TW201335549A - Serpentine heat exchanger for air conditioner - Google Patents

Serpentine heat exchanger for air conditioner Download PDF

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Publication number
TW201335549A
TW201335549A TW101133709A TW101133709A TW201335549A TW 201335549 A TW201335549 A TW 201335549A TW 101133709 A TW101133709 A TW 101133709A TW 101133709 A TW101133709 A TW 101133709A TW 201335549 A TW201335549 A TW 201335549A
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Taiwan
Prior art keywords
heat exchanger
heat
heat transfer
air conditioner
transfer tube
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TW101133709A
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Chinese (zh)
Inventor
Takamichi Watanabe
Shiro Kakiyama
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Sumitomo Light Metal Ind
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Publication of TW201335549A publication Critical patent/TW201335549A/en

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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
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/02—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using coatings, e.g. vitreous or enamel coatings
    • F28F19/04—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using coatings, e.g. vitreous or enamel coatings of rubber; of plastics material; of varnish
    • 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
    • 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
    • F28D1/0477—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 being bent in a serpentine or zig-zag
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular 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
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F28F21/062—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material the heat-exchange apparatus employing tubular 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
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2245/00—Coatings; Surface treatments
    • F28F2245/04—Coatings; Surface treatments hydrophobic

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Provided is a serpentine heat exchanger for an air conditioner, which effectively minimizes losses in heat-exchange performance due to condensation, and can be sufficiently used for a small-sized air conditioner. A serpentine heat exchanger for an air conditioner (10) is configured such that: a plurality of fins (12) is arranged parallel to each other at intervals of 0.6-5.0 mm in a direction (y direction) orthogonal to the direction (x direction) in which air flows as a heat-exchange fluid, and thereby constitutes a fin group (14); a plurality of such fin groups (14) is aligned in a direction (z direction) orthogonal to the x and y directions at a mutual distance of 2.0 mm or less, and thereby constitutes multistage fin groups (14); and a heat-exchanger pipe (16) is arranged in a serpentine configuration so as to sequentially pass through the fin group (14) at each stage.

Description

空調機用蛇管熱交換器 Air duct heat exchanger 技術領域 Technical field

本發明係有關於一種在空氣等熱交換流體與冷媒之間進行熱交換之蛇管熱交換器，尤其係有關於一種適合作為空調機用熱交換器之蛇管熱交換器。 The present invention relates to a coil heat exchanger for exchanging heat between a heat exchange fluid such as air and a refrigerant, and more particularly to a coil heat exchanger suitable as a heat exchanger for an air conditioner.

背景技術 Background technique

以往，空調機用熱交換器主要係使用十字散熱片管型熱交換器。該十字散熱片管型熱交換器之構造，係相對多數散熱片，沿垂直方向***有髮夾形彎曲之多數傳熱管，且藉該等傳熱管之擴管，散熱片與傳熱管接合在一起。此外，在此種熱交換器，係預定冷媒流通傳熱管內，並且空氣於相對傳熱管為垂直之方向沿散熱片流動，如此在冷媒與空氣之間進行熱交換。 Conventionally, a heat exchanger for an air conditioner has mainly used a cross fin heat exchanger. The structure of the cross heat sink tube type heat exchanger is a plurality of heat transfer tubes inserted in a vertical direction with a hairpin-shaped bending, and the heat transfer fins and heat transfer tubes are expanded by the heat transfer tubes. Join together. Further, in such a heat exchanger, the predetermined refrigerant flows through the heat transfer tubes, and the air flows along the fins in a direction perpendicular to the heat transfer tubes, so that heat exchange is performed between the refrigerant and the air.

然而，為製造如此構造之十字散熱片管型熱交換器，必須投入龐大設備投資。即，必須有用以成形鋁板散熱片之大型壓製裝置及其壓製模、用以將鋁板散熱片與傳熱管擴管固接之擴管裝置、及用於擴管裝置之擴管滴定管等等許多設備。尤其係室內熱交換器與室外熱交換器之間，由於散熱片之形狀(有無槽縫和百葉窗等)和傳熱管之管徑差異，所以製造時必須準備因應各種熱交換器之壓製模和擴管滴定管等，而準備此類設備需要龐大投資，因此便成為阻礙如改變熱交換器形狀之模型變更之原因。 However, in order to manufacture such a cross-shaped fin-and-tube heat exchanger, a huge equipment investment must be invested. That is, it is necessary to use a large-scale pressing device for forming an aluminum plate fin and a pressing die thereof, a pipe expanding device for expanding an aluminum plate fin and a heat transfer tube, and a pipe expanding bur tube for a pipe expanding device, and the like. device. In particular, between the indoor heat exchanger and the outdoor heat exchanger, due to the shape of the fin (with or without slots and louvers) and the difference in the diameter of the heat transfer tube, it is necessary to prepare a press mold for various heat exchangers during manufacture. Expansion of burettes, etc., and the preparation of such equipment requires a large investment, and thus becomes a cause of hindering the change of the model such as changing the shape of the heat exchanger.

另一方面，用於冰箱等之熱交換器，已知大多為獨立散熱片形態之翅管式熱交換器(蛇管熱交換器)，係包含有平行配列之多片板狀散熱片及貫通該等散熱片之冷媒管，且該冷媒管相對空氣流動方向配置成鋸齒交錯狀，並且前述板狀散熱片相對前述冷媒管分割成各列及各段(參照專利文獻1,2)。依此種蛇管熱交換器，係將設有獨立散熱片群之冷媒管彎曲加工成鋸齒交錯狀以構成熱交換器，所以可提升生產性，並且藉獨立散熱片而獲得之前緣效果，可望提高熱交換性能。 On the other hand, a heat exchanger for a refrigerator or the like is known as a fin-and-tube heat exchanger (a coil heat exchanger) which is often in the form of an independent fin, and includes a plurality of plate fins arranged in parallel and penetrates the same. The refrigerant tubes of the heat sinks are arranged in a zigzag pattern with respect to the air flow direction, and the plate fins are divided into rows and segments with respect to the refrigerant tubes (see Patent Documents 1 and 2). According to the coil heat exchanger, the refrigerant tubes provided with the independent fin groups are bent into a zigzag pattern to form a heat exchanger, so that the productivity can be improved, and the leading edge effect can be obtained by the independent fins. Improve heat exchange performance.

因此，也有將此種蛇管熱交換器應用於空調機用熱交換器之提案檢討，不過實際上，空調機用熱交換器幾乎均使用前述十字散熱片管型熱交換器，迄今尚未採用蛇管熱交換器。其原因係考慮到相較於冰箱用熱交換器，空調機用熱交換器是在空氣流向構造較薄之熱交換器(2~3段)，所以構造成獨立散熱片而獲得之效果不佳。 Therefore, there is also a proposal to apply such a coil heat exchanger to a heat exchanger for an air conditioner. However, in practice, almost all of the heat exchangers for an air conditioner use the cross fin heat exchanger, and so far, no coil heat has been used. Switch. The reason for this is that the heat exchanger for an air conditioner is a heat exchanger having a relatively thin air flow structure (2 to 3 stages), so that it is poorly obtained by constructing an independent heat sink. .

又，此專利文獻1,2所載熱交換器係設計作為冰箱等冷卻系統用熱交換器，故為防止結霜造成之散熱片間阻塞，傳熱管間距和散熱片間隔(散熱片間距)設的較大，於是空氣側之傳熱面積就變小。另一方面，空調機用熱交換器，必須防止冷凝造成之散熱片間阻塞。由於此種狀況，所以欲將始於專利文獻1,2所載熱交換器之習知蛇管熱交換器直接應用作為空調機用熱交換器，實在大為困難。 Further, the heat exchangers disclosed in Patent Documents 1 and 2 are designed as heat exchangers for cooling systems such as refrigerators, so that heat sink gaps and fin spacing (heat sink spacing) are prevented from blocking due to frost formation. The setting is larger, and the heat transfer area on the air side becomes smaller. On the other hand, the heat exchanger for an air conditioner must prevent clogging between the fins caused by condensation. Due to such a situation, it is extremely difficult to directly apply the conventional coil heat exchanger starting from the heat exchangers disclosed in Patent Documents 1 and 2 as a heat exchanger for an air conditioner.

作為將散熱片與傳熱管接合之構造之翅管式熱交換器(蛇管熱交換器)，大多使用散熱片材質和傳熱管材質 為不同材質者來構成熱交換器，若此，恐有冷凝水等導致散熱片與傳熱管間產生電蝕且散熱片或傳熱管腐蝕之虞。因此，本申請案申請人在專利文獻3(日本專利公開公報2011-185589號)提出一種藉著於散熱片形成單層或多層塗膜以提高散熱片耐蝕性之空調機用蛇管熱交換器，不過該專利文獻所揭示之熱交換器，雖然散熱片耐蝕性良好，但傳熱管恐有腐蝕之虞，且用以於散熱片形成塗膜之塗裝成本讓熱交換器生產成本增加。 As a fin-and-tube heat exchanger (snake heat exchanger) having a structure in which a heat sink and a heat transfer tube are joined, a heat sink material and a heat transfer tube material are often used. If the heat exchanger is formed of a different material, there is a fear that condensed water or the like causes electric corrosion between the heat sink and the heat transfer tube, and the heat sink or the heat transfer tube is corroded. Therefore, the applicant of the present application has proposed a coil-type heat exchanger for an air conditioner which uses a heat sink to form a single layer or a plurality of coating films to improve the corrosion resistance of the heat sink, in the patent document 3 (Japanese Patent Laid-Open Publication No. 2011-185589). However, in the heat exchanger disclosed in the patent document, although the heat sink has good corrosion resistance, the heat transfer tube may be corroded, and the coating cost for forming the coating film on the heat sink increases the production cost of the heat exchanger.

先行技術文獻 Advanced technical literature 專利文獻 Patent literature

專利文獻1：日本新型實開平5-8265號公報 Patent Document 1: Japanese New Publication No. 5-8265

專利文獻2：日本專利特開2002-243382號公報 Patent Document 2: Japanese Patent Laid-Open Publication No. 2002-243382

專利文獻3：日本專利特開2011-185589號公報 Patent Document 3: Japanese Patent Laid-Open Publication No. 2011-185589

發明概要 Summary of invention

在此，本發明係有鑑於前述實情而完成者，欲解決之課題在於提供一種可有效防止冷凝造成之熱交換性低落，並且可充分因應空調機小型化之空調機用蛇管熱交換器。 Here, the present invention has been made in view of the above circumstances, and an object to be solved is to provide a coil heat exchanger for an air conditioner that can effectively prevent the heat exchange property due to condensation from being lowered and that can sufficiently reduce the size of the air conditioner.

本發明為解決如前述課題，要旨在於一種空調機用蛇管熱交換器，係在相對熱交換流體之流通方向(x向)為直角之方向(y向)，相互平行且相隔預定間隔配置之多片散 熱片形成之多數散熱片群，在相對該等x向及y向為直角之方向(z向)相距預定距離配置成列而構成多段散熱片群，並且以一片散熱片貫通有一根至二根金屬製傳熱管之形態，該金屬製傳熱管配置成蛇行形態，以依序貫通前述各段散熱片群之蛇管熱交換器，其特徵有：(1)構成前述散熱片群之各散熱片由具有同一形狀之金屬板形成，且相鄰散熱片配列相隔0.6~5.0mm之間隔，以及(2)前述多段散熱片群之相鄰之群在前述z向配設相隔2.0mm以下之距離。另，散熱片之形狀可適當採用矩形、圓形、多角形等形狀。 In order to solve the above problems, the present invention is directed to a coil heat exchanger for an air conditioner, which is disposed in a direction perpendicular to the flow direction (x direction) of the heat exchange fluid (y direction), parallel to each other, and arranged at a predetermined interval. Piece The plurality of fin groups formed by the heat sheets are arranged in a row at a predetermined distance from the x-direction and the y-direction at a right angle (z-direction) to form a plurality of fin groups, and one to two fins are penetrated by one fin. In the form of a metal heat transfer tube, the metal heat transfer tube is arranged in a meandering manner, and sequentially passes through the coil heat exchanger of each of the heat sink groups, and is characterized in that: (1) each heat sink constituting the heat sink group The sheet is formed by a metal plate having the same shape, and the adjacent fins are arranged at intervals of 0.6 to 5.0 mm, and (2) the adjacent groups of the plurality of fin groups are disposed at a distance of 2.0 mm or less apart from the z-direction. . Further, the shape of the heat sink may suitably be a shape such as a rectangle, a circle, or a polygon.

此外，依據前述本發明之空調機用蛇管熱交換器之一較佳態樣，係構造成前述傳熱管與構成前述散熱片群之各散熱片之間之自然孔蝕電位之差，為30mV以上。藉此，可有效減少散熱片與傳熱管之電蝕造成之傳熱管腐蝕。 Further, according to a preferred aspect of the present invention, the coil heat exchanger for an air conditioner is configured to have a difference of a natural pitting potential between the heat transfer tube and each of the fins constituting the fin group, which is 30 mV. the above. Thereby, the heat transfer tube corrosion caused by the electric corrosion of the heat sink and the heat transfer tube can be effectively reduced.

又，本發明空調機用蛇管熱交換器之一較佳態樣係前述金屬板由鋁或鋁合金構成，又另一較佳態樣係前述傳熱管由鋁或鋁合金構成。 Further, in a preferred embodiment of the coil heat exchanger for an air conditioner according to the present invention, the metal plate is made of aluminum or an aluminum alloy, and in another preferred embodiment, the heat transfer tube is made of aluminum or an aluminum alloy.

此外，依據前述本發明之空調機用蛇管熱交換器之另一較佳態樣，係前述傳熱管由鋁或鋁合金構成且其外表面被賦與鋅之犧牲陽極效果。 Further, according to another preferred aspect of the above-described coil heat exchanger for an air conditioner of the present invention, the heat transfer tube is made of aluminum or an aluminum alloy and the outer surface thereof is imparted with a sacrificial anode effect of zinc.

又，前述本發明再一較佳態樣，係前述傳熱管由鋁或鋁合金構成且於其外表面形成有具有犧牲陽極效果之金屬覆膜，並且該外表面之表面粗度：Ra於管軸方向為0.2~3.0μm。 Moreover, in a further preferred aspect of the present invention, the heat transfer tube is made of aluminum or an aluminum alloy and has a metal coating having a sacrificial anode effect on the outer surface thereof, and the surface roughness of the outer surface is Ra. The tube axis direction is 0.2 to 3.0 μm.

又，依據前述本發明之空調機用蛇管熱交換器之 另一較佳態樣，前述金屬板之材質係JIS(日本工業標準)A1050、JIS A1100、JIS A1200、JIS A7072及於JIS A1050、JIS A1100或JIS A1200含有0.1~0.5質量%之Mn及/或0.1~1.8質量%之Zn者中其中任一種形成之鋁或鋁合金，且前述傳熱管之材質係JIS A1050、JIS A1100、JIS A1200及JIS A3003中其中任一種形成之鋁或鋁合金。 Further, according to the foregoing invention, the coil heat exchanger for an air conditioner In another preferred embodiment, the material of the metal plate is JIS (Japanese Industrial Standard) A1050, JIS A1100, JIS A1200, JIS A7072, and JIS A1050, JIS A1100 or JIS A1200 contains 0.1 to 0.5% by mass of Mn and/or An aluminum or an aluminum alloy formed by any one of 0.1 to 1.8% by mass of Zn, and the material of the heat transfer tube is aluminum or an aluminum alloy formed by any one of JIS A1050, JIS A1100, JIS A1200, and JIS A3003.

又，依據前述本發明之空調機用蛇管熱交換器之另一較佳態樣，前述傳熱管由銅或銅合金構成，依又另一態樣，前述傳熱管之材質係JIS H3300 C1220或JIS H3300 C5010。 Further, according to another preferred aspect of the present invention, the heat transfer tube is made of copper or a copper alloy, and according to another aspect, the heat transfer tube is made of JIS H3300 C1220. Or JIS H3300 C5010.

此外，依據前述本發明之空調機用蛇管熱交換器，較有利的係於前述金屬製傳熱管之內面，具有與管軸方向平行之直槽、具有相對管軸之預定扭角之螺旋槽或於管軸方向交叉之槽構成之十字槽中其中任一種或二種以上。 Further, the coil heat exchanger for an air conditioner according to the present invention is advantageously attached to the inner surface of the metal heat transfer tube, and has a straight groove parallel to the tube axis direction and a spiral having a predetermined twist angle with respect to the tube axis. One or more of the grooves or the cross grooves formed by the grooves intersecting in the tube axis direction.

又，本發明之空調機用蛇管熱交換器之另一較佳態樣，係前述散熱片具有多數朝厚度方向突出且底部外形呈圓形或橢圓形之浮凸部。 Further, in another preferred aspect of the coil heat exchanger for an air conditioner according to the present invention, the fin has a plurality of embossing portions which protrude in the thickness direction and have a circular or elliptical bottom shape.

