US20130240187A1 - Heat exchanger and air conditioner equipped with same - Google Patents
Heat exchanger and air conditioner equipped with same Download PDFInfo
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- US20130240187A1 US20130240187A1 US13/990,100 US201113990100A US2013240187A1 US 20130240187 A1 US20130240187 A1 US 20130240187A1 US 201113990100 A US201113990100 A US 201113990100A US 2013240187 A1 US2013240187 A1 US 2013240187A1
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- heat exchanger
- notches
- condensate water
- fins
- exchanger according
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- 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
- F28D1/05358—Assemblies of conduits connected side by side or with individual headers, e.g. section type radiators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/14—Heat exchangers specially adapted for separate outdoor units
- F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
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- 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
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0471—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a non-circular cross-section
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- 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
- F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
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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
- F28F1/126—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 consisting of zig-zag shaped fins
-
- 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
- F28F1/30—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 being attachable to the element
-
- 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
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
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- 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
- F28D2021/007—Condensers
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- 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
- F28D2021/0071—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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
Definitions
- the present invention relates to a side-flow type parallel-flow heat exchanger and an air conditioner equipped with the same.
- a parallel-flow heat exchanger has a configuration in which a plurality of flat tubes are arranged between a plurality of header pipes such that a plurality of refrigerant passages in the flat tubes communicate with interiors of the header pipes, and fins such as corrugated fins are disposed between the flat tubes.
- Such a parallel-flow heat exchanger is widely used in vehicle air conditioners, outdoor units of air conditioners for buildings, and so on.
- the corrugated fins may be installed exclusively between the flat tubes or may be mounted therebetween and also to an outward facing surface of each outermost positioned one of the plurality of flat tubes. Examples of the latter case can be seen in Patent Documents 1 to 3.
- a heat exchanger described in Patent Document 1 is a parallel-flow heat exchanger in which flat tubes are arranged in horizontal rows.
- corrugated fins are mounted also to an outward facing flat surface of each outermost one of the flat tubes, and a side plate for fin protection is disposed on an outside of each outermost one of the corrugated fins.
- a heat exchanger described in Patent Document 2 also is a parallel-flow heat exchanger in which flat tubes are arranged in horizontal rows.
- corrugated fins are mounted also to an outward facing flat surface of each outermost one of the flat tubes, and a side plate for reinforcing a core portion composed of the flat tubes and the corrugated fins, which are alternately layered on each other, is disposed on an outside of each outermost one of the corrugated fins.
- a heat exchanger described in Patent Document 3 also is a parallel-flow heat exchanger in which flat tubes are arranged in horizontal rows.
- a side sheet is brazed to an exterior of one of the corrugated fins at each of both ends of the heat exchanger.
- a heat exchanger In a case where a heat exchanger is used as an evaporator, moisture in the atmosphere condenses on a cooled surface of the heat exchanger, and thus condensate water is formed.
- a side-flow type parallel-flow heat exchanger if condensate water is accumulated on surfaces of flat tubes or of corrugated fins, an area of an air flow passage is narrowed by the water, so that heat exchange performance is deteriorated. For this reason, it is required that a side-flow type parallel-flow heat exchanger be configured to allow condensate water to be quickly drained, thereby preventing it from being accumulated therein.
- condensate water When an air temperature is low, condensate water turns into frost on a surface of a heat exchanger. Such frost may even turn into ice.
- the term “condensate water” is intended to encompass so-called defrosted water that is water resulting from melting of such frost or ice.
- a parallel-flow heat exchanger including a side sheet provided on an outside of each outermost fin is used by adopting a so-called side-flow method in which header pipes are arranged in perpendicular rows, and flat tubes are arranged in horizontal rows, there occurs a problem that condensate water is held by a lower-side one of the side sheets.
- Patent Documents 4 and 5 disclose technical ideas for solving this problem.
- an outermost corrugated fin positioned at a lower portion is at least partly exposed to have an exposed portion.
- the exposed portion is made to emerge by reducing a width of a side plate positioned on an outside of this outermost corrugated fin.
- water drainage holes for draining condensate water are provided through a side plate as a bottom surface plate.
- the water drainage holes are provided in such a number and size as not to deteriorate mechanical strength of the side plate.
- a side-flow type parallel-flow heat exchanger includes: a plurality of header pipes that are arranged parallel to each other at an interval therebetween; a plurality of flat tubes that are arranged between the plurality of header pipes and each have therein a refrigerant passage communicating with interiors of the plurality of header pipes; a plurality of fins that are mounted to flat surfaces of the plurality of flat tubes; and a side sheet that is attached to an outside of each outermost positioned one of the plurality of fins.
- One of the side sheets which is positioned at a lower portion of said heat exchanger, is provided, at an edge thereof on a condensate water gathering side in said heat exchanger, with a plurality of notches formed at intervals from each other, and each of the notches has a width extending over a length plural times a length of an interval pitch of the fins.
- the notches have a shape having an angle of less than 180° inside from the edge of the one of the side sheets.
- the notches are tapered from the edge of the one of the side sheets.
- the one of the side sheets is provided, at an edge thereof on a side opposite to the condensate water gathering side, with a plurality of notches formed at intervals from each other, and each of the notches has a width extending over a length plural times a length of the interval pitch of the fins.
- the notches formed in the one of the side sheets on the condensate water gathering side or the notches formed in the one of the side sheets on the side opposite to the condensate water gathering side have a depth exceeding half a depth of the one of the side sheets.
- the notches formed on the condensate water gathering side and the notches formed on the side opposite to the condensate water gathering side are arranged so as to be mutually staggered.
- a part of said heat exchanger can be formed into a curved portion by bending, and a part of the one of the side sheets, which is to be subjected to the bending, is provided, at an edge thereof that is to be convex after the bending, with a plurality of slits formed by cutting at intervals from each other.
- the one of the side sheets is provided, at an edge thereof that is to be concave after bending, with a plurality of the notches that have a width extending over a length plural times a length of the interval pitch of the fins and are formed at intervals from each other.
- the one of the side sheets has a plurality of through holes formed at intervals from each other at portions thereof other than portions where the notches are formed.
- each of the through holes is formed to have a width extending over a length plural times a length of the interval pitch of the fins.
- the one of the side sheets has a width smaller than a width of the fins, and the fins are exposed to an outside of the one of the side sheets on each of the condensate water gathering side and a side opposite to the condensate water gathering side.
- An air conditioner according to the present invention includes the heat exchanger of any one of the above-described configurations, and the heat exchanger is incorporated in an outdoor unit or an indoor unit of the air conditioner.
- condensate water is formed on an outermost fin positioned at a lower portion of a heat exchanger, or condensate water formed at an upper part of the heat exchanger flows down to the lower portion of the heat exchanger, such condensate water quickly drips down, i.e. is quickly drained.
- FIG. 1 is a front view of a heat exchanger according to an embodiment of the present invention.
- FIG. 2 is a perspective view of the heat exchanger shown in FIG. 1 .
- FIG. 3 is a bottom view of the heat exchanger shown in FIG. 1 .
- FIG. 4 is a partially enlarged view based on FIG. 1 .
- FIG. 5 is a partial perspective view of the heat exchanger shown in FIG. 1 .
- FIG. 6 is an explanatory view explaining a relationship between an interval pitch of fins and a width of a notch.
- FIG. 7 is an explanatory view explaining a relationship between the interval pitch of the fins and a width of a through hole.
- FIG. 8 is a first diagram explaining a shape of the notch.
- FIG. 9 is a second diagram explaining a shape of the notch.
- FIG. 10 is a third diagram explaining a shape of the notch.
- FIG. 11 is a fourth diagram explaining a shape of the notch.
- FIG. 12 is a fifth diagram explaining a shape of the notch.
- FIG. 13 is a sixth diagram explaining a shape of the notch.
- FIG. 14 is a first diagram explaining a shape of the through hole.
- FIG. 15 is a second diagram explaining a shape of the through hole.
- FIG. 16 is a third diagram explaining a shape of the through hole.
- FIG. 17 is a view explaining a method for forming the notches at a curved portion of the heat exchanger.
- FIG. 18 is a view explaining a modified form of a side sheet.
- FIG. 19 is a schematic sectional view of an outdoor unit of an air conditioner equipped with the heat exchanger according to the present invention.
- FIG. 20 is a schematic configuration view of the air conditioner equipped with the heat exchanger according to the present invention, showing a state at the time of an air-warming operation.
- FIG. 21 is a schematic configuration view of the air conditioner equipped with the heat exchanger according to the present invention, showing a state at the time of an air-cooling operation.
- FIG. 22 is a perpendicular sectional view explaining a basic structure of a side-flow type parallel-flow heat exchanger.
- FIG. 23 is a perpendicular sectional view taken along a line A-A of FIG. 22 .
- FIGS. 22 and 23 show a basic structure of a side-flow type parallel-flow heat exchanger.
- an upper side of the figure is an upper side of the heat exchanger
- a lower side of the figure is a lower side of the heat exchanger.
