° C.) or less.
- Defrosting operation refers to supplying hot gas (high-temperature high-pressure gas refrigerant) from the compressor 33 to the second heat exchanger 36 in order to prevent frost from adhering to the second heat exchanger 36 functioning as an evaporator. It is driving to do.
- the defrosting operation may be executed when the duration time of the heating operation reaches a predetermined value (for example, 30 minutes).
- the defrosting operation may be performed before the heating operation when the second heat exchanger 36 is at a certain temperature (for example, minus 6 ° C.) or less. The frost and ice adhering to the second heat exchanger 36 are melted by the hot gas supplied to the second heat exchanger 36 during the defrosting operation.
- the heat exchanger 500 according to Embodiment 1 is used as the second heat exchanger 36
- the flow direction of the air flowing into the heat exchanger 500 is not particularly limited.
- the heat exchanger 500 is directed from the water introduction region 1a side to the drainage region 1b side. It is assumed that air flows. That is, in FIG. 9, it is assumed that air flows from the left side to the right side of the drawing.
- the blower 37 may be installed on either the upstream side or the downstream side of the heat exchanger 500.
- the heat exchanger 500 includes the water conveyance area 1a in which the “water conveyance structure” is formed and the drainage area 1b in which the “drainage structure” is formed. For this reason, in the 2nd heat exchanger 36, the water droplet adhering to the fin 1 moves easily from the water conveyance area
- the amount of water remaining in the entire second heat exchanger 36 is likely to be reduced.
- the refrigeration cycle apparatus 100 since the heat exchanger 500 according to Embodiment 1 is adopted as the second heat exchanger 36, the drainage of water droplets generated in the second heat exchanger 36 is improved. Greatly improved.
- coolant used for the refrigerating-cycle apparatus 100 is not specifically limited, Even if it uses refrigerant
- coolants such as R410A, R32, HFO1234yf
- coolants such as R410A, R32, HFO1234yf
- an effect can be exhibited.
- coolants such as R410A, R32, HFO1234yf
- coolants such as R410A, R32, HFO1234yf
- the refrigeration cycle apparatus 100 can be used for any refrigerating machine oil, regardless of whether the oil dissolves in the refrigerant, such as mineral oil, alkylbenzene oil, ester oil, ether oil, fluorine oil, etc.
- the effect as the heat exchanger 500 can be exhibited.
- the refrigeration cycle apparatus 100 there are a water heater, a refrigerator, an air-conditioning hot water supply complex machine, etc., which are easy to manufacture, improve heat exchange performance, and improve energy efficiency. it can.
- a refrigerant circuit is formed by the compressor 33, the first heat exchanger 34, the expansion device 35, and the second heat exchanger 36, and the first heat exchanger 34 and Since the heat exchanger 500 according to the first embodiment is applied to at least one of the second heat exchangers 36, both improvement of drainage and securing of heat transfer performance are achieved.