另外，較佳地，本發明於前述散熱片施與有槽縫加工或百葉窗加工，而依另一較佳態樣，前述散熱片之投影面積係前述傳熱管之外徑所決定之截面積之3~30倍。 In addition, preferably, the heat sink of the present invention is provided with slot processing or louver processing, and according to another preferred aspect, the projected area of the heat sink is the cross-sectional area determined by the outer diameter of the heat transfer tube. 3 to 30 times.

此外，依據本發明之空調機用蛇管熱交換器之另一較佳態樣，前述散熱片之投影面積係200~1000mm2。 Further, according to another preferred aspect of the coil heat exchanger for an air conditioner according to the present invention, the projection area of the heat sink is 200 to 1000 mm 2 .

此外，依據前述本發明之空調機用蛇管熱交換器之另一較佳態樣，前述金屬製傳熱管之外徑係3~13mm。 Further, according to another preferred aspect of the coil heat exchanger for an air conditioner according to the present invention, the outer diameter of the metal heat transfer tube is 3 to 13 mm.

又，本發明之空調機用蛇管熱交換器之另一有利態樣，係於前述金屬板之表面設有底處理層，且於該底處理層之上形成有單層或多層塗膜層，並且該塗膜層之中至少最外層為親水性樹脂或撥水性樹脂形成之塗膜層。 Moreover, another advantageous aspect of the coil heat exchanger for an air conditioner according to the present invention is that a bottom treatment layer is provided on the surface of the metal plate, and a single layer or a plurality of coating layers are formed on the bottom treatment layer. Further, at least the outermost layer of the coating layer is a coating layer formed of a hydrophilic resin or a water repellent resin.

此外，依據前述本發明之空調機用蛇管熱交換器之另一較佳態樣，前述親水性樹脂係選自於聚乙烯醇系樹脂；聚丙烯醯胺系樹脂；聚丙烯酸酯系樹脂；纖維素系樹脂；及聚乙二醇系樹脂所構成之群。 Further, according to another preferred aspect of the above-described coil heat exchanger for an air conditioner according to the present invention, the hydrophilic resin is selected from the group consisting of a polyvinyl alcohol resin, a polypropylene amide resin, a polyacrylate resin, and a fiber. A group of a resin and a polyethylene glycol resin.

再者，依據本發明之空調機用蛇管熱交換器之另一較佳態樣，前述撥水性樹脂係選自於環氧系樹脂；聚氨酯系樹脂；丙烯酸系樹脂；三聚氰胺系樹脂；氟系樹脂；矽氧系樹脂；及聚酯系樹脂所構成之群。 Furthermore, according to another preferred aspect of the coil heat exchanger for an air conditioner according to the present invention, the water repellent resin is selected from the group consisting of an epoxy resin; a polyurethane resin; an acrylic resin; a melamine resin; a fluorine resin. ; a group of oxime resin; and a polyester resin.

另外，本發明較有利的係於前述金屬製傳熱管之表面形成有樹脂製塗膜層。又，本發明又另一較佳態樣，係前述樹脂製塗膜層包含有熱傳導性填料。 Further, in the present invention, it is advantageous to form a resin coating film layer on the surface of the metal heat transfer tube. Moreover, in still another preferred aspect of the present invention, the resin coating film layer contains a thermally conductive filler.

本發明另一要旨在於提供一種空調機，係包含有具有如前述特徵構造之蛇管熱交換器；及使熱交換流體沿前述x向流通配列於前述z向之多段散熱片群之扇機構，且當若以位在前述扇機構所行之熱交換流體流通時風速大之第一區域之散熱片群或一部分之相鄰散熱片間之間隔為p1，以位在相對該第一區域之風速為0.7以下之風速之風速小之第二區域之散熱片群或一部分之相鄰散熱片間之間隔為p2時，該等散熱片群或一部分之散熱片之間隔定為可滿足以下公式： 1.5≦p2/p1≦3.0 Another object of the present invention is to provide an air conditioner comprising: a coil heat exchanger having the above-described characteristic configuration; and a fan mechanism for circulating a heat exchange fluid along the x-direction to the plurality of fin groups arranged in the z-direction, and When the distance between the heat sink group or a portion of the adjacent heat sink in the first region where the wind speed is large when the heat exchange fluid is flowing in the fan mechanism is at a distance of p 1 , the wind speed is relative to the first region. When the interval between the heat sink group of the second region having a small wind speed of 0.7 or less and the adjacent heat sink is p 2 , the interval between the heat sink groups or a part of the heat sink is set to satisfy the following formula: 1.5≦p 2 /p 1 ≦3.0

另，依據本發明之空調機之一較佳態樣，位在前述第一區域之散熱片群或其一部分，與位在前述第二區域之散熱片群或其一部分，在前述z向係位在不同之段。 Further, in a preferred aspect of the air conditioner according to the present invention, the heat sink group or a part thereof located in the first region, and the heat sink group or a part thereof located in the second region, in the z-direction system In different segments.

另，依據本發明之空調機之另一較佳態樣，位在前述第一區域之散熱片群或其一部分，與位在前述第二區域之散熱片群或其一部分，在前述z向係位在相同之段。 Further, according to another preferred aspect of the air conditioner of the present invention, the heat sink group located in the first region or a part thereof, and the heat sink group located in the second region or a part thereof, in the z-direction system In the same segment.

依前述，本發明之空調機用蛇管熱交換器，構成各散熱片群之散熱片形狀相同，且金屬製傳熱管上相鄰散熱片之間隔(散熱片間距)為0.6~5.0mm，並且散熱片群之相鄰之群，在z向，即在相對熱交換流體之流通方向為直角之方向之散熱片群配列方向，配設相隔2.0mm以下之距離，所以在散熱片表面等產生之冷凝水會有效且順暢地排出至散熱片群之外，並不會滯留在相鄰散熱片與散熱片之間或散熱片群與散熱片群之間，當本發明之空調機用蛇管熱交換器使用在空調機時，也可有效防止冷凝造成之熱交換性能低落。 According to the above, the coil heat exchanger for an air conditioner of the present invention has the same shape of the fins constituting each fin group, and the interval (heat sink spacing) of the adjacent fins on the metal heat transfer tube is 0.6 to 5.0 mm, and The group adjacent to the heat sink group is disposed in the z direction, that is, in the direction in which the heat sink group is arranged at a right angle to the flow direction of the heat exchange fluid, and is disposed at a distance of 2.0 mm or less. The condensed water is effectively and smoothly discharged out of the heat sink group, and does not stay between the adjacent heat sink and the heat sink or between the heat sink group and the heat sink group, when the air conditioner of the present invention uses the coil heat exchange When used in an air conditioner, it can also effectively prevent the heat exchange performance caused by condensation from degrading.

又，前述空調機用蛇管熱交換器，藉著構成散熱片群之多片散熱片貫通有一根至二根傳熱管而構成獨立散熱片群，可有效提高散熱片效率，且可阻斷相鄰傳熱管藉由散熱片之熱干擾(傳導)，於是便可提升熱交換性能，並有利於實現熱交換器之小型化。 Further, the coil heat exchanger for an air conditioner can form an independent fin group by passing through one or two heat transfer tubes through a plurality of fins constituting the fin group, thereby effectively improving the fin efficiency and blocking the phase. The adjacent heat transfer tube is thermally disturbed (conducted) by the heat sink, so that the heat exchange performance can be improved and the miniaturization of the heat exchanger can be facilitated.

此外，前述空調機用蛇管熱交換器，構造成前述 傳熱管與構成前述散熱片群之各散熱片之間之自然孔蝕電位之差為30mV以上，所以散熱片與傳熱管之間即使發生電蝕，也是散熱片先行腐蝕，於是便可有效減少或消除傳熱管腐蝕之虞。如此減少或消除傳熱管腐蝕，就能有效減少或消除流通於傳熱管內之冷媒自傳熱管外漏之問題。 Further, the aforementioned air-conditioning machine coil heat exchanger is constructed as described above The difference between the natural pitting potential between the heat transfer tube and the heat sinks constituting the heat sink group is 30 mV or more. Therefore, even if electric corrosion occurs between the heat sink and the heat transfer tube, the heat sink is first corroded, so that it can be effective. Reduce or eliminate the corrosion of heat transfer tubes. By reducing or eliminating the corrosion of the heat transfer tube, the problem of leakage of the refrigerant flowing through the heat transfer tube from the heat transfer tube can be effectively reduced or eliminated.

10,40,46,48‧‧‧熱交換器 10,40,46,48‧‧‧ heat exchanger

12,42,50‧‧‧散熱片 12,42,50‧‧‧ Heat sink

14,44‧‧‧散熱片群 14,44‧‧‧ Heat sink group

16‧‧‧金屬製傳熱管 16‧‧‧Metal heat transfer tube

18‧‧‧彎曲部 18‧‧‧Bend

20‧‧‧室外機 20‧‧‧Outdoor machine

22‧‧‧扇 22‧‧‧ fan

30‧‧‧金屬板 30‧‧‧Metal plates

32‧‧‧底處理層 32‧‧‧ bottom treatment layer

34,36‧‧‧塗膜層 34, 36‧ ‧ coating layer

52‧‧‧浮凸部 52‧‧‧ embossed

54,56,58‧‧‧多孔管 54,56,58‧‧‧Poly tube

55,57,59‧‧‧分隔板 55,57,59‧‧‧ partition board

A‧‧‧上段區域 A‧‧‧Upper area

B‧‧‧下段區域 B‧‧‧Next area

d‧‧‧熱片群間距離 d‧‧‧Hot film group distance

第1圖係顯示依據本發明之空調機用蛇管熱交換器之一例之立體說明圖。 Fig. 1 is a perspective explanatory view showing an example of a coil heat exchanger for an air conditioner according to the present invention.

第2圖係概略顯示將依據本發明之空調機用蛇管熱交換器應用於空調機室外機時之一例之截面說明圖。 Fig. 2 is a schematic cross-sectional view showing an example in which a coil heat exchanger for an air conditioner according to the present invention is applied to an outdoor unit of an air conditioner.

第3圖係概略顯示將依據本發明之空調機用蛇管熱交換器應用於空調機室外機時之另一例之截面說明圖。 Fig. 3 is a cross-sectional explanatory view showing another example of the case where the coil heat exchanger for an air conditioner according to the present invention is applied to an outdoor unit of an air conditioner.

第4圖係顯示構成依據本發明之空調機用蛇管熱交換器之散熱片表面所形成之塗膜層一例之截面說明圖。 Fig. 4 is a cross-sectional explanatory view showing an example of a coating layer formed on the surface of a fin of a coil heat exchanger for an air conditioner according to the present invention.

第5圖係顯示依據本發明之空調機用蛇管熱交換器之一其他不同例之立體說明圖。 Fig. 5 is a perspective explanatory view showing another different example of a coil heat exchanger for an air conditioner according to the present invention.

第6圖係顯示依據本發明之空調機用蛇管熱交換器之另一不同例之立體說明圖。 Fig. 6 is a perspective explanatory view showing another different example of the coil heat exchanger for an air conditioner according to the present invention.

第7圖係顯示依據本發明之空調機用蛇管熱交換器之再另一不同例之立體說明圖。 Fig. 7 is a perspective explanatory view showing still another different example of the coil heat exchanger for an air conditioner according to the present invention.

第8圖係顯示構成依據本發明之空調機用蛇管熱交換器之散熱片之他例之說明圖，(a)係一片散熱片整體之立體說明圖，(b)係放大顯示浮凸部截面之截面說明圖。 Fig. 8 is an explanatory view showing another example of a heat sink constituting a coil heat exchanger for an air conditioner according to the present invention, wherein (a) is a perspective view of a whole heat sink, and (b) shows an enlarged cross section of the embossed portion. A cross-sectional illustration.

第9圖係顯示構成依據本發明之空調機用蛇管熱交換 器之金屬製傳熱管之說明圖，(a)係顯示用於第1圖所示熱交換器之金屬製傳熱管之截面說明圖，(b),(c),(d)係分別顯示作為金屬製傳熱管用之其他不同例之截面說明圖。 Figure 9 is a view showing the heat exchange of the coils constituting the air conditioner according to the present invention. (a) is a cross-sectional explanatory view showing a metal heat transfer tube used in the heat exchanger shown in Fig. 1, and (b), (c), and (d) are respectively A cross-sectional explanatory view showing another different example of the heat transfer tube made of metal is shown.

用以實施發明之形態 Form for implementing the invention

以下配合參照圖式，詳細說明本發明實施形態以更具體揭示本發明。 The embodiments of the present invention will be described in detail below with reference to the accompanying drawings,

首先，第1圖以立體圖形態顯示依據本發明之空調機用蛇管熱交換器(以下亦會僅稱為蛇管熱交換器或熱交換器)之一實施形態。在此圖中，熱交換器構造成相互平行且相隔預定距離配置之呈矩形散熱片12多片形成之多數散熱片群14，分別相距預定距離且在上下方向相互平行配列，並且金屬製傳熱管16藉由彎曲部18配設成蛇行形態，即蛇管狀，以依序貫通前述多數散熱片群14。 First, Fig. 1 shows an embodiment of a coil heat exchanger for an air conditioner according to the present invention (hereinafter also referred to simply as a coil heat exchanger or a heat exchanger) in a perspective view. In this figure, the heat exchanger is configured such that a plurality of fin groups 14 formed by a plurality of rectangular fins 12 arranged parallel to each other and spaced apart by a predetermined distance are arranged at a predetermined distance apart from each other and arranged in parallel in the up and down direction, and heat transfer by metal The tube 16 is disposed in a serpentine form, that is, a serpentine shape, by the curved portion 18, and sequentially penetrates the plurality of fin groups 14 in order.

更詳而言之，散熱片12係由預定金屬材料形成之金屬板形成預定散熱片形狀(在此為矩形)之較薄略平坦板狀散熱片，於該散熱片12之矩形略中央部位，設有供金屬製傳熱管16插通之安裝孔，該安裝孔之周緣部分設有與散熱片12一體之預定高度之環圈部。另，形成該散熱片12之金屬板，如習知宜由鋁或鋁合金構成，此外，若考慮到傳熱性優異且能確保作為散熱片之強度，使用上較有利的除JIS A1050、JIS A1100、JIS A1200等材質以外，尚有於JIS A1050、JIS A1100或JIS A1200含有約0.1~0.5質量%比例之Mn及/或含有約0.1~1.8質量%之Zn之材質等。又，若優先 考慮作為散熱片之強度時，採用JIS A7072材質較有利。另，在此，「JIS A」之字母與四位數字之組合所表記之符號，係表示JIS規格所規定之鋁或鋁合金材質。 More specifically, the heat sink 12 is a thinner, slightly flat plate-shaped heat sink having a predetermined heat sink shape (here, a rectangular shape) formed of a metal plate formed of a predetermined metal material, in a slightly central portion of the heat sink 12, A mounting hole through which the metal heat transfer tube 16 is inserted is provided, and a peripheral portion of the mounting hole is provided with a loop portion of a predetermined height integral with the heat sink 12. Further, the metal plate forming the heat sink 12 is preferably made of aluminum or an aluminum alloy. Further, in consideration of excellent heat transfer properties and ensuring strength as a heat sink, it is advantageous to use JIS A1050, JIS. In addition to materials such as A1100 and JIS A1200, JIS A1050, JIS A1100, or JIS A1200 contains Mn in a ratio of about 0.1 to 0.5% by mass and/or a material containing Zn in an amount of about 0.1 to 1.8% by mass. Also, if priority When considering the strength of the heat sink, it is advantageous to use JIS A7072 material. Here, the symbol "JIS A" in combination with the four-digit number indicates the aluminum or aluminum alloy material specified in the JIS standard.

另，考慮到兼顧熱交換器之小型化與熱交換性能，散熱片12之投影面積宜係傳熱管(金屬製傳熱管16)之外徑所決定之截面積之3~30倍。所謂該傳熱管之外徑所決定之截面積，係表示由將金屬製傳熱管16擴管固接於散熱片12之安裝孔後之傳熱管外徑所求得之截面積，例如第1圖所示，在一片散熱片貫通有一根傳熱管之蛇管熱交換器，擴管後之金屬製傳熱管16之外徑若為6.5mm，其截面積為33.2mm2。然後，當散熱片之投影面積小於傳熱管外徑所決定之截面積之3倍時，對傳熱管而言散熱片過小，所以恐未能獲得充分熱交換性能，另一方面若大於此截面積之30倍，熱交換器變得大型化，就不實用。尤其係考慮到兼顧熱交換器之小型化與熱交換性能，散熱片之投影面積以200~1000mm2為佳。因為該散熱片投影面積若小於200mm2，恐未能獲得充分熱交換性能，另一方面若大於1000mm2，熱交換器變得大型化，就不實用。 Further, in consideration of the miniaturization and heat exchange performance of the heat exchanger, the projected area of the heat sink 12 is preferably 3 to 30 times the sectional area determined by the outer diameter of the heat transfer tube (the metal heat transfer tube 16). The cross-sectional area determined by the outer diameter of the heat transfer tube is the cross-sectional area obtained by expanding the outer diameter of the heat transfer tube after the metal heat transfer tube 16 is expanded and fixed to the mounting hole of the heat sink 12, for example. As shown in Fig. 1, a coil heat exchanger in which a heat transfer tube is passed through a heat sink, the outer diameter of the metal heat transfer tube 16 after expansion is 6.5 mm, and the cross-sectional area thereof is 33.2 mm 2 . Then, when the projected area of the heat sink is less than 3 times the cross-sectional area determined by the outer diameter of the heat transfer tube, the heat sink is too small for the heat transfer tube, so that sufficient heat exchange performance may not be obtained, and if not more than this, 30 times the cross-sectional area, the heat exchanger becomes large, and it is not practical. In particular, considering the miniaturization and heat exchange performance of the heat exchanger, the projected area of the heat sink is preferably 200 to 1000 mm 2 . Since the projection area of the fin is less than 200 mm 2 , sufficient heat exchange performance may not be obtained. On the other hand, if the heat exchanger is larger than 1000 mm 2 , the heat exchanger becomes large, which is not practical.