- two perpendicular header pipes 2 and 3 are arranged parallel to each other at an interval therebetween in a horizontal direction
- a plurality of horizontal flat tubes 4 are arranged at a predetermined pitch in a perpendicular direction.
- Each of the flat tubes 4 is an elongated metal member formed by extrusion and has therein a refrigerant passage 5 for a refrigerant to flow therethrough.
- the flat tubes 4 are arranged with an extrusion direction thereof, which is also a longitudinal direction thereof, set to be horizontal, and thus a direction in which a refrigerant flows through the refrigerant passage 5 also is horizontal.
- a plurality of the refrigerant passages 5 equal in sectional shape and sectional area are arranged in a depth direction in FIG. 22 , so that a perpendicular section of each of the flat tubes 4 has a harmonica-like shape as shown in FIG. 23 .
- Each of the refrigerant passages 5 communicates with interiors of the header pipes 2 and 3 .
- Fins 6 are mounted to flat surfaces of the flat tubes 4 , respectively. While, as the fins 6 , corrugated fins are used herein, plate fins also may be used. Needless to say, at a stage of actually being incorporated in equipment, the parallel-flow heat exchanger 1 is installed at various angles as required from a design standpoint, and there are many cases where strict meanings of “perpendicular” and “horizontal
- the header pipes 2 and 3 , the flat tubes 4 , and the fins 6 are all made of a metal having good thermal conductivity, such as aluminum.
- the flat tubes 4 are fixed to the header pipes 2 and 3 by brazing or welding, and the fins 6 are fixed to the flat tubes 4 by brazing or welding.
- the fins 6 are disposed between the flat tubes 4 such that each of the fins 6 is fixed at both of its upper and lower ends to the flat surfaces of each pair of adjacent upper and lower ones of the flat tubes 4 , respectively.
- a fin disposed on an outward facing flat surface of each outermost (uppermost or lowermost) positioned one of the plurality of flat tubes 4 arranged in vertical rows is fixed only at one of its upper and lower ends to the flat surface of the each tube.
- an outermost fin is referred to as an outermost fin.
- An outermost fin positioned at an upper portion of the heat exchanger 1 is indicated by a reference symbol 6 a U
- an outermost fin positioned at a lower portion of the heat exchanger 1 is indicated by a reference symbol 6 a D.
- a side sheet 10 U is disposed on an outside of the outermost fin 6 a U, and a side sheet 10 D is disposed on an outside of the outermost fin 6 a D.
- the side sheets 10 U and 10 D are made of a metal sheet such as of aluminum and fixed to the outermost fins 6 a U and 6 a D, respectively, by brazing or welding.
- the heat exchanger 1 is of a side-flow type, and only the header pipe 3 is provided with refrigerant gates 7 and 8 .
- the header pipe 3 two partition plates 9 a and 9 c are provided at an interval therebetween in a vertical direction, and in the header pipe 2 , a partition plate 9 b is provided at a height intermediate between heights at which the partition plates 9 a and 9 c are provided, respectively.
- a refrigerant flows in through the lower-side refrigerant gate 7 as shown by a solid line arrow in FIG. 22 .
- the refrigerant that has entered through the refrigerant gate 7 is blocked by the partition plate 9 a to be directed to the header pipe 2 via some of the flat tubes 4 .
- This flow of the refrigerant is represented by a left-pointing block arrow.
- the refrigerant that has entered the header pipe 2 is blocked by the partition plate 9 b to be directed to the header pipe 3 via other ones of the flat tubes 4 .
- This flow of the refrigerant is represented by a right-pointing block arrow.
- the refrigerant that has entered the header pipe 3 is blocked by the partition plate 9 c to be directed again to the header pipe 2 via still other ones of the flat tubes 4 .
- This flow of the refrigerant is represented by another left-pointing block arrow.
- the refrigerant that has entered the header pipe 2 turns around to be directed again to the header pipe 3 via still other ones of the flat tubes 4 .
- This flow of the refrigerant is represented by another right-pointing block arrow.
- the refrigerant that has entered the header pipe 3 flows out through the refrigerant gate 8 . In this manner, the refrigerant flows from bottom to top of the heat exchanger 1 , forming a zigzag path.
- the herein described case of using three partition plates is merely one example, and the number of partition plates used and a resulting number of times the flow of a refrigerant turns around can be set arbitrarily as required.
- a flow direction of a refrigerant is reversed. That is, a refrigerant enters the header pipe 3 through the refrigerant gate 8 as shown by a dotted line arrow in FIG. 22 and then is blocked by the partition plate 9 c to be directed to the header pipe 2 via some of the flat tubes 4 .
- the refrigerant is blocked by the partition plate 9 b to be directed to the header pipe 3 via other ones of the flat tubes 4 .
- the refrigerant is blocked by the partition plate 9 a to be directed again to the header pipe 2 via still other ones of the flat tubes 4 .
- the refrigerant turns around to be directed again to the header pipe 3 via still other ones of the flat tubes 4 . Then, the refrigerant flows out through the refrigerant gate 7 as shown by another dotted line arrow. In this manner, the refrigerant flows from top to bottom of the heat exchanger 1 , forming a zigzag path.
- the heat exchanger 1 is not limited in configuration to the above-described one. A configuration is also possible in which both of the header pipes 2 and 3 are provided with a refrigerant gate. Another configuration is also possible in which no partition plates are provided in the header pipes 2 and 3 .
- FIGS. 1 to 5 show a structure of the heat exchanger 1 as an embodiment of the present invention.
- constituent components common with those in the basic structure shown in FIGS. 22 and 23 are indicated by the same reference symbols as used in FIGS. 22 and 23 , and descriptions thereof are omitted.
- condensate water In a case where the heat exchanger 1 is used as an evaporator, moisture in the atmosphere condenses on a cooled surface of the heat exchanger 1 , and thus condensate water is fowled.
- the intended meaning of “condensate water” is as described earlier.
- a parallel-flow heat exchanger such as the heat exchanger 1 , if condensate water is accumulated on surfaces of flat tubes or of fins, a sectional area of an air flow passage is narrowed by the water, so that heat exchange performance is deteriorated.
- Accumulated condensate water narrows an area of an air flow passage of the heat exchanger 1 and thus hinders ventilation, so that heat exchange performance is deteriorated. Furthermore, in a case where the heat exchanger 1 is incorporated in an outdoor unit of an air conditioner, with a drop of an outside air temperature to a freezing point or lower, condensate water may freeze to cause damage to the heat exchanger 1 . For this reason, it is required that condensate water formed in the heat exchanger 1 be drained as quickly as possible.
- a side sheet 10 D positioned at the lower portion of the heat exchanger 1 is configured as follows. That is, the side sheet 10 D is provided, at an edge thereof on a condensate water gathering side in the heat exchanger 1 , with a plurality of notches 11 formed at intervals from each other.
- the heat exchanger 1 In the case where the heat exchanger 1 is incorporated in an outdoor unit of an air conditioner, condensate water gathers on a windward side of the heat exchanger 1 . This is for the following reason. That is, in an outdoor unit, the heat exchanger 1 is installed in a state of standing substantially upright without being tilted. In a case where the heat exchanger 1 is used as an evaporator (as in, for example, an air-warming operation), heat exchange is performed more actively on a windward side than on a leeward side, and thus condensate water is accumulated on the windward side. Hence, the windward side is a condensate water gathering side.
- the heat exchanger 1 is designed to be incorporated in an outdoor unit of an air conditioner and, as shown in FIGS. 2 , 3 , and 5 , has one curved portion la at some point along its length, thus having a substantially L-shaped planar shape.
- a convex side of the curved portion la is a windward side in the outdoor unit. Accordingly, in each of FIGS. 3 and 4 , a lower side of the figure is a condensate water gathering side, and the side sheet 10 D has the notches 11 formed at the edge thereof on this side.
- the individual notches 11 have a shape having an angle of less than 180° inside the side sheet 10 D from the edge of the side sheet 10 D and are tapered from the edge of the side sheet 10 D.
- a V shape is selectively adopted as a shape satisfying these conditions.
- each of the notches 11 has, at its widest portion, a width W 1 extending over a length plural times a length of an interval pitch P of the fins 6 .
- the notches 11 are tapered from the edge of the side sheet 10 D, as shown by arrows in FIG. 8 , condensate water, upon contact with an edge of each of the notches 11 , is guided deep into the each of the notches 11 , and at a deepest point thereof, flows of the water join together to form a water droplet. Such a water droplet grows fast and drips down, i.e. is drained. Since the notches 11 have a width extending over a length plural times a length of the interval pitch P of the fins 6 , it takes only a short time for condensate water to gather to form a large water droplet, thus enabling efficient drainage of condensate water.
- the notches 11 in the present invention are not limited in shape to a V shape. Any of various shapes exemplarily shown in FIGS. 9 to 12 or any other shape can be adopted.
- Notches 11 shown in FIG. 9 have a semicircular shape or a U shape. While not having an angle at their depths, the notches 11 of this type satisfy the condition that they are tapered from the edge of the side sheet 10 D.
- Notches 11 shown in FIG. 10 have a trapezoidal shape.