Abstract
Description
図1は、本発明の実施の形態1に係るフィンチューブ型熱交換器(以下、熱交換器500と称する)の構成例の一部を概略的に示す断面図である。図2は、熱交換器500の構成例の一部を三方向から見た模式図である。図3は、熱交換器500を構成するフィン1の構成例を概略的に示す側面図である。図4は、熱交換器500を構成する伝熱管2の構成例を概略的に示す断面図である。図5は、熱交換器500の全体外観構成の一例を示す斜視概要図である。図1~図5に基づいて、熱交換器500について説明する。
フィン1は、伝熱管2の上下に配した導水領域1aと、伝熱管2の側部に配した排水領域1bと、を有している。
また、排水領域1bは、重力方向となるフィン1の長手方向に複数の切欠部10が形成されていない領域である。つまり、排水領域1bは、フィン1に付着した水(導水領域1aから導かれた水を含む)を重力方向に導く領域である。
上下に隣り合う切欠部10の重力方向の距離は、段ピッチDpで一定としている。
また、フィン1は、例えばアルミニウム製又はアルミニウム合金製である。
複数の伝熱管2は、フィン1の複数の切欠部10に装着され、フィン1と交差するものである。複数の伝熱管2は、フィン1の切欠部10に装着されるため、重力方向に並設したものとなっている。また、伝熱管2は、図1に示すように、縦幅(断面短軸方向)よりも横幅(断面長軸方向)を大きくした形状に構成されている。つまり、複数の伝熱管2は、長軸の向きがフィン1の間を流れる流体の流通方向とされ、流通方向に対して直交する段方向(紙面上下方向)に間隔を空けて配置される。
上下に隣り合う伝熱管2の重力方向の距離は、段ピッチDpで一定としている。
また、伝熱管2は、例えばアルミニウム製又はアルミニウム合金製である。
なお、伝熱管2は、例えば、押出成形により断面が長円形状となるように作製した後に、追加工により最終形状を形成してもよい。
図6は、熱交換器500を構成するフィン1の具体的な構成例の一例を示す構成図である。図1、図2及び図6に基づいて、フィン1の具体的な構成例の1つについて詳細に説明する。なお、図6では、空気の流通方向を矢印Xで、フィン1の並んでいる方向を矢印Yで、重力方向を矢印Zで、それぞれ示している。また、図6では、4本の伝熱管2がフィン1に挿入されている部分を拡大して示している。
導水構造は、導水領域1aの少なくとも一部に形成されている。具体的には、フィン1を構成する部材の一部を、稜線がX軸方向と平行となる波型にすることで導水構造を形成している。以下、波型形状の導水構造を波型導水構造1a-1と称する。導水領域1aを波型導水構造1a-1とすることにより、導水領域1aに付着した水を波型導水構造1a-1の稜線に沿って流すことができ、排水領域1bに導きやすくなる。そのため、熱交換器500としての排水性が向上することになる。
排水構造は、排水領域1bの少なくとも一部に形成されている。具体的には、フィン1を構成する部材の一部を、稜線がZ軸方向と平行となる波型にすることで排水構造を形成している。以下、波型形状の排水構造を波型排水構造1b-1と称する。排水領域1bを波型排水構造1b-1とすることにより、排水領域1bに付着した水(導水領域1aから導かれた水を含む)を波型排水構造1b-1の稜線に沿って流すことができ、熱交換器500の下方に排出しやすくなる。そのため、熱交換器500としての排水性が向上することになる。
図7は、熱交換器500を構成するフィン1の具体的な構成例の他の一例を示す構成図である。図7に基づいて、フィン1の具体的な構成例の1つについて詳細に説明する。なお、図7では、空気の流通方向を矢印Xで、フィン1の並んでいる方向を矢印Yで、重力方向を矢印Zで、それぞれ示している。また、図7では、4本の伝熱管2がフィン1に挿入されている部分を拡大して示している。
図7に示すように、フィン1を構成する部材の一部をディンプル状とすることで導水構造を形成してもよい。以下、ディンプル状の導水構造をディンプル導水構造1a-2と称する。導水領域1aをディンプル導水構造1a-2とすることにより、導水領域1aに付着した水をディンプルの表面張力を利用して排水領域1bに導きやすくなる。そのため、熱交換器500としての排水性が向上することになる。