如第1圖所示，在相對熱交換流體之空氣之流通方向(第1圖中之x向)為垂直之方向(第1圖中之y向)，即板厚度方向與空氣流通方向垂直，前述多數散熱片12配置成相互平行且相鄰散熱片12,12相隔0.6~5.0mm之間隔(散熱片間距)，較佳為1.0~4.0mm之間隔，以形成散熱片群14。此外，前述多片散熱片12形成之多數散熱片群14，在相對該 等x向及y向為直角之方向(第1圖之z向)，各散熱片群14相距2.0mm以下，較佳為1.5mm以下之距離：d配置成列，構成整體呈平板狀。另，散熱片群14配列方向之z向，係熱交換器10配置成使用狀況之狀態時為垂直方向。 As shown in Fig. 1, the air flow direction (the x direction in Fig. 1) with respect to the heat exchange fluid is a vertical direction (y direction in Fig. 1), that is, the plate thickness direction is perpendicular to the air flow direction. The plurality of fins 12 are disposed in parallel with each other and the adjacent fins 12, 12 are spaced apart by a gap of 0.6 to 5.0 mm (the fin pitch), preferably at intervals of 1.0 to 4.0 mm, to form the fin group 14. In addition, the plurality of fin groups 14 formed by the plurality of fins 12 are opposite to each other. The x-direction and the y-direction are directions of a right angle (z direction in the first drawing), and the fin groups 14 are spaced apart from each other by 2.0 mm or less, preferably at a distance of 1.5 mm or less: d is arranged in a row, and the entire structure is flat. Further, the fin group 14 is arranged in the z direction of the direction, and the heat exchanger 10 is disposed in the vertical state in the state of use.

另一方面，金屬製傳熱管16係由如習知預定金屬材料形成之具有略圓形截面之管體。此外，構成此金屬製傳熱管16之金屬材料，可較佳地使用鋁或鋁合金，或者銅或銅合金。另，此金屬製傳熱管16與構成散熱片群14之各散熱片12之間之自然孔蝕電位之差，宜為30mV以上。又，所謂金屬製傳熱管16之自然孔蝕電位，係指構成此種傳熱管之素材自身之自然孔蝕電位，應解釋為未於表面形成塗膜層和進行表面改質者。又，散熱片12之自然孔蝕電位，亦是指構成散熱片12之素材自身之自然孔蝕電位。 On the other hand, the metal heat transfer tube 16 is a tube body having a slightly circular cross section formed of a predetermined predetermined metal material. Further, as the metal material constituting the metal heat transfer tube 16, aluminum or an aluminum alloy, or copper or a copper alloy can be preferably used. Further, the difference between the natural pitting potential between the metal heat transfer tube 16 and each of the fins 12 constituting the fin group 14 is preferably 30 mV or more. Further, the natural pitting potential of the metal heat transfer tube 16 refers to the natural pitting potential of the material constituting the heat transfer tube itself, and should be interpreted as a case where the coating layer is not formed on the surface and the surface is modified. Moreover, the natural pitting potential of the heat sink 12 also refers to the natural pitting potential of the material constituting the heat sink 12.

在此，若以鋁材料或鋁合金材料構成金屬製傳熱管16，考慮到製造性(擠製性)，較有利的是採用JIS A1050、JIS A1100、JIS A1200及JIS A3003中其中任一種形成之材質，不過為提高傳熱管耐蝕性，宜如以下進行。 Here, when the metal heat transfer tube 16 is made of an aluminum material or an aluminum alloy material, it is advantageous to use any one of JIS A1050, JIS A1100, JIS A1200, and JIS A3003 in consideration of manufacturability (extrusion property). The material, however, in order to improve the corrosion resistance of the heat transfer tube, it is preferable to proceed as follows.

即，如上述，以JIS A1050、JIS A1100、JIS A1200及JIS A3003中其中任一種形成之鋁或鋁合金構成金屬製傳熱管16，並於該傳熱管外表面形成鋅熔射、含鋅助熔劑(KZnF4)、鋅鍍敷等之犧牲陽極材層，以賦與鋅之犧牲陽極效果，藉此可提高傳熱管之耐蝕性。或者，以JIS A1050、JIS A1100、JIS A1200及JIS A3003中其中任一種材質構成金屬製傳熱管16，並以含有電化學性較該等鋁或鋁合金活潑 之含Zn之JIS A7072材質作為構成散熱片12之金屬板材質，藉此可提高傳熱管耐蝕性。 That is, as described above, the aluminum heat transfer tube 16 is formed of aluminum or aluminum alloy formed by any one of JIS A1050, JIS A1100, JIS A1200, and JIS A3003, and zinc-sprayed, zinc-containing is formed on the outer surface of the heat transfer tube. A sacrificial anode layer such as a flux (KZnF 4 ) or zinc plating is used to impart a sacrificial anode effect to zinc, whereby the corrosion resistance of the heat transfer tube can be improved. Alternatively, the metal heat transfer tube 16 is made of any one of JIS A1050, JIS A1100, JIS A1200, and JIS A3003, and is composed of a JIS A7072 material containing Zn containing electrochemically active aluminum or aluminum alloy. The metal plate material of the heat sink 12 can thereby improve the corrosion resistance of the heat transfer tube.

此外，當如前述於傳熱管外表面形成有具有犧牲陽極效果之金屬覆膜時，該外表面之表面粗度：Ra於管軸方向宜為0.2~3.0μm。若此表面粗度：Ra小於0.2μm，加工傳熱管之工具之表面精度管理就不易，所以會導致傳熱管製造成本變高之問題，又若Ra大於3.0μm，散熱片環圈部與傳熱管表面之間容易產生空隙，散熱片與傳熱管之間傳熱效率就低落，並且水分會進入此空隙成為傳熱管腐蝕之原因。 Further, when a metal film having a sacrificial anode effect is formed on the outer surface of the heat transfer tube as described above, the surface roughness of the outer surface: Ra is preferably 0.2 to 3.0 μm in the tube axis direction. If the surface roughness: Ra is less than 0.2 μm, the surface precision management of the tool for processing the heat transfer tube is not easy, so the manufacturing cost of the heat transfer tube becomes high, and if Ra is greater than 3.0 μm, the fin ring portion is A gap is easily formed between the surfaces of the heat transfer tubes, and the heat transfer efficiency between the fins and the heat transfer tubes is lowered, and moisture enters the gaps to cause corrosion of the heat transfer tubes.

又，亦可由於徑向上由內側芯材層與外側皮材層形成之雙層管壁構造之包覆管來構成前述傳熱管16。因此，可採用前述JIS A1050、JIS A1100、JIS A1200及JIS A3003等作為芯材層材質，且採用JIS A7072等作為皮材層材質，如此一併實現與前述相同之效果。另，作為外側皮材層之厚度之包覆率，採用管壁總厚度之3~20%之值。該包覆率若小於3%，皮材之犧牲陽極效果就小，且貫通孔易開而耐蝕性差，又，若包覆率大於20%，相對於管壁厚度之芯材層所佔比例就小，容易導致強度低落等問題。 Further, the heat transfer tube 16 may be configured by a cover tube having a double tube wall structure formed by an inner core material layer and an outer side skin layer in the radial direction. Therefore, JIS A1050, JIS A1100, JIS A1200, and JIS A3003 can be used as the material of the core material layer, and JIS A7072 or the like can be used as the material of the skin material layer, and the same effects as described above can be achieved. Further, as the coating ratio of the thickness of the outer skin layer, a value of 3 to 20% of the total thickness of the pipe wall is used. If the coating ratio is less than 3%, the effect of the sacrificial anode of the leather material is small, the through hole is easy to open and the corrosion resistance is poor, and if the coating ratio is more than 20%, the proportion of the core layer relative to the thickness of the tube wall is Small, easily lead to problems such as low strength.

另一方面，若由銅或銅合金構成前述金屬製傳熱管16，考慮到傳熱性，較有利的是採用JIS H3300 C1220或JIS H3300 C5010等材質。另，在此所用「JIS H3300」與「C+四位數字」組合之符號，亦係表示JIS規格所規定之銅或銅合金材質。 On the other hand, when the metal heat transfer tube 16 is made of copper or a copper alloy, it is advantageous to use a material such as JIS H3300 C1220 or JIS H3300 C5010 in consideration of heat transfer performance. In addition, the symbols used in combination of "JIS H3300" and "C+ four digits" as used herein also refer to copper or copper alloy materials specified in JIS specifications.

然後，前述預定金屬材料形成之金屬製傳熱管16其外徑可適當決定以兼顧對目標所在之蛇管熱交換器10之小型化要求與熱交換性能，不過以3~13mm為佳。這是因為外徑小於3mm之傳熱管，其管之製造甚為困難，又，外徑大於13mm之傳熱管，採用此種粗傳熱管之熱交換器就須大型化，甚不實用。 Then, the outer diameter of the metal heat transfer tube 16 formed of the predetermined metal material can be appropriately determined to achieve both the miniaturization requirement and the heat exchange performance of the coil heat exchanger 10 in which the target is located, but it is preferably 3 to 13 mm. This is because the heat transfer tube with an outer diameter of less than 3 mm is difficult to manufacture, and the heat transfer tube with an outer diameter of more than 13 mm requires a large heat exchanger of such a thick heat transfer tube, which is not practical. .

又，如前述之一根金屬製傳熱管16之直線部，依序貫通構成前述散熱片群14之多片散熱片12之形成在各略中央部位之安裝孔，且金屬製傳熱管16外周面與該等多數散熱片12之安裝孔周緣之環圈內周面密接而固定(結合)。另，如此散熱片12與金屬製傳熱管16之間之結合，可適當選用以往公知各種方法，不過較佳方法尤其係於散熱片12中央部位設置內徑較金屬製傳熱管16外徑僅稍大之附環圈安裝孔，再將金屬製傳熱管16插通此安裝孔內後，將擴管塞***金屬製傳熱管16內以擴大金屬製傳熱管16之外徑，藉此使金屬製傳熱管16外周面與設在散熱片12之安裝孔內周面(環圈內周面)密接。 Further, as described above, the straight portion of the one-piece metal heat transfer tube 16 sequentially passes through the mounting holes formed in the respective central portions of the plurality of fins 12 constituting the fin group 14, and the metal heat transfer tubes 16 The outer peripheral surface is in close contact with the inner circumferential surface of the ring around the mounting hole of the plurality of fins 12, and is fixed (bonded). Further, in the combination of the heat sink 12 and the metal heat transfer tube 16, various conventionally known methods can be appropriately selected, but the preferred method is particularly such that the inner diameter of the heat sink 12 is set to be larger than the outer diameter of the metal heat transfer tube 16. Only a slightly larger attachment ring mounting hole is inserted into the mounting hole, and the expansion plug is inserted into the metal heat transfer tube 16 to enlarge the outer diameter of the metal heat transfer tube 16. Thereby, the outer peripheral surface of the metal heat transfer tube 16 is in close contact with the inner peripheral surface (the inner circumferential surface of the ring) provided in the mounting hole of the heat sink 12.

如此一來，如第1圖所示，金屬製傳熱管16依序貫通配列在相對熱交換流體之空氣之流通方向(x向)及多片散熱片12配列方向(y向)為直角之方向(z向)之散熱片群14，且呈蛇行形態，換言之，配設成蛇管狀以構成整體呈略平板狀之空調機用蛇管熱交換器10。 As a result, as shown in Fig. 1, the metal heat transfer tubes 16 are arranged in a direction perpendicular to the flow direction of the air to the heat exchange fluid (x direction) and the arrangement direction of the plurality of fins 12 (y direction) at right angles. The fin group 14 in the direction (z direction) is in a serpentine form, in other words, is arranged in a serpentine shape to form a coiled-tube heat exchanger 10 for an air conditioner having a substantially flat shape as a whole.

欲將金屬製傳熱管16製成蛇行狀來形成目標所在之熱交換器10之形狀，可例示如以下方法。即，該方法 係首先於一根長直線狀金屬製傳熱管16，配設多數散熱片群14成分別相隔預定間隔。之後，將金屬製傳熱管16未配設有散熱片群14之處彎曲加工成U字形，藉此形成彎曲部18以形成蛇行狀，如此便形成第1圖所示之目標所在之熱交換器10之形狀。 The metal heat transfer tube 16 is formed into a serpentine shape to form the shape of the heat exchanger 10 in which the target is located, and the following method can be exemplified. That is, the method First, a plurality of fin-shaped heat transfer tubes 16 are disposed in a long linear metal heat transfer tube 16 at predetermined intervals. Thereafter, the metal heat transfer tube 16 is bent into a U-shape without providing the fin group 14, thereby forming the bent portion 18 to form a serpentine shape, thereby forming the heat exchange of the target shown in FIG. The shape of the device 10.

另，在此例示之呈略平板狀空調機用蛇管熱交換器10，可適當採用作為例如第2圖所示空調機之室外機用熱交換器。即，在此第2圖，概略顯示空調機之室外機20之截面圖形態，配置在室外機20內之空調機用蛇管熱交換器10，藉扇22使熱交換流體之空氣流通，並且使預定冷媒流通於金屬製傳熱管16內，如此在該等冷媒與空氣之間進行熱交換。 In addition, the coil heat exchanger 10 for a flat-panel type air conditioner, which is exemplified herein, can be suitably used as an outdoor unit heat exchanger such as the air conditioner shown in Fig. 2. In the second embodiment, the cross-sectional view of the outdoor unit 20 of the air conditioner is schematically shown, and the air-conditioning coil heat exchanger 10 disposed in the outdoor unit 20 is used to circulate the air of the heat exchange fluid by the fan 22, and The predetermined refrigerant flows through the metal heat transfer tubes 16, so that heat exchange is performed between the refrigerants and the air.

又，將此空調機用蛇管熱交換器10使用作為呈彎折形態整體變成L字形之熱交換器之例，顯示於第3圖。在該例中，使用兩個前述L字形熱交換器(10,10’)，且該等熱交換器10,10’組合配置成平面視時呈矩形，並且扇22配置於室外機20之上部以位於該矩形之上方。然後，藉該扇22之作動，熱交換流體之空氣如箭頭所示，在矩形筒體狀內流通於組合之兩個熱交換器10,10’，如此得在冷媒與空氣之間進行熱交換。 In addition, the air-conditioning machine coil heat exchanger 10 is used as an example of a heat exchanger having an L-shape as a whole in a bent shape, and is shown in FIG. In this example, two of the aforementioned L-shaped heat exchangers (10, 10') are used, and the heat exchangers 10, 10' are arranged in combination to have a rectangular shape in plan view, and the fan 22 is disposed on the upper portion of the outdoor unit 20. To be above the rectangle. Then, by the operation of the fan 22, the air of the heat exchange fluid flows through the combined heat exchangers 10, 10' in a rectangular cylindrical shape as indicated by the arrow, so that heat exchange between the refrigerant and the air is performed. .

因此，如前述，依據本發明構造之空調機用蛇管熱交換器10，散熱片12以相距0.6~5.0mm之間隔(散熱片間距)配設於金屬製傳熱管16上而構成散熱片群14，於是當用於空調機時，可有效減少冷凝造成之熱交換性能低落。即， 若散熱片間距小於0.6mm，即使於散熱片設有後述塗膜層，因冷凝產生之水(冷凝液)仍難以自散熱片表面落下，所以熱交換性能就會低落，並且該冷凝液因送風空氣而被推出，室內恐發生濺水狀況。另一方面，若散熱片間距大於5.0mm，由於散熱片間距過大，在相同尺寸之熱交換器，散熱片數量必然會減少，恐導致熱交換性能低落。 Therefore, as described above, according to the coil heat exchanger 10 for an air conditioner constructed in accordance with the present invention, the fins 12 are disposed on the metal heat transfer tubes 16 at intervals of 0.6 to 5.0 mm (the fin pitch) to constitute a fin group. 14, when used in an air conditioner, it can effectively reduce the heat exchange performance caused by condensation. which is, If the fin distance is less than 0.6 mm, even if the heat sink is provided with a coating layer described later, water (condensate) generated by condensation is hard to fall from the surface of the fin, so heat exchange performance is lowered, and the condensate is blown by air. When the air is pushed out, there is a possibility of splashing water in the room. On the other hand, if the fin pitch is larger than 5.0 mm, the number of fins is inevitably reduced in the heat exchanger of the same size due to the excessively large fin pitch, which may result in a low heat exchange performance.

