EP2233874B1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
EP2233874B1
EP2233874B1 EP08792152.4A EP08792152A EP2233874B1 EP 2233874 B1 EP2233874 B1 EP 2233874B1 EP 08792152 A EP08792152 A EP 08792152A EP 2233874 B1 EP2233874 B1 EP 2233874B1
Authority
EP
European Patent Office
Prior art keywords
corrugated fins
downwind
upwind
ribs
flat tubes
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08792152.4A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2233874A1 (en
EP2233874A4 (en
Inventor
Takahiro Hashimoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sharp Corp
Original Assignee
Sharp Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sharp Corp filed Critical Sharp Corp
Publication of EP2233874A1 publication Critical patent/EP2233874A1/en
Publication of EP2233874A4 publication Critical patent/EP2233874A4/en
Application granted granted Critical
Publication of EP2233874B1 publication Critical patent/EP2233874B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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

Definitions

  • the present invention relates to a parallel-flow-type heat exchanger.
  • a parallel-flow-type heat exchanger having a plurality of flat tubes arranged between a plurality of header pipes, with refrigerant passages inside the flat tubes communicating with the insides of the header pipes, and with corrugated fins arranged between the flat tubes, is widely used in car air conditioners and the like. Examples are seen in documents JP2005024187 , JP2001066083 , US2006/162376 and JPS58217195 .
  • the heat exchanger described in JP2005024187 has a plurality of header pipes arranged horizontally, and has a plurality of flat tubes arranged vertically, and corrugated fins between the flat tubes are shaped like valleys with their bottom at a central part of the heat exchanger in the depth direction. At the valley-bottom part of the corrugated fins, where they join the flat tubes, through holes are formed; when defrosting operation is performed to melt frost sticking to the heat exchanger, the water resulting from the frost melting is drained through the through holes.
  • JP2001066083 describes a heat exchanger in which a plurality of tongue-like pieces are cut to raise from one and the opposite faces of the flat-plate part of corrugated fins, with a view to increasing heat exchange efficiency at the corrugated fins.
  • US 2006/162376 discloses an evaporator comprising a heat exchange core comprising a plurality of tube groups arranged in rows as spaced forwardly or rearwardly of the evaporator and each comprising a plurality of heat exchange tubes arranged in parallel at a spacing laterally of the evaporator, and a lower tank disposed at a lower end of the core and having connected thereto lower ends of the heat exchange tubes providing the tube groups.
  • the lower tank has a top surface, front and rear opposite side surfaces and a bottom surface.
  • JPS58217195 discloses a heat exchanger comprising two horizontal header pipes arranged in parallel to each other, a plurality of flat tubes connecting said header pipes and having inner refrigerant passages, and corrugated upwind-sided and downwind-sided fins having a condensate drainage gap therebetween.
  • An object of the present invention is to improve the shape of corrugated fins to achieve improved heat efficiency performance in a parallel-flow-type heat exchanger. Another object is to achieve smooth drainage of defrost water and condensed water.
  • a heat exchanger comprises: a first and a second header pipe arranged parallel at an interval from one another; a plurality of vertical flat tubes arranged with a predetermined pitch between the plurality of header pipes, with vertical refrigerant passages provided inside the flat tubes communicating with the insides of the header pipes; and corrugated fins arranged between the flat tubes.
  • the corrugated fins comprise upwind-side corrugated fins whose fin surface has a downward slope toward the downwind side and downwind-side corrugated fins whose fin surface has an upward slope toward the downwind side.
  • the downwind-side ends of the upwind-side corrugated fins and the upwind-side ends of the downwind-side corrugated fins are kept in contact with ribs formed on the side faces of the flat tubes such that a predetermined interval is formed between the upwind-side corrugated fins and the downwind-side corrugated fins, the predetermined interval being a gap with a width of 4 mm or less such that water droplets running down the upwind-side corrugated fins and water droplets running down the downwind-side corrugated fins meet and flow out without causing a bridging phenomenon.
  • the upwind-side corrugated fins have a downward slope and the downwind-side corrugated fins have an upward slope, the length over which the upwind-side corrugated fins and the downwind-side corrugated fins make contact with air can be made large compared with the depth of the flat tubes, resulting in improved heat exchange performance.
  • the ribs are continuous in the vertical direction.
  • the heat exchanger has cuts formed both in downwind-side ends of the upwind-side corrugated fins in contact with ribs and in upwind-side ends of the downwind-side corrugated fins in contact with the ribs, said contact being achieved across the cuts so that the predetermined interval has a width smaller than the thickness of the ribs.
  • the present invention it is possible to increase the length over which the corrugated fins make contact with air and thereby to achieve satisfactory heat exchange, and it is possible to accurately position and assemble the flat tubes and the corrugated fins. It is also possible to achieve quick drainage of defrost water and condensed water.
  • a heat exchanger 1 has two horizontal header pipes 2 and 3 arranged parallel at an interval from one another in the up/down direction, and has a plurality of vertical flat tubes 4 arranged with a predetermined pitch between the header pipes 2 and 3.