図7に示すように、フィン1を構成する部材の一部をディンプル状とすることで排水構造を形成してもよい。以下、ディンプル状の排水構造をディンプル排水構造1b-2と称する。ディンプル排水構造1b-2とすることにより、排水領域1bに付着した水(導水領域1aから導かれた水を含む)をディンプルの表面張力を利用して重力方向に沿って流すことができ、熱交換器500の下方に排出しやすくなる。そのため、熱交換器500としての排水性が向上することになる。
図8は、熱交換器500を構成するフィン1の具体的な構成例の更に他の一例を示す構成図である。図8に基づいて、フィン1の具体的な構成例の1つについて詳細に説明する。なお、図8では、空気の流通方向を矢印Xで、フィン1の並んでいる方向を矢印Yで、重力方向を矢印Zで、それぞれ示している。また、図8では、4本の伝熱管2がフィン1に挿入されている部分を拡大して示している。
図8に示すように、フィン1を構成する部材の一部にスリットを形成して排水構造を構成してもよい。以下、スリットを形成した排水構造をスリット排水構造1b-3と称する。スリット排水構造1b-3とすることにより、排水領域1bに付着した水(導水領域1aから導かれた水を含む)を形状の相違を利用して重力方向に沿って流すことができ、熱交換器500の下方に排出しやすくなる。そのため、熱交換器500としての排水性が向上することになる。
導水構造と排水構造の具体的な組み合わせ例として、波型導水構造1a-1と波型排水構造1b-1、ディンプル導水構造1a-2とディンプル排水構造1b-2、スリット導水構造1a-3とスリット排水構造1b-3を挙げて説明したが、これらは適宜組み合わせを変更することが可能なものとする。たとえば、波型導水構造1a-1とディンプル排水構造1b-2を組み合わせたり、ディンプル導水構造1a-2と波型排水構造1b-1を組み合わせたりすることができる。また、これらの組み合わせについても、スリット導水構造1a-3とスリット排水構造1b-3を含めるようにしてもよい。
図9は、熱交換器500を構成するフィン1の具体的な構成例の更に他の一例を示す構成図である。図10は、熱交換器500の伝熱管2の傾斜角度θと伝熱性能及び排水性能との関係を示す図である。図9及び図10に基づいて、フィン1の具体的な構成例の1つについて詳細に説明する。なお、図9では、空気の流通方向を矢印Xで、フィン1の並んでいる方向を矢印Yで、重力方向を矢印Zで、それぞれ示している。また、図9では、4本の伝熱管2がフィン1に挿入されている部分を拡大して示している。さらに図10では、縦軸が伝熱性能及び排水性能を、横軸が傾斜角度θを、それぞれ示している。
さらに、ここでは、傾斜波型導水構造1a-4を例に説明したが、ディンプル導水構造1a-2、スリット導水構造1a-3であっても同様の考え方で、傾斜させてもよい。
熱交換器500は、たとえば図3に示すフィン1と図4に示す伝熱管2の組み合わせを、流体の流通方向に対して並行な方向に間隔を空けて2列並べることで構成される。図3に示すフィン1と図4に示す伝熱管2の組み合わせを、図5に示すように風上側熱交換器500A、風下側熱交換器500Bとして2列並べて熱交換器500を構成するとよい。つまり、風上側熱交換器500A及び風下側熱交換器500Bは、図3に示すフィン1と図4に示す伝熱管2の組み合わせで同様に構成されている。
図11は、熱交換器500で発生した水の流れを説明するための模式図である。図11に基づいて、熱交換器500の作用について説明する。なお、図11には、熱交換器500で発生した水を水滴Wとして図示している。また、図11では、導水構造として波型導水構造1a-1を、排水構造として波型排水構造1b-1を、それぞれ採用した熱交換器500を例に示している。
送風手段は、例えば、プロペラファン、モータ、および、制御機器等から構成され、熱交換器500の上流側又は下流側に、プロペラファンの回転軸が略水平となるように配置されている。なお、空気の流れ方向は、導水領域1a側から熱交換器500に流入してもよいし、排水領域1b側から熱交換器500に流入してもよい。
上面2aは、空気の流れ方向と平行であるため、伝熱管2の幅方向のほぼ全域において、空気は上面2aに沿って流れことができ、大きな剥離を発生させることなく空気と伝熱管2の表面との間の熱交換を促進することができる。また、通風抵抗を軽減することができる。