- the notches 11 of this type satisfy the condition that they have an angle of less than 180° inside the side sheet 10 D from the edge thereof by having two angles of less than 180° and more than 90°, namely, two obtuse angles 11 a . Furthermore, the notches 11 of this type also satisfy the condition that they are tapered from the edge of the side sheet 10 D.
- Notches 11 shown in FIG. 11 have an inverted M shape.
- the notches 11 of this type satisfy the condition that they have an angle of less than 180° inside the side sheet 10 D from the edge thereof by having two angles of less than 90°, namely, two acute angles 11 b . Furthermore, the notches 11 of this type also satisfy the condition that they are tapered from the edge of the side sheet 10 D.
- Notches 11 shown in FIG. 12 have an inverted trapezoidal shape, each having a width that is reduced at its entry provided at the edge of the side sheet 10 D and increases with increasing depth from the entry.
- the notches 11 of this type satisfy the condition that they have an angle of less than 180° inside the side sheet 10 D from the edge thereof by having two angles of less than 90°, namely, two acute angles 11 b.
- the side sheet 10 D is provided, also at an edge thereof on a side opposite to the condensate water gathering side in the heat exchanger 1 , with a plurality of notches 12 formed at intervals from each other. That is, the side sheet 10 D has notches formed at the edges of both sides thereof.
- an upper side of the figure is the side opposite to the condensate water gathering side.
- the side opposite to the condensate water gathering side is a leeward side of the heat exchanger 1 .
- the notches 12 have a width extending over a length plural times a length of the interval pitch P of the fins 6 and are tapered from the edge of the side sheet 10 D.
- the notches 11 and the notches 12 are the same in shape (V shape) and size, which, however, is not necessarily required.
- the notches 12 may have a shape (any of the shapes exemplarily shown in FIGS. 9 to 12 or any other shape) different from that of the notches 11 , and there may be a difference in width between the notches 11 and the notches 12 .
- the side sheet 10 D is provided, also at the edge thereof on the side (leeward side) opposite to the condensate water gathering side (windward side) in the heat exchanger 1 , with the notches 12 and, therefore, has notches fainted at the edges of both sides thereof. This further enhances a condensate water drainage capability of the side sheet 10 D, and thus condensate water at the outermost fin 6 a D can be quickly drained.
- this embodiment adopts a configuration in which the side sheet 10 D is provided with notches at the edge thereof on the condensate water gathering side and at the edge thereof on the side opposite thereto in the heat exchanger 1 , in other words, a configuration in which the side sheet 10 D has notches formed at the edges of both sides thereof, a configuration also may be adopted in which the side sheet 10 D has notches formed only at the edge thereof on the condensate water gathering side.
- the notches 11 and 12 may have a size increased to such an extent as to have respective depths exceeding half a depth of the side sheet 10 D.
- the side sheet 10 D has a shape shown in FIG. 13 and thus allows condensate water to be quickly drained from the outermost fin 6 a D.
- notches 11 and 12 are arranged such that each of the notches 11 is staggered with respect to each of the notches 12 , there is no limitation thereto.
- a configuration also may be adopted in which the notches 11 and 12 are arranged such that every two of the notches 11 are staggered with respect to each of the notches 12 .
- the side sheet 10 D has through holes 13 formed at portions thereof other than portions where the notches 11 and 12 are formed.
- a plurality of the through holes 13 are formed at intervals from each other.
- the through holes 13 have a shape of an elongated circle (racetrack circle) whose longitudinal axis is aligned with a length direction of the flat tubes 4 and, as shown in FIG. 7 , have a width W 2 extending over a length plural times a length of the interval pitch P of the fins 6 .
- the through holes 13 are not limited in shape to an elongated circular shape. Various shapes such as an elliptical shape shown in FIG. 14 can be selectively adopted.
- the shape of the through holes 13 is not only a non-angular shape such as an elongated circular shape or an elliptical shape.
- a shape having an angle of less than 180° also is preferred as the shape of the through holes 13 .
- each of the through holes 13 has a right angle at each of four corners thereof.
- each of the through holes 13 has, on one diagonal axis thereof, two angles of less than 180° and more than 90°, namely, two obtuse angles, and on the other diagonal axis thereof orthogonal to the one diagonal axis, two angles of less than 90°, namely, two acute angles.
- the though holes 13 have a width extending over a length plural times a length of the interval pitch P of the fins 6 . Setting the through holes 13 to have a width extending over a length plural times a length of the interval pitch P of the fins 6 , however, allows a large amount of condensate water to collect and thus can expedite drainage of the water.
- a side sheet 10 D shown in FIG. 18 has through holes 13 but is not provided with notches 11 and 12 . Even the side sheet 10 D having such a configuration has a function of accelerating drainage of condensate water from the outermost fin 6 a D.
- a comparison between a width of the outermost fin 6 a D in a depth direction thereof, namely, an air-passing direction and a width of the side sheet 10 D in the same direction indicates that the width of the side sheet 10 D is made smaller than the width of the outermost fin 6 a D. Consequently, as shown in FIGS. 2 to 5 , the outermost fin 6 a D is exposed to an outside of the side sheet 10 D on each of the condensate water gathering side and the side opposite thereto. A portion thus exposed is present, and such an exposed portion acts as a drainage port, so that condensate water is quickly drained from the outermost fin 6 a D. It is not required that the side sheet 10 U be smaller in width than the outermost fin 6 a U. For example, the side sheet 10 U may be the same in width as the outermost fin 6 a U.
- the heat exchanger 1 has one curved portion 1 a at some point along its length, thus having a substantially L-shaped planar shape.
- the curved portion 1 a is formed by bending the heat exchanger 1 , and this process of bending can be utilized also to form the notches 11 .
- a part of the side sheet 10 D that is to be subjected to bending is provided, at an edge thereof that is to be convex after the bending, with a plurality of slits 14 formed by cutting at intervals from each other.
- the slits 14 are opened into a V shape as shown in an upper drawing in FIG. 17 and thus constitute the notches 11 having a width extending over a length plural times a length of the interval pitch P of the fins 6 . This can facilitate the formation of the notches 11 .
- the side sheet 10 D is provided with the notches 12 at an edge thereof on a side that is to be concave after bending.
- the notches 12 In consideration of the fact that bending causes the notches 12 to be reduced in open angle, in order that, even in such a state, the notches 12 will have an open angle equal to that thereof at a non-bent portion of the side sheet 10 D, i.e. the notches 12 will have a width extending over a length plural times a length of the interval pitch P of the fins 6 , the notches 12 are set to have a V shape having a wide pre-bending angle.
- the above-described heat exchanger 1 can be incorporated in an outdoor unit or an indoor unit of a separate type air conditioner.
- FIG. 19 shows an example in which the heat exchanger 1 is incorporated in the outdoor unit.
- An outdoor unit 20 shown in FIG. 19 includes a sheet-metal housing 20 a having a substantially rectangular planar shape, longer sides of which constitute a front face 20 F and a back face 20 B, and shorter sides of which constitute a left side face 20 L and a right side face 20 R.
- An exhaust port 21 is formed in the front face 20 F
- a back-face air intake port 22 is formed in the back face 20 B
- a side-face air intake port 23 is formed in the left side face 20 L.
- the exhaust port 21 is an assembly of a plurality of horizontal slit-shaped openings
- the back-face air intake port 22 and the side-face air intake port 23 are lattice-shaped openings.
- a heat exchanger 1 having an L-shaped thermal plane is disposed on an immediately inner side relative to the back-face air intake port 22 and the side-face air intake port 23 .
- a blower 24 is disposed between the heat exchanger 1 and the exhaust port 21 in order to forcibly cause heat exchange between the heat exchanger 1 and outdoor air.
- the blower 24 is formed by combining an electric motor 24 a with a propeller fan 24 b .
- a bell mouth 25 is fitted so as to surround the propeller fan 24 b for improved blowing efficiency.
- the housing 20 a includes a space on an inner side relative to the right side face 20 R, which is isolated by a partition wall 26 from an air flow flowing from the back-face air intake port 22 to the exhaust port 21 , and a compressor 27 is accommodated in this space.
- Condensate water formed in the heat exchanger 1 of the outdoor unit 20 narrows an area of an air flow passage, so that heat exchange performance is deteriorated. Moreover, in a cold climate environment where an outside air temperature stays below the freezing point, such condensate water may even freeze to cause damage to the heat exchanger 1 . Thus, in the outdoor unit 20 , drainage of condensate water from the heat exchanger 1 is a crucial problem.
- condensate water gathers on a windward side of the heat exchanger 1 .
- Condensate water formed on the windward side rarely flows over to a leeward side but directly reaches a lower portion of the heat exchanger 1 on the windward side.
- condensate water freezes to the heat exchanger 1 in the form of frost.
- An increased amount of frost necessitates a defrosting operation.
- the blower 24 is stopped from operating, and thus water resulting from melting of the frost flows mainly downward to be accumulated due to gravity without being affected by wind.