  • the flat tubes 4 are elongate members formed by extrusion of a metal with high thermal conductivity, such as aluminum, and has, formed inside them, refrigerant passages for circulation of refrigerant.
  • a plurality of refrigerant passages 5 with an identical cross-sectional shape and an identical cross-sectional area are arranged inside the flat tubes 4; thus the flat tubes 4 appear to have a cross section like a harmonica.
  • the refrigerant passages 5 need not have a uniform cross-sectional shape and a uniform cross-sectional area, but may have different cross-sectional shapes and different cross-sectional areas.
  • the flat tubes 4 are arranged such that their extrusion direction is vertical, and accordingly the direction of the circulation of refrigerant through the refrigerant passages 5 is vertical.
  • the individual refrigerant passages 5 communicate with the inside of the header pipes 2 and 3.
  • the top side of the page is the top side in the vertical direction
  • the bottom side of the page is the bottom side in the vertical direction.
  • a plurality of flat tubes 4 are arranged with a predetermined pitch such that their length direction is vertical.
  • header pipes 2 and 3 and the flat tubes 4 are fixed by welding. Between the flat tubes 4, corrugated fins 6 are arranged, and the flat tubes 4 and the corrugated fins 6 are also fixed by welding. Like the flat tubes 4, the header pipes 2 and 3 and the corrugated fins 6 are formed of a metal with high thermal conductivity (for example, aluminum).
  • a refrigerant inflow port 7 is provided, and at one end of the top-side header pipes 2, a refrigerant outflow port 8 is provided at a position diagonal to the refrigerant inflow port 7.
  • the heat-dissipation (heat-absorption) area of the heat exchanger 1 is large, allowing efficient heat exchange.
  • the left side of the page is the upwind side
  • the right side of the page is the downwind side.
  • the corrugated fins 6 divide into upwind-side corrugated fins 6U and downwind-side corrugated fins 6D.
  • the upwind-side corrugated fins 6U have a fin surface with a downward slope toward the downwind side; the downwind-side corrugated fins 6D have a fin surface with an upward slope toward the downwind side.
  • the downward slope of the upwind-side corrugated fins 6U and the upward slope of the downwind-side corrugated fins have the same angle.
  • the horizontal direction length of the upwind-side corrugated fins 6U and the horizontal direction length of the downwind-side corrugated fins 6D are equal.
  • the downward slope of the upwind-side corrugated fins 6U and the upward slope of the downwind-side corrugated fins 6D do not necessarily have to have the same angle, but may have different angles.
  • the length of the upwind-side corrugated fins 6U and the length of the downwind-side corrugated fins 6D in the air flow direction do not necessarily have to be equal, but may be different.
  • the upwind-side corrugated fins 6U and the downwind-side corrugated fins 6D appear to be a large number of V shapes arranged in the up/down direction.
  • the V shapes here, however, are not closed but open at their bottom part.
  • the upwind-side corrugated fins 6U and the downwind-side corrugated fins 6D are not in close contact with each other, but are arranged with a gap 9 secured between them.
  • the gap 9 is so sized as to enable water droplets sticking to the downwind-side ends of the upwind-side corrugated fins 6U and water droplets sticking to the upwind-side ends downwind-side corrugated fins 6D to coalesce.
  • ridge-shaped ribs 10U are provided that protrude parallel to the air circulation direction (in other words, toward the upwind side); on downwind-side ends of he flat tubes 4, ridge-shaped ribs 10D are provided that protrude parallel to the air circulation direction (in other words, toward the downwind side).
  • the ribs 10U and 10D are formed integrally with the flat tubes 4 by extrusion, and extend continuously along the length direction of the vertically arranged flat tubes, from a position slightly lower than the top end of the flat tubes to a position slightly higher than the bottom end of the flat tubes.
  • the header pipes 2 and 3 only need to have a diameter large enough to receive the body parts of the flat tubes 4, and this helps reduce the diameter of the header pipes 2 and 3 compared with in a case where they need to receive the ribs 10U and 10D as well.
  • the upwind-side ends of the upwind-side corrugated fins 6U extend to close to a position flush with the tip ends of the ribs 10U provided on the upwind-side ends of the flat tubes 4 (in this embodiment, the upwind-side ends of the upwind-side corrugated fins 6U are approximately flush with tip ends of the ribs 10U), and the downwind-side ends of the downwind-side corrugated fins 6D extend to close to a position flush with the tip ends of the ribs 10D provided on the downwind-side ends of the flat tubes 4 (in this embodiment, the downwind-side ends of the downwind-side corrugated fins 6D are approximately flush with the tip ends of the ribs 10D).
  • the width of the ribs 10U and 10D is smaller than the width of the flat tubes 4.
  • gaps are left, and these gaps form vertical drain grooves 11U.
  • gaps are left, and these gaps form vertical drain grooves 11D.
  • ribs 12 are formed that are continuous in the length direction of the flat tubes 4 (in this embodiment, the vertical direction).
  • the downwind-side ends of the upwind-side corrugated fins 6U and the upwind-side ends of the downwind-side corrugated fins 6D are kept in contact with these ribs 12.
  • a gap 9 is formed that has a width equal to the thickness of the ribs 12.