下面2cも、空気の流れ方向と平行であるため、伝熱管2の幅方向のほぼ全域において、空気は下面2cに沿って流れことができ、大きな剥離を発生させることなく空気と伝熱管2の表面との間の熱交換を促進することができる。また、通風抵抗を軽減することができる。
たとえば、熱交換器500を蒸発器として用いた場合、熱交換器500では凝縮水が発生する。この凝縮主が水滴Wとなり、フィン1の導水領域1aに付着する。導水領域1aに付着した水滴Wは、導水領域1aに沿って下方に流れる。導水領域1aを下方に流れた水滴Wは、その導水領域1aの下方に位置する伝熱管2の上面2aに到達する。
図12は、本発明の実施の形態2に係る冷凍サイクル装置100の冷媒回路構成の一例を概略的に示す回路構成図である。図12に基づいて、冷凍サイクル装置100について説明する。なお、本実施の形態2では実施の形態1との相違点を中心に説明し、実施の形態1と同一部分には、同一符号を付して説明を省略するものとする。また、図12では、冷凍サイクル装置100の一例として空気調和装置を例に説明するものとする。さらに、図12では、冷房運転時の冷媒の流れを破線矢印で示し、暖房運転時の冷媒の流れを実線矢印で示している。
次に、冷凍サイクル装置100の動作について、冷媒の流れとともに説明する。ここでは、熱交換流体が空気であり、被熱交換流体が冷媒である場合を例に、冷凍サイクル装置100の動作について説明する。
また、作動流体としては空気および冷媒の例を示したが、これに限定するものではなく、他の気体、液体、気液混合流体を用いても、同様の効果を発揮する。つまり、冷凍サイクル装置100の用途に応じて、作動流体は変化するものであり、どの場合であっても効果を奏することになる。
さらに、熱交換器500を第1熱交換器34として用いた場合においても同様な効果を奏することができる。
さらに、冷凍サイクル装置100のその他の例としては、給湯器や冷凍機、空調給湯複合機などがあり、いずれの場合も製造が容易で、熱交換性能を向上し、エネルギ効率を向上させることができる。
Claims (12)
- 重力方向に延設されたフィンと、前記フィンに交差するように装着された複数の伝熱管と、を備え、前記複数の伝熱管を重力方向に並設した熱交換器であって、
前記フィンは、
前記複数の伝熱管のそれぞれの上下に配した導水領域と、
前記複数の伝熱管のそれぞれの一方の側部に配した排水領域と、を有し、
前記導水領域は、前記排水領域に水を導く導水構造を有し、
前記排水領域は、重力方向に水を導く排水構造を有する
熱交換器。 - 前記導水構造は、
前記フィンの一部を波型に形成して構成された
請求項1に記載の熱交換器。 - 前記導水構造は、
前記フィンの一部をディンプル状に形成して構成された
請求項1に記載の熱交換器。 - 前記導水構造は、
前記フィンの一部を切り起こして形成したスリットを有している
請求項2又は3に記載の熱交換器。 - 前記排水構造は、
前記フィンの一部を波型に形成して構成された
請求項1~4のいずれか一項に記載の熱交換器。 - 前記排水構造は、
前記フィンの一部をディンプル状に形成して構成された
請求項1~4のいずれか一項に記載の熱交換器。 - 前記排水構造は、
前記フィンの一部を切り起こして形成したスリットを有している
請求項5又は6に記載の熱交換器。 - 前記複数の伝熱管は、
断面短軸方向よりも断面長軸方向を大きくした形状である
請求項1~7のいずれか一項に記載の熱交換器。 - 前記複数の伝熱管のそれぞれの断面長軸方向が、
前記排水領域に向かって下向きに傾斜している
請求項8に記載の熱交換器。 - 傾斜させた前記複数の伝熱管のそれぞれの傾斜角度を20度以下とした
請求項9に記載の熱交換器。 - 圧縮機、第1熱交換器、絞り装置、第2熱交換器を冷媒配管によって接続した冷媒回路を有し、
請求項1~10のいずれか一項に記載の熱交換器を、前記第1熱交換器及び前記第2熱交換器の少なくとも1つとして用いている
冷凍サイクル装置。 - 請求項1~10のいずれか一項に記載の熱交換器を前記第2熱交換器として用いているものにおいて、
前記第2熱交換器に空気を供給する送風機を設け、
前記送風機によって供給される空気を前記第2熱交換器の前記導水領域側から流入させる
請求項11に記載の冷凍サイクル装置。
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