- the side sheet 10 D at a lower portion of the heat exchanger 1 is formed to have the configuration of the present invention, so that condensate water is quickly drained, and this can reduce detrimental effects caused by accumulation of condensate water.
- the side sheet 10 D attached to an outside of the outermost fin 6 a D is provided, at the edge thereof on a condensate water gathering side, with the plurality of notches 11 formed at intervals from each other.
- Each of the notches 11 has a width extending over a length plural times a length of the interval pitch of the fins.
- FIGS. 20 and 21 show an example in which the heat exchanger 1 is incorporated in an indoor unit of a separate type air conditioner.
- an outdoor unit includes a compressor, a four-way valve, an expansion valve, an outdoor-side heat exchanger, an outdoor-side blower, and so on
- the indoor unit includes an indoor-side heat exchanger, an indoor-side blower, and so on.
- the outdoor-side heat exchanger functions as an evaporator, and in an air-cooling operation, as a condenser.
- the indoor-side heat exchanger functions as a condenser, and in an air-cooling operation, as an evaporator.
- FIG. 20 shows a basic configuration of the separate type air conditioner using a heat pump cycle as a refrigeration cycle.
- a heat pump cycle 101 is formed by connecting, in a loop, a compressor 102 , a four-way valve 103 , an outdoor-side heat exchanger 104 , a decompression expansion device 105 , and an indoor-side heat exchanger 106 .
- the compressor 102 , the four-way valve 103 , the heat exchanger 104 , and the decompression expansion device 105 are housed in a housing of an outdoor unit 110
- the heat exchanger 106 is housed in a housing of an indoor unit 120 .
- the heat exchanger 104 is combined with an outdoor-side blower 107
- the heat exchanger 106 is combined with an indoor-side blower 108
- the blower 107 includes a propeller fan 107 a for forming a blow-off airflow
- the blower 108 includes a cross-flow fan 108 a for forming a blow-off airflow.
- the cross-flow fan 108 a is disposed below the heat exchanger 106 , with its axis line set to be horizontal.
- the heat exchanger 1 according to the present invention can be used as a constituent component of the heat exchanger 106 of the indoor unit.
- the heat exchanger 106 is composed of three heat exchangers 106 A, 106 B, and 106 C arranged in the shape of a roof covering the blower 108 , and any one or all of the heat exchangers 106 A, 106 B, and 106 C can be constituted by the heat exchanger 1 .
- FIG. 20 shows a state at the time of an air-warming operation.
- a refrigerant at a high temperature and a high pressure expelled from the compressor 102 enters the indoor-side heat exchanger 106 , where it radiates heat and condenses.
- the refrigerant that has flowed out of the heat exchanger 106 enters the outdoor-side heat exchanger 104 , where it expands and takes in heat from outdoor air, after which it returns to the compressor 102 .
- An airflow generated by the indoor-side blower 108 accelerates heat radiation from the heat exchanger 106
- an airflow generated by the outdoor-side blower 107 accelerates heat absorption by the heat exchanger 104 .
- FIG. 21 shows a state at the time of an air-cooling operation or a defrosting operation.
- the four-way valve 103 is switched to reverse a flow direction of a refrigerant from that in an air-warming operation. That is, a refrigerant at a high temperature and a high pressure expelled from the compressor 102 enters the outdoor-side heat exchanger 104 , where it radiates heat and condenses. Via the decompression expansion device 105 , the refrigerant that has flowed out of the heat exchanger 104 enters the indoor-side heat exchanger 106 , where it expands and takes in heat from indoor air, after which it returns to the compressor 102 . An airflow generated by the outdoor-side blower 107 accelerates heat radiation from the heat exchanger 104 , and an airflow generated by the indoor-side blower 108 accelerates heat absorption by the heat exchanger 106 .
- condensate water gathers on a surface of the heat exchanger 1 on a leeward side thereof that may also be a lower surface side thereof depending on a posture of the heat exchanger 1 .
- condensate water even if formed, can be quickly drained, and thus it is possible to reduce a phenomenon in which condensate water drips over the cross-flow fan 108 a by which it is splashed.
- the present invention is applicable to a side-flow type parallel-flow heat exchanger and an integrated air conditioner equipped with the same.
Abstract
The heat exchanger (1) comprises: two header pipes (2),(3) arranged in parallel with an interval therebetween; a plurality of flat tubes (4) which are arranged between the header pipes and which place coolant paths (5) provided therein in communication with the interior of the header pipes; a plurality of fins (6) attached to the flat surface of each flat tube; and side sheets (10U), (10D) attached to an outside of the fins (6 aU), (6 aD), which are positioned farthest outward among the plurality of fins. The side sheet (10D) positioned in the bottom part of the heat exchanger (1) has a plurality of notches (11) formed at intervals from each other on the edge of the side where condensed water collects in the heat exchanger (1). The notches are each provided with a width sufficient for covering the interval pitch (P) of the fin by several pitch lengths.
Description
- The present invention relates to a side-flow type parallel-flow heat exchanger and an air conditioner equipped with the same.
- A parallel-flow heat exchanger has a configuration in which a plurality of flat tubes are arranged between a plurality of header pipes such that a plurality of refrigerant passages in the flat tubes communicate with interiors of the header pipes, and fins such as corrugated fins are disposed between the flat tubes. Such a parallel-flow heat exchanger is widely used in vehicle air conditioners, outdoor units of air conditioners for buildings, and so on.
- In the parallel-flow heat exchanger, the corrugated fins may be installed exclusively between the flat tubes or may be mounted therebetween and also to an outward facing surface of each outermost positioned one of the plurality of flat tubes. Examples of the latter case can be seen in
Patent Documents 1 to 3. - A heat exchanger described in
Patent Document 1 is a parallel-flow heat exchanger in which flat tubes are arranged in horizontal rows. In this heat exchanger, corrugated fins are mounted also to an outward facing flat surface of each outermost one of the flat tubes, and a side plate for fin protection is disposed on an outside of each outermost one of the corrugated fins. - A heat exchanger described in
Patent Document 2 also is a parallel-flow heat exchanger in which flat tubes are arranged in horizontal rows. In this heat exchanger, corrugated fins are mounted also to an outward facing flat surface of each outermost one of the flat tubes, and a side plate for reinforcing a core portion composed of the flat tubes and the corrugated fins, which are alternately layered on each other, is disposed on an outside of each outermost one of the corrugated fins. - A heat exchanger described in
Patent Document 3 also is a parallel-flow heat exchanger in which flat tubes are arranged in horizontal rows. In this heat exchanger, a side sheet is brazed to an exterior of one of the corrugated fins at each of both ends of the heat exchanger. - In a case where a heat exchanger is used as an evaporator, moisture in the atmosphere condenses on a cooled surface of the heat exchanger, and thus condensate water is formed. In a side-flow type parallel-flow heat exchanger, if condensate water is accumulated on surfaces of flat tubes or of corrugated fins, an area of an air flow passage is narrowed by the water, so that heat exchange performance is deteriorated. For this reason, it is required that a side-flow type parallel-flow heat exchanger be configured to allow condensate water to be quickly drained, thereby preventing it from being accumulated therein.
- When an air temperature is low, condensate water turns into frost on a surface of a heat exchanger. Such frost may even turn into ice. In this specification, the term “condensate water” is intended to encompass so-called defrosted water that is water resulting from melting of such frost or ice.
- When, as in the configurations described in the above patent documents, a parallel-flow heat exchanger including a side sheet provided on an outside of each outermost fin is used by adopting a so-called side-flow method in which header pipes are arranged in perpendicular rows, and flat tubes are arranged in horizontal rows, there occurs a problem that condensate water is held by a lower-side one of the side sheets.
Patent Documents - In a heat exchanger described in
Patent Document 4, when seen from below, an outermost corrugated fin positioned at a lower portion is at least partly exposed to have an exposed portion. The exposed portion is made to emerge by reducing a width of a side plate positioned on an outside of this outermost corrugated fin. - In a heat exchanger described in
Patent Document 5, water drainage holes for draining condensate water are provided through a side plate as a bottom surface plate. Through the lower-side side plate, the water drainage holes are provided in such a number and size as not to deteriorate mechanical strength of the side plate. -
- Patent Document 1: JP-A-H5-79788
- Patent Document 2: JP-A-2006-64194
- Patent Document 3: JP-A-2007-139376
- Patent Document 4: JP-A-2010-249388
- Patent Document 5: JP-A-S61-223465
- It is an object of the present invention to provide, in a side-flow type parallel-flow heat exchanger, a structure capable of draining condensate water from a lower-side outermost fin as quickly as possible.
- A side-flow type parallel-flow heat exchanger according to the present invention includes: a plurality of header pipes that are arranged parallel to each other at an interval therebetween; a plurality of flat tubes that are arranged between the plurality of header pipes and each have therein a refrigerant passage communicating with interiors of the plurality of header pipes; a plurality of fins that are mounted to flat surfaces of the plurality of flat tubes; and a side sheet that is attached to an outside of each outermost positioned one of the plurality of fins. One of the side sheets, which is positioned at a lower portion of said heat exchanger, is provided, at an edge thereof on a condensate water gathering side in said heat exchanger, with a plurality of notches formed at intervals from each other, and each of the notches has a width extending over a length plural times a length of an interval pitch of the fins.