  • the ribs 12 also are formed integrally with the flat tubes 4 by extrusion, and are continuous, in the length direction of the vertically arranged flat tubes, from a position slightly lower than the flat tube top ends to a position slightly higher than the flat tube bottom ends. This eliminates the need to form, in the header pipes 2 and 3, openings in which to insert the ribs 12, and makes simple the process of forming, in the header pipes 2 and 3, openings in which to insert the flat tubes 4.
  • the position of the ribs 12 does not necessarily have to be coincident with the position of the center of the side faces of the flat tubes 4, but may be displaced from it.
  • the upwind-side corrugated fins 6U and the downwind-side corrugated fins 6D need be located within the width of the flat tubes 4 in the air flow direction, their respective lengths in the air flow direction are adjusted. If they may extend out of the width of the flat tubes 4 in the air flow direction, their respective lengths in the air flow direction may be equal to or different from each other.
  • the ribs 12 are continuously formed in the vertical direction, they may instead be each formed of discrete parts, or may be provided only at several places (for example, at a total of three places corresponding to a top, a middle, and a bottom part of the corrugated fins, or at a total of two places corresponding to a top and a bottom part of the corrugated fins).
  • Possible ways of forming such discontinuous ribs 12 include: fitting ribs 12 as separate parts to the body of the flat tubes by welding; machine-removing desired parts of continuous ribs 12 formed integrally with the flat tubes 4; and machine-cutting part of the flat tubes 4 into ribs.
  • the heat exchanger 1 When refrigerant is passed through the heat exchanger 1 while air is circulated with an unillustrated fan, in an operation mode in which the heat exchanger 1 is used as an evaporator (for example, when heating operation is performed by use of the heat exchanger 1 in the outdoor unit of a separate-type air conditioner comprising an indoor unit and an outdoor unit, the heat exchanger 1 acts as an evaporator), the heat exchanger 1 absorbs heat from the air, and in return releases cold into the air.
  • the upwind-side corrugated fins 6U and the downwind-side corrugated fins 6D each have a sloped fin surface, compared with in a case where corrugated fins have no slope and are arranged horizontally, the corrugated fins 6 as a whole extend longer in the air flow direction, achieving high heat exchange performance.
  • the gap 9 is so sized as to enable water droplet sticking to the downwind-side ends of the upwind-side corrugated fins 6U and water droplets sticking to the upwind-side ends of the downwind-side corrugated fins 6D to coalesce; thus, when water droplets on the upwind-side corrugated fins 6U and water droplets on the downwind-side corrugated fins 6D meet at the gap 9, they break each other's surface tension and coalesce, and flow out quickly through the gap 9 without causing the bridging phenomenon.
  • an operation mode in which the heat exchanger 1 is used as an evaporator an operation mode in which the heat exchanger 1 absorbs heat from the outdoor air
  • moisture in the air may, in the form of frost, stick to the surface of the flat tubes 4 and the corrugated fins 6.
  • frost gets thicker and lowers heat exchange performance; thus it is necessary to perform, from time to time, defrosting operation, in which the heat exchanger 1 is turned to a condenser, to melt frost.
  • defrost water resulting from frost melting also is drained smoothly through the drain grooves11U and 11D and the gap 9.
  • the downward slope of the upwind-side corrugated fins 6U and the upward slope of the downwind-side corrugated fins 6D can be selected within the range of 5° to 40°. The sharper the slope, the larger the heat exchange area and thus the easier it is to drain, but the higher the resistance to the circulation of air. It is therefore advisable to set the angle at an appropriate value through experiments.
  • the interval between the flat tubes 4 is 5.5 mm; the thickness of the flat tubes 4 is 1.3 mm; in the air flow direction, the horizontal direction length of both the upwind-side corrugated fins 6U and the downwind-side corrugated fins 6D is 18 mm; the ridge-valley pitch of both the upwind-side corrugated fins 6U and the downwind-side corrugated fins 6D is 2 mm to 3 mm; the size of the gap 9 is 0.5 mm at the maximum. Needless to say, these values are merely examples, and are not meant to limit the contents of the invention.
  • the gap 9 has simply to be so sized as to enable water droplets sticking to the downwind-side ends of the upwind-side corrugated fins 6U and water droplets sticking to the upwind-side ends of the downwind-side corrugated fins 6D to coalesce, its size can be set within the range up to 4 mm at the maximum.
  • a second embodiment of the present invention is shown in Fig. 5 .
  • the ribs 12 need to be given a thickness of 0.5 mm or less.
  • cuts 13 are formed that receive the ribs 12. This makes it possible to give the gap 9 a width smaller than the thickness of the ribs 12.
  • the ribs 12 have a large thickness, it is possible to give the gap 9 such a size as to enable water droplets sticking to the downwind-side ends of the upwind-side corrugated fins 6U and water droplets sticking to the upwind-side ends of the downwind-side corrugated fins 6D to coalesce.
  • the ribs 12 are easier to form by extrusion when they have a thickness that is large to a certain degree (for example, 2 mm). In a case where the gap 9 can be made large (for example, 2 mm), the thickness of the ribs 12 can itself be made use of, and thus there is no need to form cuts 13.
  • the present invention finds wide application in parallel-flow-type heat exchangers.
EP08792152.4A 2007-11-02 2008-08-04 Heat exchanger Not-in-force EP2233874B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007286394A JP4275182B2 (ja) 2007-11-02 2007-11-02 熱交換器
PCT/JP2008/063948 WO2009057364A1 (ja) 2007-11-02 2008-08-04 熱交換器