此外，在此熱交換器10，於z向之垂直方向，多段散熱片群14之相鄰之群配設相隔2.0mm以下，較佳為1.5mm以下之距離(d)，藉此可使於散熱片12表面產生之冷凝液順暢朝下方流下而排出至外部，於是遂可有效發揮熱交換器10之熱交換性能。相對於此，在垂直方向相鄰之散熱片群14,14之間隔(d)若大於2,0mm，於散熱片12表面產生之冷凝液在自散熱片12表面流下時，恐將滯留於相鄰散熱片群14,14之間或散熱片12之端部，然後此滯留冷凝液就會導致如前述熱交換性能低落和濺水等問題。 Further, in the heat exchanger 10, in the vertical direction of the z direction, the adjacent groups of the plurality of fin groups 14 are disposed at a distance (d) of 2.0 mm or less, preferably 1.5 mm or less. The condensate generated on the surface of the fins 12 flows down smoothly and is discharged to the outside, so that the heat exchange performance of the heat exchanger 10 can be effectively exhibited. On the other hand, if the interval (d) of the fin groups 14 and 14 adjacent in the vertical direction is greater than 2,0 mm, the condensate generated on the surface of the fin 12 may stagnate in the phase when flowing down from the surface of the fin 12 Between the adjacent fin groups 14, 14 or the ends of the fins 12, the retention of the condensate may cause problems such as low heat exchange performance and splashing.

又，在此熱交換器10，係由獨立之散熱片群14構成熱交換器，所以相較於一片散熱片安裝有多數傳熱管而構成之翅管式熱交換器，可有效提高散熱片效率並且減少或阻斷相鄰傳熱管藉由散熱片之熱干擾(傳導)，故有利於提升熱交換性能。因此，亦可發揮實現熱交換器10小型化之優點。 Further, in the heat exchanger 10, since the heat exchanger 10 is composed of the independent fin groups 14, the fin-and-tube heat exchanger formed by attaching a plurality of heat transfer tubes to one fin can effectively improve the fins. Efficiency and reduce or block the adjacent heat transfer tubes by the thermal interference (conduction) of the heat sink, which is beneficial to improve the heat exchange performance. Therefore, the advantage of miniaturization of the heat exchanger 10 can also be exerted.

以上，詳述本發明熱交換器之一代表性實施形態，不過其僅作為例示，應知本發明並不可由前述實施形態之具體記述來作任何限定性解釋。 In the above, a representative embodiment of the heat exchanger of the present invention is described in detail. However, the present invention is not limited by the specific description of the above embodiments.

例如在前述實施形態中，散熱片12係由無塗裝金屬板形成預定散熱片形狀，不過亦可使用於金屬板表面形成有單層或多層塗膜層之預塗布金屬板來形成散熱片12。此時，塗膜層之至少最外層為親水性樹脂或撥水性樹脂形成之塗膜層。藉由形成有親水性樹脂或撥水性樹脂形成之塗膜層之預塗布金屬板來形成散熱片12，即使在空調機設定溫度與外界溫度之間之溫度差明顯且於散熱片12表面產生冷凝之狀況下，仍有利於維持熱交換器10之熱交換性能。 For example, in the above embodiment, the heat sink 12 is formed into a predetermined fin shape from a non-coated metal sheet, but a precoated metal sheet having a single layer or a plurality of coat layers formed on the surface of the metal sheet may be used to form the heat sink 12 . . At this time, at least the outermost layer of the coating layer is a coating layer formed of a hydrophilic resin or a water repellent resin. The heat sink 12 is formed by a precoated metal sheet formed with a coating layer formed of a hydrophilic resin or a water repellent resin, even if the temperature difference between the set temperature of the air conditioner and the outside temperature is significant and condensation occurs on the surface of the heat sink 12. In this case, it is still advantageous to maintain the heat exchange performance of the heat exchanger 10.

此外，在前述預塗布金屬板，若設有親水性樹脂形成之塗膜層作為最外層，於該最外層之表面，因冷凝而產生之水成為膜狀，所以可有效減少冷凝水造成之通風阻抗(空氣通過散熱片間時之阻抗)增加且維持穩定高熱交換性能。另一方面，若設有撥水性樹脂形成之塗膜層作為最外層，於該最外層之表面，因冷凝而產生之水可成為細微水滴並自散熱片表面順暢落下，有效排出至散熱片外，所以與設置親水性樹脂形成之塗膜層作為最外層時相同，可有效減少冷凝水造成之通風阻抗增加，且維持熱交換器10之熱交換性能。 Further, in the precoated metal sheet, if a coating layer formed of a hydrophilic resin is provided as an outermost layer, water generated by condensation on the surface of the outermost layer is formed into a film shape, so that ventilation due to condensed water can be effectively reduced. The impedance (the impedance of the air as it passes between the fins) increases and maintains a stable high heat exchange performance. On the other hand, if a coating layer formed of a water-repellent resin is provided as the outermost layer, water generated by condensation on the surface of the outermost layer can be finely dripped and smoothly fall from the surface of the fin, and can be efficiently discharged to the outside of the fin. Therefore, the same as when the coating layer formed of the hydrophilic resin is provided as the outermost layer, the increase in the ventilation resistance caused by the condensed water can be effectively reduced, and the heat exchange performance of the heat exchanger 10 can be maintained.

另，如此於散熱片12表面形成之至少最外層為親水性樹脂或撥水性樹脂形成之塗膜層，親水性樹脂可例舉如聚乙烯醇系樹脂(聚乙烯醇與其衍生物)；聚丙烯醯胺系樹脂(聚丙烯醯胺與其衍生物)；聚丙烯酸酯系樹脂(聚丙烯酸酯與其衍生物)；纖維素系樹脂(羧甲纖維素鈉、羧甲纖維素銨等)；聚乙二醇系樹脂(聚乙二醇、聚環氧乙烷等)等等。 又，撥水性樹脂可例舉如環氧系樹脂；聚氨酯系樹脂；丙烯酸系樹脂；三聚氰胺系樹脂；氟系樹脂；矽氧系樹脂；及聚酯系樹脂等等。 Further, at least the outermost layer formed on the surface of the heat sink 12 is a coating layer formed of a hydrophilic resin or a water repellent resin, and the hydrophilic resin may, for example, be a polyvinyl alcohol resin (polyvinyl alcohol and a derivative thereof); Amidoxime resin (polyacrylamide and its derivatives); polyacrylate resin (polyacrylate and its derivatives); cellulose resin (carboxymethylcellulose sodium, carboxymethylcellulose ammonium, etc.); An alcohol resin (polyethylene glycol, polyethylene oxide, etc.) or the like. Further, the water-repellent resin may, for example, be an epoxy resin; a polyurethane resin; an acrylic resin; a melamine resin; a fluorine resin; a silicone resin; and a polyester resin.

此外，當然可使用設有親水性樹脂或撥水性樹脂形成之單一塗膜層之預塗布金屬板作為散熱片12，不過較佳的可使用於作為基板之金屬板之表面，首先形成環氧系樹脂、胺甲酸乙酯系樹脂、聚酯系樹脂、氯化氯乙烯系樹脂等形成之耐蝕性塗膜層，再於其表面形成前述親水性樹脂等形成之塗膜層如此設有多層塗膜層之預塗布金屬板。如前述於作為基板之金屬板之表面設置耐蝕性塗膜層，可提高散熱片12之耐蝕性。另，如此形成於金屬板表面之各塗膜層之厚度，以每單層0.1~5.0μm為佳。這是由於若各塗膜層之厚度小於0.1μm時，恐不利於獲得各塗膜層之效果。另一方面，若設置厚度大於5.0μm之塗膜層，各塗膜層之效果就已呈飽和狀態，所以形成此種塗膜層僅不過徒然浪費成本。 Further, it is of course possible to use a precoated metal sheet provided with a single coating layer formed of a hydrophilic resin or a water repellent resin as the heat sink 12, but it is preferable to use the surface of the metal sheet as the substrate first to form an epoxy system. a corrosion-resistant coating film layer formed of a resin, a urethane resin, a polyester resin, a chlorinated vinyl chloride resin, or the like, and a coating film formed by forming the hydrophilic resin or the like on the surface thereof, and thus having a multilayer coating film A precoated metal sheet of the layer. When the corrosion-resistant coating film layer is provided on the surface of the metal plate as the substrate, the corrosion resistance of the heat sink 12 can be improved. Further, the thickness of each of the coating layers formed on the surface of the metal sheet is preferably 0.1 to 5.0 μm per one layer. This is because if the thickness of each coating layer is less than 0.1 μm, it is disadvantageous that the effect of obtaining each coating layer is disadvantageous. On the other hand, if a coating layer having a thickness of more than 5.0 μm is provided, the effect of each coating layer is saturated, so that the formation of such a coating layer is merely a waste of cost.

又，當於構成散板12之金屬板表面設置親水性樹脂和撥水性樹脂形成之塗膜層或耐蝕性塗膜層時，宜在金屬板30表面預先形成有底處理層32(參照第4圖)。設置此底處理層32，可提高金屬板與前述各塗膜層(34,36)之間之密接性。在此，底處理層32可例舉如藉使用磷鉻酸鹽、鉻酸鉻等之鉻酸鹽處理以及使用鉻化合物以外之磷酸鈦、磷酸鋯、磷酸鉬、磷酸鋅、氧化鈦或氧化鋯之非鉻酸鹽處理等之化學薄膜(化成處理)而獲得之薄膜層等。另，化學薄膜處 理方法有反應型及塗布型，本發明可採用其中任一種方法。 Further, when a coating layer or a corrosion-resistant coating layer formed of a hydrophilic resin and a water-repellent resin is provided on the surface of the metal plate constituting the dispersion plate 12, it is preferable to form the bottom treatment layer 32 on the surface of the metal plate 30 (see the fourth Figure). The bottom treatment layer 32 is provided to improve the adhesion between the metal sheet and each of the coating layers (34, 36). Here, the bottom treatment layer 32 may, for example, be treated with chromate such as phosphoric acid chromate or chromium chromate, and titanium phosphate, zirconium phosphate, molybdenum phosphate, zinc phosphate, titanium oxide or zirconium oxide other than a chromium compound. A thin film layer obtained by a chemical film (chemical conversion treatment) such as non-chromate treatment. In addition, the chemical film office The method is reactive and coated, and any of the methods can be used in the present invention.

此外，例示實施形態中，相鄰散熱片12,12之間隔(散熱片間距)全部設為等間隔，不過當然也以在一個熱交換器10內，依散熱片群14配設部位和散熱片群14中之散熱片12配設部位，在散熱片群14間或一個散熱片群14中構成不同散熱片間距。 Further, in the illustrated embodiment, the intervals (heatsink pitch) of the adjacent fins 12 and 12 are all equal intervals, but of course, the heat sink 10 is disposed in the heat exchanger group 10 and the heat sink is disposed. The fins 12 in the group 14 are disposed at different locations, and different fin spacings are formed between the fin groups 14 or one fin group 14.

具體而言，流通金屬製傳熱管16之冷媒，在金屬製傳熱管16之冷媒出入口附近之氣相區及液相區，相較於該金屬製傳熱管16之冷媒中間部之氣液二相區，由於冷煤自身熱交換性能低且顯然熱傳導率低，所以可縮小此部位之散熱片間距以擴大熱交換面積來提高熱交換效率。 Specifically, the refrigerant flowing through the metal heat transfer tube 16 is in the gas phase region and the liquid phase region near the refrigerant inlet and outlet of the metal heat transfer tube 16 as compared with the refrigerant intermediate portion of the metal heat transfer tube 16 In the liquid two-phase zone, since the cold coal itself has low heat exchange performance and apparently low thermal conductivity, the fin spacing of the portion can be reduced to expand the heat exchange area to improve heat exchange efficiency.

又，在第3圖所示空調機之室外機20，當藉扇22使空氣流通熱交換器10,10’時，位於最接近該扇22之區域之上段區域A之散熱片群14之散熱片12間流通之空氣流速，較最遠離該扇22之區域之下段區域B之散熱片群14之散熱片12間流通之空氣流速快。 Further, in the outdoor unit 20 of the air conditioner shown in Fig. 3, when the air is passed through the heat exchangers 10, 10' by the fan 22, the heat sink group 14 located in the upper region A of the region closest to the fan 22 is dissipated. The air flow rate between the sheets 12 is faster than the air flow rate between the fins 12 of the fin group 14 which is farthest from the area of the fan 22.

例如上段區域A之散熱片群14之散熱片12間流通之空氣流速：Va可為下段區域B之散熱片群14之散熱片12間流通之空氣流速：Vb之約1.5~2倍，此時，若將上段區域A之散熱片群14之相鄰散熱片12,12間間隔(散熱片間距：p1)縮小以提高熱交換性能，並且亦將下段區域B之散熱片群14之相鄰散熱片12,12間間隔(散熱片間距：p2)設成與前述散熱片間距：p1相同之散熱片間距，在下段區域B之散熱片群14，就會發生通風阻抗變得過大，整體熱交換性能低落之 問題。 For example, the air flow rate between the fins 12 of the fin group 14 in the upper section A: Va can be the air flow rate between the fins 12 of the fin group 14 in the lower section B: about 1.5 to 2 times the Vb. If the interval between the adjacent fins 12, 12 of the heat sink group 14 of the upper section A (the fin distance: p 1 ) is reduced to improve the heat exchange performance, and the heat sink group 14 of the lower section B is also adjacent to each other. The fins 12, 12 are spaced apart (the fin spacing: p 2 ), and the fin spacing is the same as the fin spacing: p 1 . In the fin region 14 of the lower region B, the ventilation resistance becomes too large. The problem of low overall heat exchange performance.

於是，為避免前述問題發生，宜相對接近扇22之上段區域A之散熱片群14之散熱片間距：p1，將位在離扇22較遠之下段區域B之散熱片群14之散熱片間距：p2以適當比例擴大。在此，在本發明，較有利的採用結構係考慮到該等區域A，B之熱交換流體之空氣流速(風速)，而規範位在扇22進行空氣流通時之風速大之上段區域A(第一區域)之散熱片群14之多數散熱片部位之散熱片間距：p1，與位在相對該上段區域A之風速為0.7以下風速之風速小下段區域B(第二區域)之散熱片群14之散熱片間距：p2之間關係，調整個別區域之散熱片群14之散熱片間距，俾該等間距之比：p2/p1為1.5以上3.0以下(1.5≦p2/p1≦3.0)，如此來控制通風阻抗，提高整體熱交換性能。 Therefore, in order to avoid the above problem, it is preferable to relatively close to the fin spacing of the fin group 14 of the upper region A of the fan 22: p 1 , and the fin of the fin group 14 located in the region B farther from the fan 22. Spacing: p 2 is expanded in an appropriate ratio. Here, in the present invention, it is advantageous to adopt the structure in consideration of the air flow rate (wind speed) of the heat exchange fluid of the regions A, B, and the gauge position is higher in the upper portion of the wind when the fan 22 performs air circulation. The fin spacing of the majority of the fin portions of the fin group 14 of the first region: p 1 , and the fins of the lower region B (second region) having a wind speed lower than the wind speed of 0.7 or less with respect to the upper region A The fin spacing of the group 14: the relationship between p 2 , the fin spacing of the fin group 14 of the individual regions is adjusted, and the ratio of the pitches is: p 2 /p 1 is 1.5 or more and 3.0 or less (1.5 ≦p 2 /p) 1 ≦ 3.0), thus controlling the ventilation resistance and improving the overall heat exchange performance.

另，該p2/p1之值若小於1.5，改變該兩散熱片間距之比率所獲效果就不充分，難以期待熱交換性能提高。又，該p2/p1之值若大於3.0，將各熱交換器10,10’位在上段區域A之散熱片群14之相鄰散熱片12,12間間隔：p1，設成散熱片間距適當範圍下限之0.6mm時，加熱器運轉時各散熱片12之冷凝水附著造成之通風阻抗增大會引起空氣側熱傳導率低落，進而空氣側熱傳導率低落便成為熱交換性能低落之原因。 Further, if the value of p 2 /p 1 is less than 1.5, the effect obtained by changing the ratio of the distance between the two fins is insufficient, and it is difficult to expect an improvement in heat exchange performance. Moreover, if the value of p 2 /p 1 is greater than 3.0, the heat exchangers 10, 10' are located in the heat sink 12 of the upper section A, and the spacing between the adjacent fins 12, 12 is: p 1 , which is set to dissipate heat. When the sheet spacing is 0.6 mm at the lower limit of the appropriate range, the increase in the ventilation resistance caused by the adhesion of the condensed water of each of the fins 12 during the operation of the heater causes the air side thermal conductivity to be lowered, and the air side thermal conductivity is lowered, which causes the heat exchange performance to be low.