- In the heat exchanger configured as above, preferably, the notches have a shape having an angle of less than 180° inside from the edge of the one of the side sheets.
- In the heat exchanger configured as above, preferably, the notches are tapered from the edge of the one of the side sheets.
- In the heat exchanger configured as above, preferably, the one of the side sheets is provided, at an edge thereof on a side opposite to the condensate water gathering side, with a plurality of notches formed at intervals from each other, and each of the notches has a width extending over a length plural times a length of the interval pitch of the fins.
- In the heat exchanger configured as above, preferably, the notches formed in the one of the side sheets on the condensate water gathering side or the notches formed in the one of the side sheets on the side opposite to the condensate water gathering side have a depth exceeding half a depth of the one of the side sheets.
- In the heat exchanger configured as above, preferably, the notches formed on the condensate water gathering side and the notches formed on the side opposite to the condensate water gathering side are arranged so as to be mutually staggered.
- In the heat exchanger configured as above, preferably, a part of said heat exchanger can be formed into a curved portion by bending, and a part of the one of the side sheets, which is to be subjected to the bending, is provided, at an edge thereof that is to be convex after the bending, with a plurality of slits formed by cutting at intervals from each other.
- In the heat exchanger configured as above, preferably, the one of the side sheets is provided, at an edge thereof that is to be concave after bending, with a plurality of the notches that have a width extending over a length plural times a length of the interval pitch of the fins and are formed at intervals from each other.
- In the heat exchanger configured as above, preferably, the one of the side sheets has a plurality of through holes formed at intervals from each other at portions thereof other than portions where the notches are formed.
- In the heat exchanger configured as above, preferably, each of the through holes is formed to have a width extending over a length plural times a length of the interval pitch of the fins.
- In the heat exchanger configured as above, preferably, in a depth direction, the one of the side sheets has a width smaller than a width of the fins, and the fins are exposed to an outside of the one of the side sheets on each of the condensate water gathering side and a side opposite to the condensate water gathering side.
- An air conditioner according to the present invention includes the heat exchanger of any one of the above-described configurations, and the heat exchanger is incorporated in an outdoor unit or an indoor unit of the air conditioner.
- According to the present invention, even if condensate water is formed on an outermost fin positioned at a lower portion of a heat exchanger, or condensate water formed at an upper part of the heat exchanger flows down to the lower portion of the heat exchanger, such condensate water quickly drips down, i.e. is quickly drained.
-
FIG. 1 is a front view of a heat exchanger according to an embodiment of the present invention. -
FIG. 2 is a perspective view of the heat exchanger shown inFIG. 1 . -
FIG. 3 is a bottom view of the heat exchanger shown inFIG. 1 . -
FIG. 4 is a partially enlarged view based onFIG. 1 . -
FIG. 5 is a partial perspective view of the heat exchanger shown inFIG. 1 . -
FIG. 6 is an explanatory view explaining a relationship between an interval pitch of fins and a width of a notch. -
FIG. 7 is an explanatory view explaining a relationship between the interval pitch of the fins and a width of a through hole. -
FIG. 8 is a first diagram explaining a shape of the notch. -
FIG. 9 is a second diagram explaining a shape of the notch. -
FIG. 10 is a third diagram explaining a shape of the notch. -
FIG. 11 is a fourth diagram explaining a shape of the notch. -
FIG. 12 is a fifth diagram explaining a shape of the notch. -
FIG. 13 is a sixth diagram explaining a shape of the notch. -
FIG. 14 is a first diagram explaining a shape of the through hole. -
FIG. 15 is a second diagram explaining a shape of the through hole. -
FIG. 16 is a third diagram explaining a shape of the through hole. -
FIG. 17 is a view explaining a method for forming the notches at a curved portion of the heat exchanger. -
FIG. 18 is a view explaining a modified form of a side sheet. -
FIG. 19 is a schematic sectional view of an outdoor unit of an air conditioner equipped with the heat exchanger according to the present invention. -
FIG. 20 is a schematic configuration view of the air conditioner equipped with the heat exchanger according to the present invention, showing a state at the time of an air-warming operation. -
FIG. 21 is a schematic configuration view of the air conditioner equipped with the heat exchanger according to the present invention, showing a state at the time of an air-cooling operation. -
FIG. 22 is a perpendicular sectional view explaining a basic structure of a side-flow type parallel-flow heat exchanger. -
FIG. 23 is a perpendicular sectional view taken along a line A-A ofFIG. 22 . - With reference to the appended drawings, the following describes embodiments of the present invention.
-
FIGS. 22 and 23 show a basic structure of a side-flow type parallel-flow heat exchanger. In each ofFIGS. 22 and 23 , an upper side of the figure is an upper side of the heat exchanger, and a lower side of the figure is a lower side of the heat exchanger. In aheat exchanger 1, twoperpendicular header pipes header pipes flat tubes 4 are arranged at a predetermined pitch in a perpendicular direction. Each of theflat tubes 4 is an elongated metal member formed by extrusion and has therein arefrigerant passage 5 for a refrigerant to flow therethrough. Theflat tubes 4 are arranged with an extrusion direction thereof, which is also a longitudinal direction thereof, set to be horizontal, and thus a direction in which a refrigerant flows through therefrigerant passage 5 also is horizontal. A plurality of therefrigerant passages 5 equal in sectional shape and sectional area are arranged in a depth direction inFIG. 22 , so that a perpendicular section of each of theflat tubes 4 has a harmonica-like shape as shown inFIG. 23 . Each of therefrigerant passages 5 communicates with interiors of theheader pipes Fins 6 are mounted to flat surfaces of theflat tubes 4, respectively. While, as thefins 6, corrugated fins are used herein, plate fins also may be used. Needless to say, at a stage of actually being incorporated in equipment, the parallel-flow heat exchanger 1 is installed at various angles as required from a design standpoint, and there are many cases where strict meanings of “perpendicular” and “horizontal” are not applicable. - The
header pipes flat tubes 4, and thefins 6 are all made of a metal having good thermal conductivity, such as aluminum. Theflat tubes 4 are fixed to theheader pipes fins 6 are fixed to theflat tubes 4 by brazing or welding. - The
fins 6 are disposed between theflat tubes 4 such that each of thefins 6 is fixed at both of its upper and lower ends to the flat surfaces of each pair of adjacent upper and lower ones of theflat tubes 4, respectively. Naturally, a fin disposed on an outward facing flat surface of each outermost (uppermost or lowermost) positioned one of the plurality offlat tubes 4 arranged in vertical rows is fixed only at one of its upper and lower ends to the flat surface of the each tube. Henceforth, such a fin is referred to as an outermost fin. An outermost fin positioned at an upper portion of theheat exchanger 1 is indicated by areference symbol 6 aU, and an outermost fin positioned at a lower portion of theheat exchanger 1 is indicated by areference symbol 6 aD. - A
side sheet 10U is disposed on an outside of theoutermost fin 6 aU, and aside sheet 10D is disposed on an outside of theoutermost fin 6 aD. Theside sheets outermost fins 6 aU and 6 aD, respectively, by brazing or welding. - The
heat exchanger 1 is of a side-flow type, and only theheader pipe 3 is provided withrefrigerant gates header pipe 3, twopartition plates header pipe 2, apartition plate 9 b is provided at a height intermediate between heights at which thepartition plates - In a case where the
heat exchanger 1 is used as an evaporator, a refrigerant flows in through the lower-siderefrigerant gate 7 as shown by a solid line arrow inFIG. 22 . The refrigerant that has entered through therefrigerant gate 7 is blocked by thepartition plate 9 a to be directed to theheader pipe 2 via some of theflat tubes 4. This flow of the refrigerant is represented by a left-pointing block arrow. The refrigerant that has entered theheader pipe 2 is blocked by thepartition plate 9 b to be directed to theheader pipe 3 via other ones of theflat tubes 4. This flow of the refrigerant is represented by a right-pointing block arrow. The refrigerant that has entered theheader pipe 3 is blocked by thepartition plate 9 c to be directed again to theheader pipe 2 via still other ones of theflat tubes 4. This flow of the refrigerant is represented by another left-pointing block arrow. The refrigerant that has entered theheader pipe 2 turns around to be directed again to theheader pipe 3 via still other ones of theflat tubes 4. This flow of the refrigerant is represented by another right-pointing block arrow. The refrigerant that has entered theheader pipe 3 flows out through therefrigerant gate 8. In this manner, the refrigerant flows from bottom to top of theheat exchanger 1, forming a zigzag path. The herein described case of using three partition plates is merely one example, and the number of partition plates used and a resulting number of times the flow of a refrigerant turns around can be set arbitrarily as required. - In a case where the
heat exchanger 1 is used as a condenser, a flow direction of a refrigerant is reversed. That is, a refrigerant enters theheader pipe 3 through therefrigerant gate 8 as shown by a dotted line arrow inFIG. 22 and then is blocked by thepartition plate 9 c to be directed to theheader pipe 2 via some of theflat tubes 4. In theheader pipe 2, the refrigerant is blocked by thepartition plate 9 b to be directed to theheader pipe 3 via other ones of theflat tubes 4. In theheader pipe 3, the refrigerant is blocked by thepartition plate 9 a to be directed again to theheader pipe 2 via still other ones of theflat tubes 4. In theheader pipe 2, the refrigerant turns around to be directed again to theheader pipe 3 via still other ones of theflat tubes 4. Then, the refrigerant flows out through therefrigerant gate 7 as shown by another dotted line arrow. In this manner, the refrigerant flows from top to bottom of theheat exchanger 1, forming a zigzag path. - The
heat exchanger 1 is not limited in configuration to the above-described one. A configuration is also possible in which both of theheader pipes header pipes -