Publications (3)

Publication Number Publication Date
EP2233874A1 EP2233874A1 (en) 2010-09-29
EP2233874A4 EP2233874A4 (en) 2013-12-18
EP2233874B1 true EP2233874B1 (en) 2017-07-05

Family

ID=40590766

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08792152.4A Not-in-force EP2233874B1 (en) 2007-11-02 2008-08-04 Heat exchanger

Country Status (4)

Country Link
EP (1) EP2233874B1 (zh)
JP (1) JP4275182B2 (zh)
CN (1) CN101809400B (zh)
WO (1) WO2009057364A1 (zh)

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FR2882519B1 (fr) 2005-02-28 2008-12-26 Oreal Coloration de matieres keratiniques notamment humaines par transfert thermique a sec d'un colorant direct azomethinique composition comprenant ledit colorant et son procede de preparation
JP4334588B2 (ja) * 2007-10-04 2009-09-30 シャープ株式会社 熱交換器
JP5517745B2 (ja) * 2010-05-24 2014-06-11 サンデン株式会社 熱交換器用チューブ及び熱交換器
JP5936297B2 (ja) * 2010-09-29 2016-06-22 三菱重工業株式会社 熱交換器
US20120291476A1 (en) * 2011-05-16 2012-11-22 Whirlpool Corporation Cooling system integration enabling platform architecture
JP2013213603A (ja) * 2012-04-02 2013-10-17 Nippon Light Metal Co Ltd コルゲートフィン式熱交換器の排水構造
JP6538076B2 (ja) * 2014-04-16 2019-07-03 杭州三花▲微▼通道▲換▼▲熱▼▲器▼有限公司Ｓａｎｈｕａ（Ｈａｎｇｈｏｕ）Ｍｉｃｒｏ Ｃｈａｎｎｅｌ Ｈｅａｔ Ｅｘｃｈａｎｇｅｒ Ｃｏ．，Ｌｔｄ． フィン及びフィンを備える折り曲げ式熱交換器
KR102375396B1 (ko) 2014-05-13 2022-03-18 노파르티스 아게 연골형성을 유도하기 위한 화합물 및 조성물
CN105987540A (zh) * 2015-02-10 2016-10-05 上海交通大学 管片式平行流换热器
WO2017017814A1 (ja) * 2015-07-29 2017-02-02 三菱電機株式会社 熱交換器及び冷凍サイクル装置
CN108253834A (zh) * 2016-12-28 2018-07-06 丹佛斯微通道换热器（嘉兴）有限公司 用于换热器的扁管和具有该扁管的换热器
CN107726884A (zh) * 2017-09-19 2018-02-23 东莞市丰瑞德温控技术有限公司 倾斜翅片式平行流换热器及其制作工艺
WO2020230268A1 (ja) * 2019-05-14 2020-11-19 三菱電機株式会社 熱交換器及び冷凍サイクル装置

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Also Published As

Publication number Publication date
WO2009057364A1 (ja) 2009-05-07
JP2009115339A (ja) 2009-05-28
EP2233874A1 (en) 2010-09-29
CN101809400A (zh) 2010-08-18
CN101809400B (zh) 2011-11-02
EP2233874A4 (en) 2013-12-18
JP4275182B2 (ja) 2009-06-10

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