又，在此，前述散熱片間距：p1，係設定作為位在最接近扇22之區域之上段區域A之至少一段散熱片群14之相鄰散熱片間間隔，一般而言，在此接近扇22之上段區 域A，包含有配列於z向之多段(n段)散熱片群14之中，位在接近扇22之n/4段數之散熱片群14。同樣地，散熱片間距：p2，係採用作為位在最遠離扇22之區域之下段區域B之至少一段散熱片群之相鄰散熱片間間隔，一般而言，可有利地應用在構成熱交換器10,10’之多段(n段)散熱片群14之中，位在最遠離扇22之區域之n/4段數之散熱片群14。再者，位在上段區域A與下段區域B之間中間區域之散熱片群14(n/2段)，該等散熱片群14之風速若為上段區域A之風速之0.7倍以下，可決定該散熱片間距(p2)以滿足前述p2/p1之不等式。另。該p1表示為位在上段區域A之至少一段散熱片群14之平均散熱片間距，此外，p2表示為位在下段區域B之至少一段散熱片群14之平均散熱片間距。 Further, here, the fin pitch: p 1 is set as the interval between adjacent fins of at least one fin group 14 positioned in the upper region A of the region closest to the fan 22, and is generally close thereto. The upper section A of the fan 22 includes a plurality of fins 14 arranged in the z-direction (n-segment) fin group 14 and located in the n/4 segment of the fan 22. Similarly, the fin spacing: p 2 is used as the spacing between adjacent fins of at least one length of the fin group located in the region B below the region furthest from the fan 22, and in general, can be advantageously applied to the constituent heat. Among the plurality of (n-segment) fin groups 14 of the exchangers 10, 10', the fin group 14 is located in the n/4 segment of the region farthest from the fan 22. Furthermore, the fin group 14 (n/2 segment) located in the intermediate portion between the upper region A and the lower segment B, and the wind speed of the fin group 14 is 0.7 times or less of the wind speed of the upper region A, and can be determined. The fin pitch (p 2 ) satisfies the aforementioned inequality of p 2 /p 1 . another. The p 1 is expressed as the average fin spacing of at least one length of the fin group 14 located in the upper region A, and further, p 2 is the average fin spacing of the at least one fin group 14 located in the lower region B.

此外，各熱交換器10,10’中，位在配列於z向之多段(n段)散熱片群之上段區域A與下段區域B間之中間區域之散熱片群14之空氣流速：Vc，具有Vb≦Vc≦Va之關係，所以此多段散熱片群14之中間區域之段(一般為n/2之段數)之散熱片群14之散熱片間距：p3，宜設定成p1≦p3≦p2。 Further, in each of the heat exchangers 10, 10', the air flow rate of the fin group 14 located in the middle portion between the segment area A and the lower section B of the plurality of (n-segment) fin groups in the z direction is Vc, With the relationship of Vb ≦ Vc ≦ Va, the fin spacing of the heat sink group 14 of the section of the intermediate section of the multi-stage heat sink group 14 (generally the number of segments of n/2): p 3 , should be set to p 1 ≦ p 3 ≦p 2 .

另，前述熱交換流體(空氣)之流速(風速)之變化，除產生於位在z向上不同段之散熱片群14,14間以外，亦產生於同一段散熱片群之不同散熱片配設部位，換言之，亦產生於配設在傳熱管16管軸方向之不同位置之一個散熱片群14之散熱片12間，所以前述散熱片間距p1,p2之關係在其中任一種情況時均適用。 In addition, the change in the flow rate (wind speed) of the heat exchange fluid (air) is generated in the heat sink group 14 and 14 which are located in different segments in the z direction, and is also generated in the same heat sink group of the same heat sink group. The portion, in other words, is also formed between the fins 12 of one fin group 14 disposed at different positions in the tube axis direction of the heat transfer tube 16, so that the relationship of the fin pitches p 1 , p 2 is in either case Both apply.

又，前述實施形態之熱交換器10構造成一片散熱 片12貫通有一根金屬製傳熱管16，不過如第5圖所示，一片散熱片42貫通有二根金屬製傳熱管16並形成各散熱片群44之構造之熱交換器40亦可。 Further, the heat exchanger 10 of the above embodiment is constructed as a heat sink The sheet 12 has a metal heat transfer tube 16 therethrough. However, as shown in FIG. 5, the heat exchanger 40 having the heat dissipation fins 42 penetrating through the two metal heat transfer tubes 16 and forming the heat sink group 44 may also be used. .

此外，熱交換器10亦可係相對熱交換流體(空氣)流通方向，將多數疊合之形狀如第6圖和第7圖所示，二個平板狀熱交換器10相距預定間隔疊合以構成一個空調機用蛇管熱交換器46,48。當如此將多數平板狀熱交換器10相對空氣流通方向疊合時，如第6圖所示熱交換器46，配置成相鄰熱交換器10之散熱片12成為格柵狀，換言之，於熱交換流體流通方向，前段熱交換器10之一個散熱片群14鄰接後段熱交換器10之一個散熱片群14，除此之外，亦可如第7圖所示熱交換器48，配置成前段熱交換器10之一個散熱片群14鄰接後段熱交換器10之二個散熱片群14，使相鄰熱交換器10之散熱片12成為千鳥格狀。然而，就熱交換性能而言，如第7圖所示疊合成千鳥格狀，較可期待良好熱交換效率。此外，當熱交換器10如此於熱交換流體之空氣之流通方向疊合多數時，亦可在不能期待高熱交換效率之部位將散熱片間距擴大以減少通風阻抗。如此減少通風阻抗，熱交換流體之空氣之流動就變良好，且配置在相對空氣流通方向為後側之熱交換器10亦有充分空氣流動，所以可提高熱交換器整體之熱交換效率。 In addition, the heat exchanger 10 may also be in a direction of flow of the heat exchange fluid (air), and the plurality of stacked shapes are superimposed at predetermined intervals as shown in FIGS. 6 and 7. A coil heat exchanger 46, 48 for air conditioners is constructed. When the plurality of flat heat exchangers 10 are superimposed in the air flow direction as described above, the heat exchangers 46 as shown in Fig. 6 are arranged such that the fins 12 of the adjacent heat exchangers 10 are in the form of a grid, in other words, in the heat. In the exchange fluid flow direction, one fin group 14 of the front stage heat exchanger 10 is adjacent to one fin group 14 of the rear stage heat exchanger 10. Alternatively, the heat exchanger 48 may be arranged as the front stage as shown in FIG. One fin group 14 of the heat exchanger 10 is adjacent to the two fin groups 14 of the rear stage heat exchanger 10, so that the fins 12 of the adjacent heat exchangers 10 are in a thousand bird shape. However, in terms of heat exchange performance, as shown in Fig. 7, it is superimposed into a houndstooth shape, and a good heat exchange efficiency can be expected. Further, when the heat exchanger 10 is superposed in a plurality of directions in the flow direction of the air of the heat exchange fluid, the fin pitch can be enlarged at a portion where high heat exchange efficiency cannot be expected to reduce the ventilation resistance. By reducing the ventilation resistance in this way, the flow of the air of the heat exchange fluid becomes good, and the heat exchanger 10 disposed on the rear side with respect to the air flow direction also has a sufficient air flow, so that the heat exchange efficiency of the entire heat exchanger can be improved.

另，構成此熱交換器10(40,46,48)之散熱片，除例示呈略平坦狀矩形之散熱片12(42)以外，亦可適當使用如第8圖所示於散熱片表面，具有多數朝散熱片厚度方向突出 且底部外形呈圓形或橢圓形之浮凸部52之散熱片50。如此於散熱片表面形成浮凸部52，通過積層之散熱片50間之熱交換用空氣在接觸浮凸部52後，就轉換朝向散熱片50之積層方向(縱向)和沿該積層方向直行之方向(橫向)，如此就變成適度之縱向渦流(以下稱為縱窩)及橫向渦流(以下稱為橫窩)。此適度渦流，可適度攪亂散熱片間之空氣，因此可提高熱交換性能。又，當使用翅管式熱交換器(蛇管熱交換器)作為寒冷地之室外機之低溫環境下之蒸發器時，此種適度渦流，尤其是縱窩，可減少較低溫空氣滯留於散熱片表面，且使易滯留於散熱片間之中央部位之較高溫空氣接觸散熱片表面，於是便可有效減少散熱片表面之結霜或結霜之霜增加。 Further, the heat sink constituting the heat exchanger 10 (40, 46, 48) may be suitably used as shown in Fig. 8 on the surface of the heat sink, except for the heat sink 12 (42) having a substantially flat rectangular shape. Has a majority protruding toward the thickness of the heat sink And the heat sink 50 of the embossing portion 52 having a circular or elliptical shape in the bottom shape. Thus, the embossed portion 52 is formed on the surface of the heat sink, and the air for heat exchange between the laminated heat sinks 50 is switched toward the lamination direction (longitudinal direction) of the heat sink 50 and straight in the direction of the lamination after contacting the embossed portion 52. The direction (lateral direction) thus becomes a moderate longitudinal eddy current (hereinafter referred to as a vertical pocket) and a lateral eddy current (hereinafter referred to as a transverse pocket). This moderate eddy current can moderately disturb the air between the fins, thereby improving heat exchange performance. Moreover, when a fin-and-tube heat exchanger (snake heat exchanger) is used as the evaporator in a low-temperature environment of a cold outdoor unit, such moderate eddy current, especially the vertical nest, can reduce the lower temperature air remaining in the heat sink. The surface and the higher temperature air which is easily retained in the central portion between the fins contact the surface of the fin, thereby effectively reducing the frosting or frosting of the fin surface.

因前述浮凸部52存在而獲得之熱交換性能提高，亦可藉由槽縫加工和百葉窗加工形成之剪切槽縫和百葉窗槽縫來同樣地實現。因此，此種槽縫加工和百葉窗加工與用以形成浮凸部52之浮凸加工一齊或取代浮凸加工，依據已知方法於散熱片(12,42)施行。 The heat exchange performance obtained by the presence of the embossed portion 52 is improved, and can also be realized by the slit slit and the louver slit formed by the slit processing and the louver processing. Therefore, such slot processing and louver processing are performed in conjunction with or instead of embossing for forming the embossed portion 52, and are applied to the heat sink (12, 42) in accordance with a known method.

又，金屬製傳熱管16之管徑，可因應流通管內之冷媒之流動特性，依熱交換器10之部位，使用不同外徑。例如，在液相區就設成較小外徑之傳熱管，並且在氣相區就使用較大外徑之傳熱管，如此有利於提高管內熱傳導率和減少壓力損失。另，如此依熱交換器部位來採用不同管徑之金屬製傳熱管時，除使用一根管徑於管軸方向預定部位適當改變之長金屬製傳熱管之外，亦可例如使用按每一 散熱片群14適當選擇管徑之金屬製傳熱管，且藉U形彎管等連接該等金屬製傳熱管以製成呈蛇行狀之金屬製傳熱管。 Further, the diameter of the metal heat transfer tube 16 can be different depending on the flow characteristics of the refrigerant in the flow tube depending on the portion of the heat exchanger 10. For example, a heat transfer tube having a smaller outer diameter is provided in the liquid phase region, and a heat transfer tube having a larger outer diameter is used in the gas phase region, which is advantageous in improving the heat conductivity in the tube and reducing the pressure loss. In addition, when a heat transfer tube made of a metal having a different diameter is used depending on the heat exchanger portion, a long metal heat transfer tube whose diameter is appropriately changed at a predetermined portion in the tube axis direction may be used, for example, Each The fin group 14 is appropriately selected from a metal heat transfer tube having a pipe diameter, and the metal heat transfer tubes are connected by a U-bend or the like to form a serpentine metal heat transfer tube.

此外，在先前例示之實施形態中，金屬製傳熱管16，係使用內面平滑之管體(參照第9(a)圖)，不過亦可採用於傳熱管之內面形成有與長向平行之直槽、具有相對管軸之預定扭角之螺旋槽或具有槽以預定角度交叉之槽形態之十字槽此些所謂附內面槽傳熱管。如此一來，使傳熱管內面之傳熱面積增大，且更使流通傳熱管中之冷媒流動複雜化，遂可進一步提高熱交換器10之熱交換性能。另，如此採用附內面槽傳熱管之蛇管熱交換器10，可係其整體採用相同槽形態之附內面槽傳熱管，不過除此之外，例如亦可係按構成散熱片群14之每一道次，製成槽形狀不同之形態之附內面槽傳熱管。另，如此形成於傳熱管內面之槽，其槽深度以0.05~1.0mm為佳，槽條數量在相對傳熱管長向之直角截面設置15~150條，藉此可有效提高熱交換性能。 Further, in the previously exemplified embodiment, the metal heat transfer tube 16 is a tube having a smooth inner surface (see Fig. 9(a)), but may be formed on the inner surface of the heat transfer tube. A so-called inner grooved heat transfer tube that is parallel to a straight groove, a spiral groove having a predetermined twist angle with respect to the pipe axis, or a groove having a groove shape in which the groove intersects at a predetermined angle. As a result, the heat transfer area of the inner surface of the heat transfer tube is increased, and the flow of the refrigerant in the heat transfer tube is further complicated, so that the heat exchange performance of the heat exchanger 10 can be further improved. In addition, the coil heat exchanger 10 with the inner groove heat transfer tube may be used as the inner groove heat transfer tube of the same groove shape as a whole, but in addition, for example, the heat sink group may be configured. For each of the 14 passes, an inner groove heat transfer tube having a different groove shape is formed. In addition, the groove formed on the inner surface of the heat transfer tube has a groove depth of 0.05 to 1.0 mm, and the number of the groove is 15 to 150 at a right angle to the longitudinal direction of the heat transfer tube, thereby effectively improving heat exchange performance. .

此外，本發明所用金屬製傳熱管16，可係外面呈略圓形者，除例如第9(b)、(c)、(d)圖所示截面由一片分隔板55、二片平行之分隔板57,57、二片交叉之分隔板59,59所分隔之多孔管54,56,58之外，亦可適當採用公知各種多孔管。 Further, the metal heat transfer tube 16 used in the present invention may have a slightly rounded outer surface, except for, for example, the cross section shown in Figures 9(b), (c), and (d) is divided by a partition plate 55 and two parallel plates. In addition to the porous tubes 54, 56, 58 separated by the partition plates 57, 57 and the two intersecting partition plates 59, 59, various known porous tubes can be suitably used.

另外，構成蛇管熱交換器10之金屬製傳熱管16，可適當使用於表面形成有樹脂製塗膜層者。前述蛇管熱交換器10，係藉機械擴管法等方法使金屬製傳熱管16與散熱片12密接而組裝來安裝，若微觀該等散熱片與傳熱管之接 觸部分，金屬製傳熱管16與各散熱片12之間是存在些許空隙。然而，若有此種空隙存在，散熱片與傳熱管之間之接觸熱阻抗就增大，恐導致熱交換性能低落。在此，為減少散熱片與傳熱管之間之接觸熱阻抗以有效發揮熱交換器性能，金屬製傳熱管16與散熱片12之間之空隙不宜存在，因此在金屬製傳熱管16之表面形成前述樹脂製塗膜層，藉此有利於減少前述空隙產生。 Further, the metal heat transfer tube 16 constituting the coil heat exchanger 10 can be suitably used in a case where a resin coating layer is formed on the surface. In the coil heat exchanger 10, the metal heat transfer tube 16 and the heat sink 12 are closely attached to each other by means of a mechanical expansion method, and assembled, and if the heat sink is connected to the heat transfer tube. The contact portion has a slight gap between the metal heat transfer tube 16 and each of the fins 12. However, if such a void exists, the thermal impedance of contact between the heat sink and the heat transfer tube increases, which may result in a low heat exchange performance. Here, in order to reduce the contact thermal impedance between the heat sink and the heat transfer tube to effectively exhibit the heat exchanger performance, the gap between the metal heat transfer tube 16 and the heat sink 12 is not suitable, so the metal heat transfer tube 16 The surface of the resin coating layer is formed on the surface, thereby facilitating the reduction of the aforementioned void generation.