FIGS. 1 to 5 show a structure of theheat exchanger 1 as an embodiment of the present invention. In these figures, constituent components common with those in the basic structure shown inFIGS. 22 and 23 are indicated by the same reference symbols as used inFIGS. 22 and 23 , and descriptions thereof are omitted. - In a case where the
heat exchanger 1 is used as an evaporator, moisture in the atmosphere condenses on a cooled surface of theheat exchanger 1, and thus condensate water is fowled. The intended meaning of “condensate water” is as described earlier. In a parallel-flow heat exchanger such as theheat exchanger 1, if condensate water is accumulated on surfaces of flat tubes or of fins, a sectional area of an air flow passage is narrowed by the water, so that heat exchange performance is deteriorated. In addition, since theheat exchanger 1 is of the side-flow type, condensate water formed on an upper one offlat tubes 4 or offins 6 flows therefrom sequentially down to the lower ones of theflat tubes 4 or of thefins 6, and anoutermost fin 6 aD, therefore, is a place where accumulation of condensate water is most likely to occur. - Accumulated condensate water narrows an area of an air flow passage of the
heat exchanger 1 and thus hinders ventilation, so that heat exchange performance is deteriorated. Furthermore, in a case where theheat exchanger 1 is incorporated in an outdoor unit of an air conditioner, with a drop of an outside air temperature to a freezing point or lower, condensate water may freeze to cause damage to theheat exchanger 1. For this reason, it is required that condensate water formed in theheat exchanger 1 be drained as quickly as possible. - In the present invention, in order to solve the above-described problem, a
side sheet 10D positioned at the lower portion of theheat exchanger 1 is configured as follows. That is, theside sheet 10D is provided, at an edge thereof on a condensate water gathering side in theheat exchanger 1, with a plurality ofnotches 11 formed at intervals from each other. - In the case where the
heat exchanger 1 is incorporated in an outdoor unit of an air conditioner, condensate water gathers on a windward side of theheat exchanger 1. This is for the following reason. That is, in an outdoor unit, theheat exchanger 1 is installed in a state of standing substantially upright without being tilted. In a case where theheat exchanger 1 is used as an evaporator (as in, for example, an air-warming operation), heat exchange is performed more actively on a windward side than on a leeward side, and thus condensate water is accumulated on the windward side. Hence, the windward side is a condensate water gathering side. - The
heat exchanger 1 is designed to be incorporated in an outdoor unit of an air conditioner and, as shown inFIGS. 2 , 3, and 5, has one curved portion la at some point along its length, thus having a substantially L-shaped planar shape. A convex side of the curved portion la is a windward side in the outdoor unit. Accordingly, in each ofFIGS. 3 and 4 , a lower side of the figure is a condensate water gathering side, and theside sheet 10D has thenotches 11 formed at the edge thereof on this side. - Preferably, the
individual notches 11 have a shape having an angle of less than 180° inside theside sheet 10D from the edge of theside sheet 10D and are tapered from the edge of theside sheet 10D. In the embodiment, as a shape satisfying these conditions, a V shape is selectively adopted. As shown inFIG. 6 , each of thenotches 11 has, at its widest portion, a width W1 extending over a length plural times a length of an interval pitch P of thefins 6. - Since the
notches 11 are tapered from the edge of theside sheet 10D, as shown by arrows inFIG. 8 , condensate water, upon contact with an edge of each of thenotches 11, is guided deep into the each of thenotches 11, and at a deepest point thereof, flows of the water join together to form a water droplet. Such a water droplet grows fast and drips down, i.e. is drained. Since thenotches 11 have a width extending over a length plural times a length of the interval pitch P of thefins 6, it takes only a short time for condensate water to gather to form a large water droplet, thus enabling efficient drainage of condensate water. - The
notches 11 in the present invention are not limited in shape to a V shape. Any of various shapes exemplarily shown inFIGS. 9 to 12 or any other shape can be adopted. -
Notches 11 shown inFIG. 9 have a semicircular shape or a U shape. While not having an angle at their depths, thenotches 11 of this type satisfy the condition that they are tapered from the edge of theside sheet 10D. -
Notches 11 shown inFIG. 10 have a trapezoidal shape. Thenotches 11 of this type satisfy the condition that they have an angle of less than 180° inside theside sheet 10D from the edge thereof by having two angles of less than 180° and more than 90°, namely, twoobtuse angles 11 a. Furthermore, thenotches 11 of this type also satisfy the condition that they are tapered from the edge of theside sheet 10D. -
Notches 11 shown inFIG. 11 have an inverted M shape. Thenotches 11 of this type satisfy the condition that they have an angle of less than 180° inside theside sheet 10D from the edge thereof by having two angles of less than 90°, namely, twoacute angles 11 b. Furthermore, thenotches 11 of this type also satisfy the condition that they are tapered from the edge of theside sheet 10D. -
Notches 11 shown inFIG. 12 have an inverted trapezoidal shape, each having a width that is reduced at its entry provided at the edge of theside sheet 10D and increases with increasing depth from the entry. Thenotches 11 of this type satisfy the condition that they have an angle of less than 180° inside theside sheet 10D from the edge thereof by having two angles of less than 90°, namely, twoacute angles 11 b. - No matter which shape the
notches 11 have among the shapes shown inFIGS. 8 to 12 , condensate water, upon contact with an edge of each of thenotches 11, is guided deep into the each of thenotches 11, and at a deepest point thereof, flows of the water join together to form a large water droplet, which then drips down. - The
side sheet 10D is provided, also at an edge thereof on a side opposite to the condensate water gathering side in theheat exchanger 1, with a plurality ofnotches 12 formed at intervals from each other. That is, theside sheet 10D has notches formed at the edges of both sides thereof. In each ofFIGS. 3 and 4 , an upper side of the figure is the side opposite to the condensate water gathering side. In the case where theheat exchanger 1 is incorporated in an outdoor unit of an air conditioner, the side opposite to the condensate water gathering side is a leeward side of theheat exchanger 1. Similarly to thenotches 11, thenotches 12 have a width extending over a length plural times a length of the interval pitch P of thefins 6 and are tapered from the edge of theside sheet 10D. - In the embodiment shown in
FIGS. 1 to 5 , thenotches 11 and thenotches 12 are the same in shape (V shape) and size, which, however, is not necessarily required. Thenotches 12 may have a shape (any of the shapes exemplarily shown inFIGS. 9 to 12 or any other shape) different from that of thenotches 11, and there may be a difference in width between thenotches 11 and thenotches 12. - As described above, in the case where the
heat exchanger 1 is incorporated in an outdoor unit of an air conditioner, theside sheet 10D is provided, also at the edge thereof on the side (leeward side) opposite to the condensate water gathering side (windward side) in theheat exchanger 1, with thenotches 12 and, therefore, has notches fainted at the edges of both sides thereof. This further enhances a condensate water drainage capability of theside sheet 10D, and thus condensate water at theoutermost fin 6 aD can be quickly drained. - While this embodiment adopts a configuration in which the
side sheet 10D is provided with notches at the edge thereof on the condensate water gathering side and at the edge thereof on the side opposite thereto in theheat exchanger 1, in other words, a configuration in which theside sheet 10D has notches formed at the edges of both sides thereof, a configuration also may be adopted in which theside sheet 10D has notches formed only at the edge thereof on the condensate water gathering side. - The
notches side sheet 10D. With this configuration, theside sheet 10D has a shape shown inFIG. 13 and thus allows condensate water to be quickly drained from theoutermost fin 6 aD. - While in
FIG. 13 ,notches notches 11 is staggered with respect to each of thenotches 12, there is no limitation thereto. For example, a configuration also may be adopted in which thenotches notches 11 are staggered with respect to each of thenotches 12. - The
side sheet 10D has throughholes 13 formed at portions thereof other than portions where thenotches notches 11 and thenotches 12, a plurality of the throughholes 13 are formed at intervals from each other. The through holes 13 have a shape of an elongated circle (racetrack circle) whose longitudinal axis is aligned with a length direction of theflat tubes 4 and, as shown inFIG. 7 , have a width W2 extending over a length plural times a length of the interval pitch P of thefins 6. - Since the through
holes 13 are present, drainage of condensate water accumulated at theoutermost fin 6 aD is even further enhanced. - The through holes 13 are not limited in shape to an elongated circular shape. Various shapes such as an elliptical shape shown in
FIG. 14 can be selectively adopted. - Preferred as the shape of the through
holes 13 is not only a non-angular shape such as an elongated circular shape or an elliptical shape. A shape having an angle of less than 180° also is preferred as the shape of the through holes 13. - For example, in a case of having a rectangular shape shown in
FIG. 15 , each of the throughholes 13 has a right angle at each of four corners thereof. In a case of having a rhombus shape shown inFIG. 16 , each of the throughholes 13 has, on one diagonal axis thereof, two angles of less than 180° and more than 90°, namely, two obtuse angles, and on the other diagonal axis thereof orthogonal to the one diagonal axis, two angles of less than 90°, namely, two acute angles. - With the through
holes 13 shaped to have an angle of less than 180° as in the above-described shapes, condensate water is guided toward the angle where flows of the water join together to form a large water droplet, which then drips down. Thus, condensate water is quickly drained. - It is not necessarily required that the though holes 13 have a width extending over a length plural times a length of the interval pitch P of the
fins 6. Setting the throughholes 13 to have a width extending over a length plural times a length of the interval pitch P of thefins 6, however, allows a large amount of condensate water to collect and thus can expedite drainage of the water. - A
side sheet 10D shown inFIG. 18 has throughholes 13 but is not provided withnotches side sheet 10D having such a configuration has a function of accelerating drainage of condensate water from theoutermost fin 6 aD. - A comparison between a width of the
outermost fin 6 aD in a depth direction thereof, namely, an air-passing direction and a width of theside sheet 10D in the same direction indicates that the width of theside sheet 10D is made smaller than the width of theoutermost fin 6 aD. Consequently, as shown inFIGS. 2 to 5 , theoutermost fin 6 aD is exposed to an outside of theside sheet 10D on each of the condensate water gathering side and the side opposite thereto. A portion thus exposed is present, and such an exposed portion acts as a drainage port, so that condensate water is quickly drained from theoutermost fin 6 aD. It is not required that theside sheet 10U be smaller in width than theoutermost fin 6 aU. For example, theside sheet 10U may be the same in width as theoutermost fin 6 aU. - As described earlier, the
heat exchanger 1 has onecurved portion 1 a at some point along its length, thus having a substantially L-shaped planar shape. After theheat exchanger 1 is formed by using theflat tubes 4 of a linear shape, thecurved portion 1 a is formed by bending theheat exchanger 1, and this process of bending can be utilized also to form thenotches 11. - As shown in a rectangular framed area at a lower portion of
FIG. 17 , a part of theside sheet 10D that is to be subjected to bending is provided, at an edge thereof that is to be convex after the bending, with a plurality ofslits 14 formed by cutting at intervals from each other. As a result of bending, theslits 14 are opened into a V shape as shown in an upper drawing inFIG. 17 and thus constitute thenotches 11 having a width extending over a length plural times a length of the interval pitch P of thefins 6. This can facilitate the formation of thenotches 11. - The
side sheet 10D is provided with thenotches 12 at an edge thereof on a side that is to be concave after bending. In consideration of the fact that bending causes thenotches 12 to be reduced in open angle, in order that, even in such a state, thenotches 12 will have an open angle equal to that thereof at a non-bent portion of theside sheet 10D, i.e. thenotches 12 will have a width extending over a length plural times a length of the interval pitch P of thefins 6, thenotches 12 are set to have a V shape having a wide pre-bending angle. - The above-described
heat exchanger 1 can be incorporated in an outdoor unit or an indoor unit of a separate type air conditioner.FIG. 19 shows an example in which theheat exchanger 1 is incorporated in the outdoor unit. - An
outdoor unit 20 shown inFIG. 19 includes a sheet-metal housing 20 a having a substantially rectangular planar shape, longer sides of which constitute afront face 20F and aback face 20B, and shorter sides of which constitute aleft side face 20L and aright side face 20R. Anexhaust port 21 is formed in thefront face 20F, a back-faceair intake port 22 is formed in theback face 20B, and a side-faceair intake port 23 is formed in theleft side face 20L. Theexhaust port 21 is an assembly of a plurality of horizontal slit-shaped openings, and the back-faceair intake port 22 and the side-faceair intake port 23 are lattice-shaped openings. Four sheet-metal members that are thefront face 20F, theback face 20B, the left side face 20L, and the right side face 20R, together with unshown top and bottom panels, form the box-shapedhousing 20 a. - In the
housing 20 a, aheat exchanger 1 having an L-shaped thermal plane is disposed on an immediately inner side relative to the back-faceair intake port 22 and the side-faceair intake port 23. Ablower 24 is disposed between theheat exchanger 1 and theexhaust port 21 in order to forcibly cause heat exchange between theheat exchanger 1 and outdoor air. Theblower 24 is formed by combining anelectric motor 24 a with apropeller fan 24 b. In thehousing 20 a, on an inner surface of thefront face 20F, abell mouth 25 is fitted so as to surround thepropeller fan 24 b for improved blowing efficiency. Thehousing 20 a includes a space on an inner side relative to the right side face 20R, which is isolated by apartition wall 26 from an air flow flowing from the back-faceair intake port 22 to theexhaust port 21, and acompressor 27 is accommodated in this space. - Condensate water formed in the
heat exchanger 1 of theoutdoor unit 20 narrows an area of an air flow passage, so that heat exchange performance is deteriorated. Moreover, in a cold climate environment where an outside air temperature stays below the freezing point, such condensate water may even freeze to cause damage to theheat exchanger 1. Thus, in theoutdoor unit 20, drainage of condensate water from theheat exchanger 1 is a crucial problem. - For the reason described earlier, in the
outdoor unit 20, condensate water gathers on a windward side of theheat exchanger 1. Condensate water formed on the windward side rarely flows over to a leeward side but directly reaches a lower portion of theheat exchanger 1 on the windward side. When an outside air temperature is low, condensate water freezes to theheat exchanger 1 in the form of frost. An increased amount of frost necessitates a defrosting operation. During the defrosting operation, theblower 24 is stopped from operating, and thus water resulting from melting of the frost flows mainly downward to be accumulated due to gravity without being affected by wind. For this reason, theside sheet 10D at a lower portion of theheat exchanger 1 is formed to have the configuration of the present invention, so that condensate water is quickly drained, and this can reduce detrimental effects caused by accumulation of condensate water. - That is, the
side sheet 10D attached to an outside of theoutermost fin 6 aD is provided, at the edge thereof on a condensate water gathering side, with the plurality ofnotches 11 formed at intervals from each other. Each of thenotches 11 has a width extending over a length plural times a length of the interval pitch of the fins. By the configuration described above, assuming that condensate water is formed on theoutermost fin 6 aD positioned at the lower portion of theheat exchanger 1, or that condensate water formed at an upper part of theheat exchanger 1 flows down to theoutermost fin 6 aD, the condensate water is drawn deep into each of thenotches 11 to collect and thus quickly drips down, i.e. is drained. This can prevent a situation in which condensate water is accumulated at theoutermost fin 6 aD positioned at the lower portion of theheat exchanger 1, so that a ventilation characteristic is impaired to deteriorate heat exchange performance. -
FIGS. 20 and 21 show an example in which theheat exchanger 1 is incorporated in an indoor unit of a separate type air conditioner. In the separate type air conditioner shown inFIGS. 20 and 21 , an outdoor unit includes a compressor, a four-way valve, an expansion valve, an outdoor-side heat exchanger, an outdoor-side blower, and so on, and the indoor unit includes an indoor-side heat exchanger, an indoor-side blower, and so on. In an air-warming operation, the outdoor-side heat exchanger functions as an evaporator, and in an air-cooling operation, as a condenser. In an air-warming operation, the indoor-side heat exchanger functions as a condenser, and in an air-cooling operation, as an evaporator. -
FIG. 20 shows a basic configuration of the separate type air conditioner using a heat pump cycle as a refrigeration cycle. Aheat pump cycle 101 is formed by connecting, in a loop, acompressor 102, a four-way valve 103, an outdoor-side heat exchanger 104, adecompression expansion device 105, and an indoor-side heat exchanger 106. Thecompressor 102, the four-way valve 103, theheat exchanger 104, and thedecompression expansion device 105 are housed in a housing of anoutdoor unit 110, and theheat exchanger 106 is housed in a housing of anindoor unit 120. Theheat exchanger 104 is combined with an outdoor-side blower 107, and theheat exchanger 106 is combined with an indoor-side blower 108. Theblower 107 includes apropeller fan 107 a for forming a blow-off airflow, and theblower 108 includes across-flow fan 108 a for forming a blow-off airflow. Thecross-flow fan 108 a is disposed below theheat exchanger 106, with its axis line set to be horizontal. - The
heat exchanger 1 according to the present invention can be used as a constituent component of theheat exchanger 106 of the indoor unit. Theheat exchanger 106 is composed of threeheat exchangers blower 108, and any one or all of theheat exchangers heat exchanger 1. -
FIG. 20 shows a state at the time of an air-warming operation. At this time, a refrigerant at a high temperature and a high pressure expelled from thecompressor 102 enters the indoor-side heat exchanger 106, where it radiates heat and condenses. Via thedecompression expansion device 105, the refrigerant that has flowed out of theheat exchanger 106 enters the outdoor-side heat exchanger 104, where it expands and takes in heat from outdoor air, after which it returns to thecompressor 102. An airflow generated by the indoor-side blower 108 accelerates heat radiation from theheat exchanger 106, and an airflow generated by the outdoor-side blower 107 accelerates heat absorption by theheat exchanger 104. -
FIG. 21 shows a state at the time of an air-cooling operation or a defrosting operation. At this time, the four-way valve 103 is switched to reverse a flow direction of a refrigerant from that in an air-warming operation. That is, a refrigerant at a high temperature and a high pressure expelled from thecompressor 102 enters the outdoor-side heat exchanger 104, where it radiates heat and condenses. Via thedecompression expansion device 105, the refrigerant that has flowed out of theheat exchanger 104 enters the indoor-side heat exchanger 106, where it expands and takes in heat from indoor air, after which it returns to thecompressor 102. An airflow generated by the outdoor-side blower 107 accelerates heat radiation from theheat exchanger 104, and an airflow generated by the indoor-side blower 108 accelerates heat absorption by theheat exchanger 106. - In a case where the
heat exchanger 1 according to the present invention is used as a constituent component of theheat exchanger 106 of the indoor unit, condensate water gathers on a surface of theheat exchanger 1 on a leeward side thereof that may also be a lower surface side thereof depending on a posture of theheat exchanger 1. Through the use of theheat exchanger 1 according to the present invention, condensate water, even if formed, can be quickly drained, and thus it is possible to reduce a phenomenon in which condensate water drips over thecross-flow fan 108 a by which it is splashed. - The foregoing has described the embodiments of the present invention. The present invention, however, is not limited in scope thereto and can be implemented in variously modified forms within the spirit of the invention.