此外，構成前述樹脂製塗膜層之樹脂，除聚乙烯樹脂等熱塑性樹脂之外，可舉如與前述形成於散熱片12表面者相同之親水性樹脂及撥水性樹脂，以及環氧系樹脂、胺甲酸乙酯系樹脂、聚酯系樹脂、氯化氯乙烯系樹脂等。於金屬製傳熱管16表面形成該等各種樹脂形成之塗膜層，可獲得如下效果。即，關於聚乙烯樹脂等熱塑性樹脂，將設有附環圈之孔之散熱片12，組裝於最外層具有聚乙烯樹脂等熱塑性樹脂形成之塗膜層之金屬製傳熱管16後，加熱到聚乙烯樹脂等熱塑性樹脂熔點以上，然後當冷卻時，形成在附環圈孔周緣之環圈之邊緣部分與金屬製傳熱管之間間隙，可藉聚乙烯樹脂等熱塑性樹脂有利地填塞，而確保散熱片12與金屬製傳熱管16之間之接觸面積更大，所以更能提高熱交換器之熱交換性能。又，於金屬製傳熱管16形成親水性樹脂或撥水性樹脂形成之塗膜層作為最外層，可使金屬製傳熱管16之露出部(未組裝有散熱片之部分)具有與散熱片12相同之功能。此外，於金屬製傳熱管16之表面，設置環氧系樹脂、胺甲酸乙酯系樹脂、聚酯系樹脂、氯化 氯乙烯系樹脂形成之塗膜層，可提高金屬製傳熱管16之耐蝕性。 In addition, the resin constituting the resin coating film layer may be a hydrophilic resin such as a polyethylene resin or the like, and a water-repellent resin and a water-repellent resin, and an epoxy resin, which are the same as those of the surface of the heat sink 12 described above. An urethane resin, a polyester resin, a chlorinated vinyl chloride resin, or the like. By forming a coating layer formed of these various resins on the surface of the metal heat transfer tube 16, the following effects can be obtained. In other words, the thermoplastic resin such as a polyethylene resin is provided with a heat-dissipating fin 12 provided with a hole of a loop, and is assembled to a metal heat-transfer tube 16 having a coating layer formed of a thermoplastic resin such as a polyethylene resin on the outermost layer, and then heated to When the thermoplastic resin such as a polyethylene resin has a melting point or more, and then, when cooled, a gap formed between the edge portion of the ring around the circumference of the ring ring hole and the metal heat transfer tube can be advantageously filled with a thermoplastic resin such as a polyethylene resin. It is ensured that the contact area between the heat sink 12 and the metal heat transfer tube 16 is larger, so that the heat exchange performance of the heat exchanger can be further improved. Further, the metal heat transfer tube 16 is formed by forming a coating layer of a hydrophilic resin or a water repellent resin as an outermost layer, and the exposed portion of the metal heat transfer tube 16 (the portion where the heat sink is not assembled) has a heat sink. 12 same features. Further, an epoxy resin, a urethane resin, a polyester resin, and a chlorination are provided on the surface of the metal heat transfer tube 16. The coating layer formed of the vinyl chloride resin can improve the corrosion resistance of the metal heat transfer tube 16.

又，考慮到提高熱傳導性，前述樹脂製塗膜層宜包含有熱傳導性填料。該熱傳導性填料，可例舉如氮化硼、氮化鋁、氮化矽、碳化矽、氧化鋁、氧化鋯、氧化鈦、碳之細微粉末等。 Further, in view of improving thermal conductivity, the resin coating film layer preferably contains a thermally conductive filler. The heat conductive filler may, for example, be boron nitride, aluminum nitride, tantalum nitride, tantalum carbide, aluminum oxide, zirconium oxide, titanium oxide or fine powder of carbon.

另，本發明係可採用於金屬製傳熱管16表面設有如前述各種樹脂形成之單一塗膜層之構造，不過較佳地係採用於金屬製傳熱管16表面，首先形成環氧系樹脂、胺甲酸乙酯系樹脂、聚酯系樹脂、氯化氯乙烯系樹脂等形成之耐蝕性塗膜層，再於其上形成聚乙烯樹脂等熱塑性樹脂、親水性樹脂或撥水性樹脂形成之樹脂製塗膜層。又，樹脂製塗膜層之厚度，以每單層0.1~5.0μm為佳。這是由於若樹脂製塗膜層之厚度小於0.1μm時，恐不利於獲得前述各樹脂製塗膜層之效果，另一方面，若設置厚度大於5.0μm之樹脂製塗膜層，各塗膜層之效果就已呈飽和狀態，僅不過徒然浪費成本。 Further, the present invention can be applied to a structure in which a metal coating tube 16 is provided with a single coating layer formed of various resins as described above, but is preferably applied to the surface of the metal heat transfer tube 16 to form an epoxy resin first. a corrosion-resistant coating film layer formed of a urethane resin, a polyester resin, or a chlorinated vinyl chloride resin, and a resin formed of a thermoplastic resin such as a polyethylene resin or a hydrophilic resin or a water-repellent resin. Coating film layer. Further, the thickness of the resin coating layer is preferably 0.1 to 5.0 μm per one layer. This is because if the thickness of the resin coating layer is less than 0.1 μm, the effect of obtaining each of the resin coating layers may be disadvantageous. On the other hand, if a resin coating layer having a thickness of more than 5.0 μm is provided, each coating film The effect of the layer is saturated, but it is a waste of cost.

又，於金屬製傳熱管16表面設置前述樹脂形成之樹脂製塗膜層時，宜在金屬製傳熱管16表面預先形成有底處理層。設置此底處理層，可提高金屬製傳熱管16與前述各塗膜層之間之密接性。在此，底處理層可例舉如藉使用磷鉻酸鹽、鉻酸鉻等之鉻酸鹽處理以及使用鉻化合物以外之磷酸鈦、磷酸鋯、磷酸鉬、磷酸鋅、氧化鈦或氧化鋯之非鉻酸鹽處理等之化學薄膜(化成處理)而獲得之薄膜層 等。另，化學薄膜處理方法有反應型及塗布型，本發明可採用其中任一種方法。 Moreover, when the resin coating film layer formed of the resin is provided on the surface of the metal heat transfer tube 16, it is preferable to form a bottom treatment layer on the surface of the metal heat transfer tube 16 in advance. By providing the undercoat layer, the adhesion between the metal heat transfer tube 16 and each of the above-mentioned coating layers can be improved. Here, the undertreatment layer may, for example, be a chromate treatment using a phosphorous chromate or a chromium chromate or a titanium phosphate, zirconium phosphate, molybdenum phosphate, zinc phosphate, titanium oxide or zirconium oxide other than a chromium compound. Thin film layer obtained by chemical film (chemical treatment) such as non-chromate treatment Wait. Further, the chemical film processing method has a reactive type and a coating type, and any of the methods can be employed in the present invention.

其他不一一列舉，不過本發明係依所屬技術領域中具有通常知識者之知識，便可在添加各種變更、修正、改良之態樣中實施，當然，該實施態樣只要未脫離本發明主旨，就均屬於本發明範圍內。 Others may be enumerated, but the present invention may be implemented in various modifications, corrections, and improvements depending on the knowledge of those having ordinary skill in the art, and of course, the embodiment does not depart from the gist of the present invention. All are within the scope of the invention.

實施例 Example

以下，揭示本發明代表性實施例，可使本發明更具體且清楚，不過當然本發明並不因此些實施例之記載而受到任何限制。 In the following, the present invention will be more specifically and clearly described, and the present invention is not limited by the description of the embodiments.

-實施例1- - Example 1

首先，擠製加工鋁合金(JIS A3003)，形成截面外周形狀呈圓形且外徑8.0mm，而且管內面形成有預定之槽之各種附內面槽傳熱管，作為用以構成依據本發明之空調機用蛇管熱交換器之傳熱管。即，形成3種附內面槽傳熱管：管外徑：8.0mm，管壁壁厚：0.65mm，形成於相鄰槽間之內面散熱片之散熱片高度：0.65mm，槽條數量：30條，導角：0°之管內面形成有直槽之附內面槽傳熱管；管外徑：8.0mm，壁厚：0.42mm，散熱片高度：0.28mm，槽條數量：50條，導角：34°之管內面形成有螺旋槽之附內面槽傳熱管；及管外徑：8.0mm，壁厚：0.42mm，一次槽間之散熱片高度：0.28mm，二次槽間之散熱片高度：0.10mm，一次槽及二次槽條數量：各50條，一次槽之導角：34°，二次槽之導角：10°之管內面形成有十字槽之附內面槽傳熱管。 另，此種附內面槽管之製造方法，可適當選擇公知各種方法來使用，例如可適當採用日本專利特開平8-49992號公報和日本專利特開2004-301495號公報所揭示之方法。 First, an extruded aluminum alloy (JIS A3003) is formed, and various inner-side groove heat transfer tubes having a circular outer shape and an outer diameter of 8.0 mm and having a predetermined groove formed on the inner surface of the tube are formed as a basis for The invention discloses a heat transfer tube for a coil heat exchanger for an air conditioner. That is, three types of inner surface groove heat transfer tubes are formed: tube outer diameter: 8.0 mm, tube wall thickness: 0.65 mm, heat sink height of inner fin formed between adjacent grooves: 0.65 mm, number of slots : 30 strips, lead angle: 0° inside the tube is formed with a straight groove with an inner groove heat transfer tube; tube outer diameter: 8.0mm, wall thickness: 0.42mm, fin height: 0.28mm, number of slots: 50, lead angle: 34° inside the tube is formed with a spiral groove with an inner groove heat transfer tube; and the tube outer diameter: 8.0mm, wall thickness: 0.42mm, the heat sink height between the first groove: 0.28mm, The height of the fin between the secondary slots: 0.10mm, the number of primary slots and secondary slots: 50 each, the lead angle of the primary slot: 34°, the lead angle of the secondary slot: 10°, the inner surface of the tube is formed with a cross The inner groove of the groove is attached to the heat transfer tube. In addition, the method for producing the inner-side grooved tube can be appropriately selected and used in various ways. For example, the method disclosed in Japanese Laid-Open Patent Publication No. Hei 8-49992 and Japanese Patent Application Laid-Open No. Hei No. 2004-301495 can be suitably employed.

然後，準備3種對如此形成之各附內面槽傳熱管之外表面熔射鋅金屬粉後，藉熱處理在表層200μm範圍形成有鋅濃化層之長直線狀鋁合金製傳熱管(16)。即，分別由槽狀筆直之附內面槽傳熱管準備傳熱管A1，由槽狀為螺旋槽之附內面槽傳熱管準備傳熱管A2，然後由槽狀為十字槽之附內面槽傳熱管準備傳熱管A3。另，該等A1~A3傳熱管之外面表面粗度(Ra)，均為Ra：1.0μm。 Then, three kinds of long linear aluminum alloy heat transfer tubes formed by melting a zinc-rich metal powder on the outer surface of each of the inner surface groove heat transfer tubes thus formed, and having a zinc-concentrated layer in the surface layer of 200 μm are prepared ( 16). That is, the heat transfer tube A1 is prepared by the groove-shaped straight inner groove heat transfer tube, and the heat transfer tube A2 is prepared by the inner groove heat transfer tube with the groove shape as the spiral groove, and then the groove shape is attached to the cross groove. The inner groove heat transfer tube is prepared for the heat transfer tube A3. In addition, the surface roughness (Ra) of the outer surface of the A1 to A3 heat transfer tubes was Ra: 1.0 μm.

又，其他傳熱管，則係準備銅合金(磷脫氧銅：JIS H3300 C1220)形成之外徑8.0mm且於其內周面形成有螺旋槽之附內面槽傳熱管作為傳熱管A4。另，此傳熱管A4，係管外徑：8.0mm，壁厚：0.3mm，散熱片高度：0.12mm，槽條數量：80條，相對管軸之導角：43°，且外面表面粗度(Ra)為Ra：0.3μm。此外，準備二根與前述傳熱管A1~A3同樣地，擠製加工鋁合金以於內面形成預定直槽且外徑8.0mm之附內面槽傳熱管，並分別於其中一根外表面不形成鋅濃化層且使外面表面粗度(Ra)為Ra：0.3μm如此準備作為傳熱管A5，再於另一根外表面，在與前述傳熱管A1~A3同樣之表面層200μm範圍形成鋅濃化層且使外面表面粗度(Ra)為Ra：5.0μm作為傳熱管A6。另，該等傳熱管A5,A6之內面槽之形狀和尺寸等與傳熱管A1相同。 In addition, the other heat transfer tube is prepared by preparing a copper alloy (phosphorus deoxidized copper: JIS H3300 C1220) having an outer diameter of 8.0 mm and having an inner groove on the inner peripheral surface thereof as a heat transfer tube A4. . In addition, the heat transfer tube A4, the outer diameter of the tube: 8.0 mm, wall thickness: 0.3 mm, fin height: 0.12 mm, number of slots: 80, guide angle with respect to the tube axis: 43 °, and the outer surface is thick The degree (Ra) is Ra: 0.3 μm. In addition, in the same manner as the heat transfer tubes A1 to A3 described above, the aluminum alloy is extruded to form an inner surface groove heat transfer tube having a predetermined straight groove and an outer diameter of 8.0 mm on the inner surface, respectively. The zinc concentration layer is not formed on the surface, and the outer surface roughness (Ra) is Ra: 0.3 μm, so that it is prepared as the heat transfer tube A5, and on the other outer surface, on the same surface layer as the heat transfer tubes A1 to A3. The zinc-concentrated layer was formed in the range of 200 μm and the outer surface roughness (Ra) was Ra: 5.0 μm as the heat transfer tube A6. Further, the shape and size of the inner surface grooves of the heat transfer tubes A5, A6 are the same as those of the heat transfer tubes A1.

另一方面，準備3種散熱片材料，即，板厚：0.1mm 之鋁材質：JIS A1100之板材B1；板厚：0.1mm之鋁材質：JIS A 7072之板材B2，及於該板材B2表面形成有第4圖所示3層表面處理膜之板材B3。另，板材B3，係對前述板材B2施行磷鉻酸鹽浸漬處理而於板材B2表面形成磷鉻酸鹽形成之化成薄膜(32)後，再利用輥塗布機於此化成薄膜(32)上塗布環氧樹脂，並以220℃溫度加熱10秒，藉此形成膜厚1μm之耐蝕性塗膜(34)，然後空冷之後，於耐蝕性塗膜(34)上塗布聚乙烯醇樹脂(PVA樹脂)形成之親水性塗膜用塗料，並以220℃溫度加熱10秒，藉此形成膜厚1.5μm之親水性塗膜(36)之散熱片材料。分別將如此準備之3種散熱片材料裁斷成在第1圖之x向為12mm且在z向為16mm之尺寸之矩形，並於其略中央部設置用以供傳熱管插通之貫通孔(於周緣設有0.5mm之環圈之貫通孔)，如此來準備多片之3種散熱片(12)。 On the other hand, three kinds of fin materials are prepared, that is, the plate thickness: 0.1 mm Aluminum material: JIS A1100 sheet B1; sheet thickness: 0.1 mm aluminum material: JIS A 7072 sheet B2, and sheet B3 having a three-layer surface treatment film shown in Fig. 4 formed on the surface of the sheet B2. Further, the sheet material B3 is subjected to a phosphoric acid immersion treatment on the sheet material B2 to form a film (32) formed by forming a phosphorochromate on the surface of the sheet material B2, and then coated on the film (32) by a roll coater. The epoxy resin was heated at a temperature of 220 ° C for 10 seconds to form a corrosion-resistant coating film (34) having a film thickness of 1 μm, and then air-cooled, and then coated with a polyvinyl alcohol resin (PVA resin) on the corrosion-resistant coating film (34). The formed coating material for a hydrophilic coating film was heated at a temperature of 220 ° C for 10 seconds to form a heat sink material of a hydrophilic coating film (36) having a film thickness of 1.5 μm. The three kinds of fin materials thus prepared are cut into rectangles having a size of 12 mm in the x direction and 16 mm in the z direction, and a through hole for inserting the heat transfer tubes at a slight central portion thereof. (The through hole of a 0.5 mm ring is provided on the periphery), so that a plurality of three kinds of fins (12) are prepared.

然後，使用如此準備之各種傳熱管(16)與散熱片(12)，所謂外面散熱片，來於一根傳熱管(16)上如以下形成目標所在之散熱片群(14)。即，將多片散熱片配列成位處平行而各自貫通孔相距預定間隔，然後傳熱管依序貫通地插通貫通孔後，將傳熱管擴管，如此使傳熱管與散熱片變成一體以於該傳熱管上形成散熱片群。此時，擴管後之傳熱管管徑(D)為8.75mm，且對一片散熱片，一根傳熱管成為貫通其略中央之形態。又，於傳熱管之直管部，散熱片間隔(散熱片間距)設為1.0mm。另，在此，準備300片散熱片，將其區分成各60片之群，在各散熱片群，散熱片平行配列以接 合，如此於一根傳熱管，相距預定間隔形成全部均同寬之五個散熱片群。 Then, using the heat transfer tubes (16) and the heat sinks (12) thus prepared, so-called outer fins, a heat sink tube (16) is formed on a heat transfer tube (16) as follows. That is, a plurality of fins are arranged in parallel at positions, and the through holes are spaced apart by a predetermined interval, and then the heat transfer tubes are inserted through the through holes in sequence, and then the heat transfer tubes are expanded, so that the heat transfer tubes and the heat sinks become The integrated body forms a heat sink group on the heat transfer tube. At this time, the tube diameter (D) of the heat transfer tube after the pipe expansion was 8.75 mm, and a heat transfer tube was formed so as to penetrate the center of the heat transfer tube. Further, in the straight tube portion of the heat transfer tube, the fin interval (heat sink distance) was set to 1.0 mm. In addition, here, 300 fins are prepared and divided into groups of 60 pieces. In each fin group, the fins are arranged in parallel to be connected. In this way, in a heat transfer tube, five fin groups of all the same width are formed at predetermined intervals.

接著，分別製作第1圖所示形狀之蛇管熱交換器，即，對傳熱管未形成有散熱片群之處施行彎曲加工，使傳熱管構造成U字形且散熱片群配列相距預定間隔(d)，並且傳熱管配置成蛇行狀態，依序貫通該等配列之散熱片群。另，如表1所示，將散熱片群間之距離(d)為本發明範圍內者作為No.1~10之熱交換器，將本發明範圍外者作為No.11,12之熱交換器。 Next, the coil heat exchanger having the shape shown in Fig. 1 is separately produced, that is, the heat transfer tube is not formed with a fin group, and the heat transfer tube is formed in a U shape and the fin group is arranged at a predetermined interval. (d), and the heat transfer tubes are arranged in a meandering state, sequentially passing through the arranged heat sink groups. Further, as shown in Table 1, the distance (d) between the fin groups is the heat exchanger of No. 1 to 10 within the scope of the present invention, and the heat exchanger of No. 11, 12 is used as the outside of the scope of the present invention. Device.

另，將測量之如此準備之各熱交換器No.1~12之傳熱管之芯材與散熱片之各孔蝕電位，及該等散熱片與傳熱管之間之孔蝕電位差，合併顯示於以下表1。在此，測量各孔蝕電位時之條件，係使用5%NaCl水溶液(pH=3，醋酸酸性)作為測試溶液，測試溫度：25℃，作為測試時之對極之電極素材：SCE，掃描速度：20mV/m，如此來進行測量。 In addition, the pitting potentials of the core material and the heat sink of the heat transfer tubes of each of the heat exchangers No. 1 to 12 thus prepared, and the pitting potential difference between the fins and the heat transfer tubes are combined. Shown in Table 1 below. Here, the conditions for measuring each pitting potential are as follows: 5% NaCl aqueous solution (pH=3, acetic acid acidity) is used as the test solution, and the test temperature is 25° C., as the electrode material of the opposite electrode during the test: SCE, scanning speed : 20mV/m, so measure.

然後，在噴霧室內溫度：35℃，噴霧量：1~2ml/80cm2/h之條件下，分別對如此準備之各熱交換器噴吹以醋酸調整為pH：3之5%鹽水測試液達4週，如此實施腐蝕測試。在此腐蝕測試後，對各熱交換器，藉顯微鏡觀察剝離散熱片後之傳熱管之孔蝕，並比較評價其多寡。即，孔蝕顯著時表示為×，辨認出少許孔蝕時表示為△，幾乎未辨認出孔蝕時表示為○，完全未辨認出孔蝕時表示為◎，其結果揭示於表1。 Then, in the spray chamber temperature: 35 ° C, spray amount: 1 ~ 2ml / 80cm 2 / h, respectively, each of the heat exchangers thus prepared is sprayed with acetic acid adjusted to pH: 3 5% saline test solution For 4 weeks, the corrosion test was carried out in this way. After the corrosion test, the perforation of the heat transfer tubes after the heat sink was peeled off was observed by a microscope for each heat exchanger, and the amount of the heat transfer tubes was compared. That is, when the pitting corrosion is remarkable, it is represented by ×, when a small pitting corrosion is recognized, it is represented by Δ, and when pitting corrosion is hardly recognized, it is represented by ○, and when pitting corrosion is not recognized at all, it is represented by ◎, and the results are shown in Table 1.

又，為評價各熱交換器所含水分，於是抬起浸漬 於水槽之各熱交換器，測量靜置1分鐘後之水分量，視此為保水量。在此，以散熱片間距為1.0mm之熱交換器之重量為100%，相對比較下，以150%以下為合格。 In addition, in order to evaluate the moisture content of each heat exchanger, the impregnation is lifted. In each heat exchanger of the water tank, the amount of water after standing for 1 minute was measured, and this was regarded as the water retention amount. Here, the weight of the heat exchanger having a fin pitch of 1.0 mm is 100%, and in comparison, 150% or less is acceptable.

自此表1結果可知，散熱片群間距離(d)為1.0mm或1.5mm之熱交換器No.1~10，均保水量(水分量)少，因此認定為可將冷凝水自熱交換器順暢排出者。又，在熱交換器No.1~3,5,7，Al材質傳熱管與Al材質散熱片之組合，仍構成該等構件間之自然孔蝕電位差為30mV以上，所以實施腐蝕測試，也幾乎未辨認出傳熱管發生孔蝕。另外，在熱交換器No.4及No.6，Cu材質傳熱管與Al材質散熱片之組合，構成該等構件間之自然孔蝕電位差大幅超過30mV，所以實施腐蝕測試，完全未辨認出傳熱管發生孔蝕。相對於此，在散熱片群間距離(d)大於2mm之熱交換器No.11及No. 12，保水量多，因此冷凝水之排出不充分，並且於傳熱管辨認出孔蝕。又，在使用傳熱管外面之表面粗度(Ra)在本發明範圍外之Ra：5.0μm之傳熱管A6而形成之熱交換器No.9，儘管孔蝕電位差為92mV，較30mV大，但結果是仍辨認出少許孔蝕。即，因外表面之表面粗度大而於散熱片環圈部與傳熱管表面之間產生之空隙有水分(冷凝水)滯留，所以容易產生孔蝕。 As can be seen from the results of Table 1, the heat exchanger No. 1 to 10 having a distance (d) of 1.0 mm or 1.5 mm between the fin groups has a small water retention amount (water content), and thus it is considered that the condensed water can be self-heat exchanged. Smooth discharge. In addition, in the heat exchanger No.1 to 3,5,7, the combination of the Al heat transfer tube and the Al material heat sink still constitutes a natural pitting potential difference of 30 mV or more between the members, so the corrosion test is performed. Pitting corrosion of the heat transfer tubes was almost unrecognized. In addition, in the heat exchanger No. 4 and No. 6, the combination of the heat transfer tube made of Cu and the heat sink of the Al material constitutes a natural pitting potential difference between these members which greatly exceeds 30 mV, so the corrosion test is performed, and it is completely unrecognized. Pitting corrosion occurs in the heat transfer tube. On the other hand, the heat exchanger No. 11 and No. in which the distance (d) between the fin groups is greater than 2 mm. 12, the amount of water retention is large, so the discharge of condensed water is insufficient, and the pitting corrosion is recognized in the heat transfer tube. Further, the heat exchanger No. 9 formed by using the heat transfer tube A6 having a surface roughness (Ra) outside the heat transfer tube outside the range of the present invention of Ra: 5.0 μm, although the pitting potential difference is 92 mV, is larger than 30 mV. But the result is still a little pitting. In other words, since the surface roughness of the outer surface is large and moisture (condensed water) is accumulated in the gap between the fin ring portion and the surface of the heat transfer tube, pitting corrosion is likely to occur.

-實施例2- - Example 2

與實施例1之熱交換器No.1同樣地使用A1作為傳熱管，B2作為散熱片，來製成具有16段散熱片群且其上段區域A和下段區域B及其中間區域中，散熱片群之散熱片間距有各種變化之蛇管熱交換器No.21~No.27。各熱交換器之位在上段區域A之散熱片群為4段，且位在下段區域B之散熱片群為4段，此外有8段散熱片群位在該等區域A,B之間之中間區域，各區域之散熱片間距(p1,p2,p3)，考慮到各自位置之風速，故而構成表2所示之值。 In the same manner as the heat exchanger No. 1 of the first embodiment, A1 was used as the heat transfer tube, and B2 was used as the heat sink to form a heat sink having 16 segments, and the upper region A and the lower portion B and the intermediate portion thereof were cooled. The coil heat exchanger No. 21 to No. 27 with various variations in the fin pitch of the film group. The heat sink group in the upper section A of each heat exchanger has 4 segments, and the heat sink group located in the lower section B has 4 segments, and 8 segments of heat sinks are located between the regions A and B. In the intermediate portion, the fin pitch (p 1 , p 2 , p 3 ) of each region takes into account the wind speed at each position, and thus the values shown in Table 2 are formed.

接著，對如前述製成之熱交換器No.21~No.27，為比較其熱交換性能，進行以下實驗。具體而言，在如第3圖所示形態中，將各熱交換器設置在風洞裝置之狀態下，使扇以預定旋轉速度運轉進行通風，此外冷媒側之出入口條件均為固定，如此來測量冷媒質量流量(kg/s)。然後，將所測量之冷媒質量流量乘以冷媒出入口之比焓差(J/kg)，算出熱交換量(W)。另，此實驗中，熱交換器No.21之上段區域A之風速為3.0m/s，下段區域B之風速為1.0m/s，中間區 域之風速為1.5m/s。又，在該實驗中，因散熱片片數之差異而空氣側傳熱面積不同，所以利用算出之熱交換流量除以空氣側傳熱面積之值，算出當熱交換器No.21之值為1.0時之個別性能比。其結果一併顯示於以下表2。 Next, in order to compare the heat exchange performance of the heat exchangers No. 21 to No. 27 prepared as described above, the following experiment was conducted. Specifically, in the embodiment shown in Fig. 3, each of the heat exchangers is installed in the state of the wind tunnel device, the fan is operated at a predetermined rotational speed, and the inlet and outlet conditions on the refrigerant side are fixed, so that the measurement is performed. Refrigerant mass flow rate (kg/s). Then, the measured refrigerant mass flow rate is multiplied by the ratio 焓 (J/kg) of the refrigerant inlet and outlet to calculate the heat exchange amount (W). In addition, in this experiment, the wind speed of the upper section A of the heat exchanger No. 21 was 3.0 m/s, and the wind speed of the lower section B was 1.0 m/s, the intermediate zone. The wind speed of the domain is 1.5m/s. Further, in this experiment, since the heat transfer area on the air side was different due to the difference in the number of fins, the value of the heat exchanger No. 21 was calculated by dividing the calculated heat exchange flow rate by the value of the heat transfer area on the air side. Individual performance ratio at 1.0. The results are shown together in Table 2 below.

自此表2結果可知，熱交換器No.21其散熱片間距自上段區域A至下段區域B均為3.0mm，具有實用上可堪作為空調機之熱交換量。又，熱交換器No.22,25及26其等p2/p1之值位在本發明所規定較佳範圍內，熱交換器整體也無通風阻抗過大狀況，確認熱交換性能尤佳。此外，熱交換器No.23,24與熱交換器No.21同樣地p2/p1之值在較佳範圍之外，當設定上段散熱片群之適當運轉條件，下段散熱片群之通風阻抗過度增大，雖然實用上可堪作為空調機，但作為熱交換器整體之熱交換性能提升效果，認定並不充分。又，熱交換器No.27其p2/p1之值過大，並且下段區域之散熱片間距(p2)較適當散熱片間距大，所以認定為熱交換性能低。 As is apparent from the results of Table 2, the heat exchanger No. 21 has a fin pitch of 3.0 mm from the upper section A to the lower section B, and has a practical heat exchange capacity as an air conditioner. Further, the values of p 2 /p 1 of the heat exchangers Nos. 22, 25 and 26 are within the preferred ranges specified in the present invention, and the heat exchanger as a whole has no excessive ventilation resistance, and it is confirmed that the heat exchange performance is particularly good. Further, in the heat exchanger Nos. 23 and 24, similarly to the heat exchanger No. 21, the value of p 2 / p 1 is outside the preferred range, and when the proper operating conditions of the upper fin group are set, the lower fin group is ventilated. The impedance is excessively increased, and although it is practically applicable as an air conditioner, the effect of improving the heat exchange performance of the entire heat exchanger is not sufficient. Further, in the heat exchanger No. 27, the value of p 2 /p 1 was too large, and the fin pitch (p 2 ) in the lower region was larger than the appropriate fin pitch, so that the heat exchange performance was considered to be low.

-實施例3- - Example 3

所準備的傳熱管係由磷脫氧銅(JIS H3300 C1220)形成之附內面槽傳熱管，其多條內面槽係相對管軸以預定導角延伸之螺旋槽。另，該附內面槽傳熱管之各尺寸，係外徑：6.35mm，底壁厚：0.23mm，槽深度：0.15mm，槽條數量：58條，導角：30°。 The prepared heat transfer tube is an inner grooved heat transfer tube formed of phosphorus deoxidized copper (JIS H3300 C1220), and a plurality of inner groove grooves are spiral grooves extending at a predetermined lead angle with respect to the tube axis. In addition, the dimensions of the inner surface groove heat transfer tube are: outer diameter: 6.35 mm, bottom wall thickness: 0.23 mm, groove depth: 0.15 mm, number of groove bars: 58 pieces, and lead angle: 30°.

另一方面，散熱片材料係準備板厚：0.13mm之純鋁(JIS A1050)板材，該散熱片材料之表面有施行與實施例1相同之3層構造之表面處理。此外，準備形成有膜厚1.5μm之撥水性塗膜(36)之另種散熱片材料，即，塗布於耐蝕性塗膜(34)表面之樹脂，使用環氧系樹脂形成之撥水性塗膜用塗料取代前述親水性塗膜(36)，將其塗布於耐蝕性塗膜(34)表面且以220℃溫度加熱10秒。 On the other hand, the fin material was prepared as a pure aluminum (JIS A1050) sheet having a thickness of 0.13 mm, and the surface of the fin material was subjected to a surface treatment of the same three-layer structure as in Example 1. Further, another heat sink material in which a water-repellent coating film (36) having a film thickness of 1.5 μm is formed, that is, a resin applied to the surface of the corrosion-resistant coating film (34), and a water-repellent coating film formed using an epoxy resin is prepared. The hydrophilic coating film (36) was replaced with a coating material, applied to the surface of the corrosion-resistant coating film (34), and heated at a temperature of 220 ° C for 10 seconds.

然後，將如此準備之2種散熱片材料分別裁斷成第1圖之x向12mm，z向16mm之尺寸之矩形，並且於其略中央部設置用以插通傳熱管之貫通孔(於周緣設有0.5mm之環圈之貫通孔)，如此來準備多數2種散熱片。 Then, the two kinds of fin materials thus prepared are respectively cut into rectangles of x-direction 12 mm and z-direction 16 mm in the first figure, and through-holes for inserting the heat transfer tubes at the center of the periphery (at the periphery) A through hole of a 0.5 mm ring is provided, so that a plurality of two types of fins are prepared.

此外，使用如此準備之傳熱管及散熱片，如下進行以於一根傳熱管上形成目標所在之散熱片群。即，將多數此散熱片配列成位處平行而各自貫通孔相距預定間隔，然後傳熱管依序貫通地插通貫通孔後，將傳熱管擴管，如此使傳熱管與散熱片變成一體以於該傳熱管上形成散熱片群。此時，擴管後之傳熱管管徑(D)為6.75mm，且對一片散熱片，一根傳熱管成為貫通其略中央之形態。又，於傳熱 管之直管部，分別依序平行配列以接合散熱片而成為如下述表3散熱片間隔(散熱片間距)和散熱片片數，藉此形成全部均為相同寬度之目標所在散熱片群。 Further, using the thus prepared heat transfer tubes and fins, a heat sink group in which a target is formed is formed on one heat transfer tube as follows. That is, a plurality of the fins are arranged in parallel at positions, and the through holes are spaced apart by a predetermined interval, and then the heat transfer tubes are inserted through the through holes in sequence, and the heat transfer tubes are expanded, so that the heat transfer tubes and the heat sinks become The integrated body forms a heat sink group on the heat transfer tube. At this time, the tube diameter (D) of the heat transfer tube after the pipe expansion was 6.75 mm, and a heat transfer tube was formed so as to penetrate the center of the heat sink. Again, in heat transfer The straight tube portions of the tubes are arranged in parallel in order to join the heat sinks to form the fin spacing (heat sink spacing) and the number of fins as shown in Table 3 below, thereby forming a heat sink group having the same width.

接著，在於傳熱管之長向相距預定間隔形成如前述構成之16個散熱片群後，對傳熱管未配設有散熱片群之處施行彎曲加工以使傳熱管成為U字形態，散熱片群配列相距預定間隔，並且傳熱管配置成蛇行狀態，依序貫通該等配列之散熱片群，如此來製成第1圖所示蛇管熱交換器。另，平行彎曲之傳熱管之間隔(中心間距離)為18mm，散熱片間之間隙為1mm。 Then, after the heat sink tubes are formed with the 16 fin groups as described above at a predetermined interval, the heat transfer tubes are not provided with a heat sink group, and the heat transfer tubes are U-shaped. The fin group is arranged at a predetermined interval, and the heat transfer tubes are arranged in a meandering state, sequentially passing through the arranged fin groups, thereby forming the coil heat exchanger shown in Fig. 1. Further, the interval between the heat transfer tubes which are parallelly bent (the distance between the centers) is 18 mm, and the gap between the fins is 1 mm.