- The present invention is applicable to a side-flow type parallel-flow heat exchanger and an integrated air conditioner equipped with the same.
-
-
- 1 heat exchanger
- 2, 3 header pipe
- 4 flat tube
- 5 refrigerant passage
- 6 fin
- 6 aU, 6 aD outermost fin
- 10U, 10D side sheet
- 11, 12 notch
- 13 through hole
- 20 outdoor unit
- 110 outdoor unit
- 120 indoor unit
Claims (12)
1. A side-flow type parallel-flow heat exchanger, comprising:
a plurality of header pipes that are arranged parallel to each other at an interval therebetween;
a plurality of flat tubes that are arranged between the plurality of header pipes and each have therein a refrigerant passage communicating with interiors of the plurality of header pipes;
a plurality of fins that are mounted to flat surfaces of the plurality of flat tubes; and
a side sheet that is attached to an outside of each outermost positioned one of the plurality of fins,
wherein
one of the side sheets, which is positioned at a lower portion of said heat exchanger, is provided, at an edge thereof on a condensate water gathering side in said heat exchanger, with a plurality of notches formed at intervals from each other, and
each of the notches has a width extending over a length plural times a length of an interval pitch of the fins.
2. The heat exchanger according to claim 1 , wherein
the notches have a shape having an angle of less than 180° inside from the edge of the one of the side sheets.
3. The heat exchanger according to claim 2 , wherein
the notches are tapered from the edge of the one of the side sheets.
4. The heat exchanger according to claim 3 , wherein
the one of the side sheets is provided, at an edge thereof on a side opposite to the condensate water gathering side, with a plurality of notches formed at intervals from each other, and
each of the notches has a width extending over a length plural times a length of the interval pitch of the fins.
5. The heat exchanger according to claim 4 , wherein
the notches formed in the one of the side sheets on the condensate water gathering side or the notches formed in the one of the side sheets on the side opposite to the condensate water gathering side have a depth exceeding half a depth of the one of the side sheets.
6. The heat exchanger according to claim 4 , wherein
the notches formed on the condensate water gathering side and the notches formed on the side opposite to the condensate water gathering side are arranged so as to be mutually staggered.
7. The heat exchanger according to claim 1 , wherein
a part of said heat exchanger can be formed into a curved portion by bending, and a part of the one of the side sheets, which is to be subjected to the bending, is provided, at an edge thereof that is to be convex after the bending, with a plurality of slits formed by cutting at intervals from each other.
8. The heat exchanger according to claim 7 , wherein
the one of the side sheets is provided, at an edge thereof that is to be concave after bending, with a plurality of the notches that have a width extending over a length plural times a length of the interval pitch of the fins and are formed at intervals from each other.
9. The heat exchanger according to claim 1 , wherein
the one of the side sheets has a plurality of through holes formed at intervals from each other at portions thereof other than portions where the notches are formed.
10. The heat exchanger according to claim 9 , wherein
each of the through holes is formed to have a width extending over a length plural times a length of the interval pitch of the fins.
11. The heat exchanger according to claim 1 , wherein
in a depth direction, the one of the side sheets has a width smaller than a width of the fins, and the fins are exposed to an outside of the one of the side sheets on each of the condensate water gathering side and a side opposite to the condensate water gathering side.
12. An air conditioner comprising the heat exchanger according to claim 1 ,
wherein the heat exchanger is incorporated in an outdoor unit or an indoor unit of said air conditioner.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010286627A JP5009413B2 (en) | 2010-12-22 | 2010-12-22 | Heat exchanger and air conditioner equipped with the same |
JP2010-286627 | 2010-12-22 | ||
PCT/JP2011/076022 WO2012086333A1 (en) | 2010-12-22 | 2011-11-11 | Heat exchanger and air conditioner equipped with same |
Publications (1)
Publication Number | Publication Date |
---|---|
US20130240187A1 true US20130240187A1 (en) | 2013-09-19 |
Family
ID=46313615
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/990,100 Abandoned US20130240187A1 (en) | 2010-12-22 | 2011-11-11 | Heat exchanger and air conditioner equipped with same |
Country Status (5)
Country | Link |
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US (1) | US20130240187A1 (en) |
JP (1) | JP5009413B2 (en) |
KR (1) | KR101558717B1 (en) |
CN (1) | CN103261828B (en) |
WO (1) | WO2012086333A1 (en) |
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US20150168072A1 (en) * | 2012-09-04 | 2015-06-18 | Sharp Kabushiki Kaisha | Parallel-flow type heat exchanger and air conditioner equipped with same |
US20150211807A1 (en) * | 2014-01-29 | 2015-07-30 | Trane International Inc. | Heat Exchanger with Fluted Fin |
US20150241080A1 (en) * | 2014-02-21 | 2015-08-27 | Keihin Thermal Technology Corporation | Air-conditioning apparatus for vehicle |
US20170108278A1 (en) * | 2014-04-18 | 2017-04-20 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. | Heat exchanger and manufacturing method therefor, heat exchange module, heat exchange device, and heat source unit |
US20170234587A1 (en) * | 2014-10-16 | 2017-08-17 | Daikin Industries, Ltd. | Refrigerant evaporator |
FR3116593A1 (en) * | 2020-11-20 | 2022-05-27 | Cinier Radiateurs | ANTIVIRAL VERTICAL REVERSIBLE AIR CONDITIONING WALL TERMINAL |
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CN103411281B (en) * | 2012-12-29 | 2015-10-28 | 泰铂(上海)实业有限公司 | Air conditioning for automobiles U-shape heating and cooling used for indoor machine core body |
WO2020129155A1 (en) * | 2018-12-18 | 2020-06-25 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
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US10030912B2 (en) * | 2014-04-18 | 2018-07-24 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. | Heat exchanger and manufacturing method therefor, heat exchange module, heat exchange device, and heat source unit |
US10429134B2 (en) * | 2014-04-18 | 2019-10-01 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. | Heat exchanger and manufacturing method therefor, heat exchange module, heat exchange device, and heat source unit |
US20170234587A1 (en) * | 2014-10-16 | 2017-08-17 | Daikin Industries, Ltd. | Refrigerant evaporator |
US10030899B2 (en) * | 2014-10-16 | 2018-07-24 | Daikin Industries, Ltd. | Refrigerant evaporator |
FR3116593A1 (en) * | 2020-11-20 | 2022-05-27 | Cinier Radiateurs | ANTIVIRAL VERTICAL REVERSIBLE AIR CONDITIONING WALL TERMINAL |
WO2022106181A1 (en) | 2020-11-20 | 2022-05-27 | Cinier Radiateurs | Vertical reversible air-conditioning wall terminal |
Also Published As
Publication number | Publication date |
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CN103261828B (en) | 2015-11-25 |
JP5009413B2 (en) | 2012-08-22 |
JP2012132644A (en) | 2012-07-12 |
KR20140018199A (en) | 2014-02-12 |
CN103261828A (en) | 2013-08-21 |
KR101558717B1 (en) | 2015-10-07 |
WO2012086333A1 (en) | 2012-06-28 |
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