將如前述進行而得之9種熱交換器No.31~39分別如第2圖所示設置於預定室外機，再使冷媒(R410A)流通傳熱管，且藉由扇旋轉執行冷氣運轉，並觀察有無濺水。其結果，係散熱片間隔為0.5mm之熱交換器No.35,37雖然於散熱片表面設有親水性樹脂或撥水性樹脂之塗膜層，但 認定為有發生濺水狀況。另一方面，散熱片間隔為1.0mm以上之熱交換器No.31~34,36,38，認定為全無濺水，確認良好運轉狀態。 Each of the nine types of heat exchangers No. 31 to 39 obtained as described above is installed in a predetermined outdoor unit as shown in Fig. 2, and the refrigerant (R410A) is caused to flow through the heat transfer tubes, and the air-conditioning operation is performed by fan rotation. And observe if there is any splashing water. As a result, the heat exchanger No. 35, 37 having a fin interval of 0.5 mm is provided with a coating layer of a hydrophilic resin or a water-repellent resin on the surface of the fin, but It was determined that there was a splash. On the other hand, in the heat exchangers No. 31 to 34, 36, and 38 in which the fin interval is 1.0 mm or more, it is considered that there is no splashing water, and the good operation state is confirmed.

此外，No.31~34,36,38之散熱片間隔為1.0mm以上之熱交換器(計6種)，為比較其等熱交換性能，便分別進形以下實驗。具體而言，如第2圖所示，設置於預定室外機之狀態下，藉扇使空氣以一定速度及風速流動，且冷媒側之出入口條件均為固定，如此來測量冷媒質量流量(kg/s)。然後，將所測量之冷媒質量流量乘以冷媒出入口之比焓差(J/kg)，算出熱交換量(W)。 Further, No. 31 to 34, 36, and 38 heat exchangers having a fin interval of 1.0 mm or more (six types) were subjected to the following experiments in order to compare their heat exchange performance. Specifically, as shown in Fig. 2, in a state where the predetermined outdoor unit is installed, the fan is used to flow the air at a constant speed and the wind speed, and the inlet and outlet conditions on the refrigerant side are fixed, so that the refrigerant mass flow rate (kg/) is measured. s). Then, the measured refrigerant mass flow rate is multiplied by the ratio 焓 (J/kg) of the refrigerant inlet and outlet to calculate the heat exchange amount (W).

其結果，係散熱片間隔為1.0mm之熱交換器No.31,33其等熱交換量均約為1500W，且散熱片間隔為3.0mm之熱交換器No.32,34均為750W，由此確認該等熱交換器均具有實用上可堪作為空調機之熱交換量。然而，散熱片間隔8mm之No.36,38其等熱交換量低至約100W，故兩者認定為實用上難以作為空調機之熱交換器。 As a result, the heat exchanger No. 31, 33 having a fin interval of 1.0 mm has a heat exchange amount of about 1500 W, and the heat exchanger No. 32, 34 having a fin interval of 3.0 mm is 750 W, This confirms that these heat exchangers have practical heat exchange capacity as air conditioners. However, No. 36, 38 with a fin interval of 8 mm has a heat exchange amount as low as about 100 W, and both of them are considered to be practically difficult to be used as a heat exchanger of an air conditioner.

又，對該等熱交換器No.31~34，求出由傳熱管外徑所決定之截面積與散熱片之投影面積，分別為截面積(ST)：31.7mm2，投影面積(SF)：192mm2，所以其面積比(SF/ST)為6.1倍，位在本發明所規定之適當範圍內(3~30倍)，確認係在兼顧熱交換性能及熱交換器小型化之觀點上為較佳者。 Further, for the heat exchangers No. 31 to 34, the cross-sectional area determined by the outer diameter of the heat transfer tube and the projected area of the heat sink were determined, and the cross-sectional area (ST): 31.7 mm 2 and the projected area (SF). ): 192mm 2 , so the area ratio (SF/ST) is 6.1 times, which is within the appropriate range (3 to 30 times) as specified in the present invention. It is confirmed that the heat exchange performance and the heat exchanger are miniaturized. The above is better.

10‧‧‧熱交換器 10‧‧‧ heat exchanger

12‧‧‧散熱片 12‧‧‧ Heat sink

14‧‧‧散熱片群 14‧‧‧ Heat sink group

16‧‧‧金屬製傳熱管 16‧‧‧Metal heat transfer tube

18‧‧‧彎曲部 18‧‧‧Bend

Claims (23)

一種空調機用蛇管熱交換器，係在相對熱交換流體之流通方向(x向)為直角之方向(y向)，相互平行且相隔預定間隔配置之多片散熱片形成之多數散熱片群，在相對該等x向及y向為直角之方向(z向)相距預定距離配置成列而構成多段散熱片群，並且以一片散熱片貫通有一根至二根金屬製傳熱管之形態，該金屬製傳熱管配置成蛇行形態，以依序貫通前述各段散熱片群之蛇管熱交換器，且構成前述散熱片群之各散熱片由具有同一形狀之金屬板形成，且相鄰散熱片配列相隔0.6~5.0mm之間隔，並且前述多段散熱片群之相鄰之群在前述z向配設相隔2.0mm以下之距離。 A coil heat exchanger for an air conditioner, which is a plurality of fin groups formed by a plurality of fins arranged in parallel with each other at a predetermined interval in a direction perpendicular to a flow direction (x direction) of a heat exchange fluid (y direction), a plurality of finned fins are arranged in a row at a predetermined distance from the x-direction and the y-direction in a direction perpendicular to the y-direction (z-direction), and one heat sink is connected to one of the two metal heat transfer tubes. The metal heat transfer tube is arranged in a meandering manner, and sequentially passes through the coil heat exchanger of each of the heat sink groups, and each of the heat sinks constituting the heat sink group is formed of a metal plate having the same shape, and adjacent heat sinks The arrangement is spaced apart by a distance of 0.6 to 5.0 mm, and the adjacent groups of the plurality of finned fin groups are disposed at a distance of 2.0 mm or less apart from the z-direction. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中構造成前述傳熱管與構成前述散熱片群之各散熱片之間之自然孔蝕電位之差，為30mV以上。 The coil heat exchanger for an air conditioner according to the first aspect of the invention, wherein a difference between a natural pitting potential of the heat transfer tube and each of the fins constituting the fin group is 30 mV or more. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中前述金屬板由鋁或鋁合金構成。 The coil heat exchanger for an air conditioner according to claim 1, wherein the metal plate is made of aluminum or an aluminum alloy. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中前述傳熱管由鋁或鋁合金構成。 The coil heat exchanger for an air conditioner according to claim 1, wherein the heat transfer tube is made of aluminum or an aluminum alloy. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中前述傳熱管由鋁或鋁合金構成且其外表面被賦與鋅之犧牲陽極效果。 The coil heat exchanger for an air conditioner according to claim 1, wherein the heat transfer tube is made of aluminum or an aluminum alloy and the outer surface thereof is imparted with a sacrificial anode effect of zinc. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中前述傳熱管由鋁或鋁合金構成且於其外表面形成有具 有犧牲陽極效果之金屬覆膜，並且該外表面之表面粗度：Ra於管軸方向為0.2~3.0μm。 The coil heat exchanger for an air conditioner according to the first aspect of the invention, wherein the heat transfer tube is made of aluminum or an aluminum alloy and is formed on an outer surface thereof. There is a metal coating which sacrifices an anode effect, and the surface roughness of the outer surface: Ra is 0.2 to 3.0 μm in the tube axis direction. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中前述金屬板之材質係JIS(日本工業標準)A1050、JIS A1100、JIS A1200、JIS A7072及於JIS A1050、JIS A1100或JIS A1200含有0.1~0.5質量%之Mn及/或0.1~1.8質量%之Zn者中其中任一種形成之鋁或鋁合金，且前述傳熱管之材質係JIS A1050、JIS A1100、JIS A1200及JIS A3003中其中任一種形成之鋁或鋁合金。 The coil heat exchanger for an air conditioner according to the first aspect of the invention, wherein the material of the metal plate is JIS (Japanese Industrial Standard) A1050, JIS A1100, JIS A1200, JIS A7072, and JIS A1050, JIS A1100 or JIS A1200. An aluminum or an aluminum alloy formed by any one of 0.1 to 0.5% by mass of Mn and/or 0.1 to 1.8% by mass of Zn, and the material of the heat transfer tube is JIS A1050, JIS A1100, JIS A1200, and JIS A3003. Any of the formed aluminum or aluminum alloys. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中前述傳熱管由銅或銅合金構成。 The coil heat exchanger for an air conditioner according to the first aspect of the invention, wherein the heat transfer tube is made of copper or a copper alloy. 如申請專利範圍第8項之空調機用蛇管熱交換器，其中前述傳熱管之材質係JIS H3300 C1220或JIS H3300 C5010。 The coil heat exchanger for an air conditioner according to claim 8, wherein the heat transfer tube is made of JIS H3300 C1220 or JIS H3300 C5010. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中於前述金屬製傳熱管之內面，具有與管軸方向平行之直槽、具有相對管軸之預定扭角之螺旋槽或於管軸方向交叉之槽構成之十字槽中其中任一種或二種以上。 The coil heat exchanger for an air conditioner according to claim 1, wherein the inner surface of the metal heat transfer tube has a straight groove parallel to the tube axis direction, a spiral groove having a predetermined twist angle with respect to the tube axis, or Any one or two or more of the cross grooves formed by the grooves intersecting in the tube axis direction. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中前述散熱片具有多數朝厚度方向突出且底部外形呈圓形或橢圓形之浮凸部。 The coil heat exchanger for an air conditioner according to claim 1, wherein the fin has a plurality of embossing portions which protrude in a thickness direction and have a circular or elliptical bottom shape. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中於前述散熱片施與有槽縫加工或百葉窗加工。 The coil heat exchanger for an air conditioner according to claim 1, wherein the heat sink is provided with slot processing or blind processing. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中 前述散熱片之投影面積係前述傳熱管之外徑所決定之截面積之3~30倍。 For example, the coil heat exchanger for air conditioners of claim 1 is applicable. The projected area of the heat sink is 3 to 30 times the cross-sectional area determined by the outer diameter of the heat transfer tube. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中前述散熱片之投影面積係200~1000mm2。 For example, the coil heat exchanger for an air conditioner according to the first aspect of the patent application, wherein the projection area of the heat sink is 200 to 1000 mm 2 . 如申請專利範圍第1項之空調機用蛇管熱交換器，其中前述金屬製傳熱管之外徑係3~13mm。 The coil heat exchanger for an air conditioner according to claim 1, wherein the outer diameter of the metal heat transfer tube is 3 to 13 mm. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中於前述金屬板之表面設有底處理層，且於該底處理層之上形成有單層或多層塗膜層，並且該塗膜層之中至少最外層為親水性樹脂或撥水性樹脂形成之塗膜層。 The coil heat exchanger for an air conditioner according to claim 1, wherein a bottom treatment layer is provided on a surface of the metal plate, and a single layer or a plurality of coating layers are formed on the bottom treatment layer, and the coating layer is coated. At least the outermost layer of the film layer is a coating layer formed of a hydrophilic resin or a water repellent resin. 如申請專利範圍第16項之空調機用蛇管熱交換器，其中前述親水性樹脂係選自於聚乙烯醇系樹脂；聚丙烯醯胺系樹脂；聚丙烯酸酯系樹脂；纖維素系樹脂；及聚乙二醇系樹脂所構成之群。 The coil heat exchanger for an air conditioner according to claim 16, wherein the hydrophilic resin is selected from the group consisting of a polyvinyl alcohol resin, a polypropylene amide resin, a polyacrylate resin, and a cellulose resin; A group consisting of polyethylene glycol resins. 如申請專利範圍第16項之空調機用蛇管熱交換器，其中前述撥水性樹脂係選自於環氧系樹脂；聚氨酯系樹脂；丙烯酸系樹脂；三聚氰胺樹脂系樹脂；氟系樹脂；矽氧系樹脂；及聚酯系樹脂所構成之群。 The coil heat exchanger for an air conditioner according to claim 16, wherein the water repellency resin is selected from the group consisting of an epoxy resin; a polyurethane resin; an acrylic resin; a melamine resin resin; a fluorine resin; A group of resins and polyester resins. 如申請專利範圍第1項之空調機用蛇管熱交換器，其中於前述金屬製傳熱管之表面形成有樹脂製塗膜層。 The coil heat exchanger for an air conditioner according to claim 1, wherein a resin coating layer is formed on a surface of the metal heat transfer tube. 如申請專利範圍第19項之空調機用蛇管熱交換器，其中前述樹脂製塗膜層包含有熱傳導性填料。 The coil heat exchanger for an air conditioner according to claim 19, wherein the resin coating layer contains a thermally conductive filler. 一種空調機，係包含有申請專利範圍第1~20項中其中任一項之蛇管熱交換器；及使熱交換流體沿前述x向流通 配列於前述z向之多段散熱片群之扇機構，且當若以位在前述扇機構所行之熱交換流體流通時風速大之第一區域之散熱片群或一部分之相鄰散熱片間之間隔為p1，以位在相對該第一區域之風速為0.7以下之風速之風速小之第二區域之散熱片群或一部分之相鄰散熱片間之間隔為p2時，該等散熱片群或一部分之散熱片之間隔定為可滿足以下公式：1.5≦p2/p1≦3.0。 An air conditioner comprising: a coil heat exchanger according to any one of claims 1 to 20; and a fan mechanism for circulating a heat exchange fluid along the x-direction and arranged in the plurality of fin groups of the z-direction. And if the interval between the heat sink groups or a portion of the adjacent heat sinks of the first region where the wind speed is large when the heat exchange fluid is flowing in the fan mechanism is at a distance p 1 , which is located opposite to the first region When the interval between the heat sink group of the second region where the wind speed is less than 0.7 and the adjacent heat sink of the portion is p 2 , the interval between the heat sink groups or a part of the heat sink is set to satisfy the following formula : 1.5≦p 2 /p 1 ≦3.0. 如申請專利範圍第21項之空調機，其中位在前述第一區域之散熱片群或其一部分，與位在前述第二區域之散熱片群或其一部分，在前述z向係位在不同之段。 The air conditioner of claim 21, wherein the heat sink group or a part thereof in the first region and the heat sink group or a part thereof located in the second region are different in the z-direction system segment. 如申請專利範圍第21項之空調機，其中位在前述第一區域之散熱片群或其一部分，與位在前述第二區域之散熱片群或其一部分，在前述z向係位在相同之段。 The air conditioner of claim 21, wherein the heat sink group or a part thereof in the first region and the heat sink group or a part thereof located in the second region are in the same z direction segment.
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Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014228235A (en) * 2013-05-24 2014-12-08 ホシザキ電機株式会社 Heat exchanger and refrigerator using heat exchanger for condenser or evaporator
KR101400170B1 (en) 2013-09-03 2014-05-28 주식회사 안성에이치이산업 Preventing damage and protection apparatus for heat exchanger using plate
JP6693699B2 (en) * 2015-01-23 2020-05-13 株式会社Ａｆｒｅｘ Heat exchanger and manufacturing method thereof
WO2017070093A1 (en) * 2015-10-23 2017-04-27 Carrier Corporation Hydrophobic heat exchangers
JP2018080857A (en) * 2016-11-14 2018-05-24 サンデンホールディングス株式会社 Heat exchanger
JP2019015432A (en) * 2017-07-05 2019-01-31 日立ジョンソンコントロールズ空調株式会社 Heat exchanger and heat exchange unit
CN107351646A (en) * 2017-08-17 2017-11-17 上海加冷松芝汽车空调股份有限公司 Outdoor heat exchanger for automobile heat pump air-conditioning system
CN109579594A (en) * 2017-09-29 2019-04-05 杭州三花微通道换热器有限公司 Heat exchanger core body and air conditioner with it
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JP2019138582A (en) * 2018-02-13 2019-08-22 株式会社Uacj Heat exchanger for refrigerator freezer
JP2020076531A (en) * 2018-11-07 2020-05-21 ダイキン工業株式会社 Heat exchanger and air conditioner including the same
BR202022020179Y1 (en) * 2022-10-05 2023-09-26 Gav Representação Comercial Ltda CONSTRUCTIVE ARRANGEMENT APPLIED TO ALUMINUM WIRE EVAPORATOR AND CONDENSER

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09303985A (en) * 1996-05-13 1997-11-28 Kobe Steel Ltd Copper tube for heat exchanger excellent in tube expansion
JP2005118857A (en) * 2003-10-20 2005-05-12 Furukawa Sky Kk Coating apparatus for member for heat exchanger made of aluminum alloy and method for manufacturing the heat exchanger using the same
JPWO2007108386A1 (en) * 2006-03-23 2009-08-06 パナソニック株式会社 Finned tube heat exchanger, fins for heat exchanger and heat pump device
JP4969471B2 (en) * 2008-01-29 2012-07-04 三菱電機株式会社 Manufacturing method of aluminum tube for heat exchanger and heat exchanger
JP2009250510A (en) * 2008-04-04 2009-10-29 Mitsubishi Electric Corp Heat exchanger and its manufacturing method
JP5578702B2 (en) * 2009-12-24 2014-08-27 三菱アルミニウム株式会社 Aluminum alloy fin material for heat exchanger and heat exchanger
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