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JP2013250033A - Parallel-flow heat exchanger and air conditioner comprising same - Google Patents

Parallel-flow heat exchanger and air conditioner comprising same Download PDF

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Publication number
JP2013250033A
JP2013250033A JP2012126740A JP2012126740A JP2013250033A JP 2013250033 A JP2013250033 A JP 2013250033A JP 2012126740 A JP2012126740 A JP 2012126740A JP 2012126740 A JP2012126740 A JP 2012126740A JP 2013250033 A JP2013250033 A JP 2013250033A
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Prior art keywords
heat exchanger
water
receiving tank
water receiving
refrigerant
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JP2012126740A
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JP5940895B2 (en
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Tatsu Nagata
達 永田
Ryuta Onishi
竜太 大西
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Sharp Corp
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Sharp Corp
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Priority to JP2012126740A priority Critical patent/JP5940895B2/en
Priority to CN201380011298.XA priority patent/CN104136876B/en
Priority to PCT/JP2013/064847 priority patent/WO2013183508A1/en
Priority to MYPI2014002486A priority patent/MY168586A/en
Publication of JP2013250033A publication Critical patent/JP2013250033A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D3/00—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 flows in a continuous film, or trickles freely, over the conduits
    • F28D3/02—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 flows in a continuous film, or trickles freely, over the conduits with 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
    • F28F25/00—Component parts of trickle coolers
    • F28F25/02—Component parts of trickle coolers for distributing, circulating, and accumulating liquid
    • F28F25/04—Distributing or accumulator troughs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/22—Means for preventing condensation or evacuating condensate
    • F24F13/222—Means for preventing condensation or evacuating condensate for evacuating condensate
    • F24F2013/225—Means for preventing condensation or evacuating condensate for evacuating condensate by evaporating the condensate in the cooling medium, e.g. in air flow from the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0084—Condensers

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a parallel-flow heat exchanger of side flow system, in which water sprinkling to surfaces of the heat exchanger can be easily performed.SOLUTION: A parallel-flow heat exchanger 50 includes two vertical header pipes 51, 52 arranged parallel across a gap and a plurality of flat tubes flatted in the vertical direction 53 for connecting the header pipes 51, 52. A water receiving tank 60 parallel to the flat tube 53 is formed on a top part of the heat exchanger 50, and water dropped down from water conduit holes 61 formed in the water receiving tank 60 flows down along a surface of the heat exchanger 50. A plurality of water conduit holes 61 are arranged at predetermined intervals along a length direction of the water receiving tank 60. Among corrugated fins 55 attached to the flat tube 53, a side sheet 56a attached to the corrugated fin 55 located on the highest position is formed as the water receiving tank 60.

Description

本発明はパラレルフロー型熱交換器及びそれを搭載した空気調和機に関する。   The present invention relates to a parallel flow heat exchanger and an air conditioner equipped with the heat exchanger.

複数のヘッダパイプの間に複数の偏平チューブを配置して偏平チューブ内部の複数の冷媒通路をヘッダパイプの内部に連通させるとともに、偏平チューブ間にコルゲートフィン等のフィンを配置したパラレルフロー型の熱交換器は、カーエアコンや建物用空気調和機の室外側ユニットなどに広く利用されている。   A parallel flow type heat in which a plurality of flat tubes are arranged between a plurality of header pipes so that a plurality of refrigerant passages in the flat tubes communicate with the inside of the header pipe, and fins such as corrugated fins are arranged between the flat tubes. Exchangers are widely used in outdoor units of car air conditioners and building air conditioners.

特許文献１には、２本の垂直方向ヘッダパイプと、両ヘッダパイプを連結する複数の水平方向偏平チューブを備えるサイドフロー方式のパラレルフロー型熱交換器が記載されている。この熱交換器では偏平チューブの間にコルゲートフィンが配置されている。   Patent Document 1 describes a side flow type parallel flow heat exchanger including two vertical header pipes and a plurality of horizontal flat tubes connecting the two header pipes. In this heat exchanger, corrugated fins are arranged between the flat tubes.

一方で家屋用の空気調和機では、ヒートポンプ方式を採用し、また室外機と室内機に分かれるセパレート型としたものが主流となっている。このような空気調和機で冷房運転を行うと、室内機の側でドレン水が発生する。通常の場合、ドレン水は単に屋外に排水されるのみであるが、このドレン水を室外機側熱交換器の凝縮性能の向上に役立てようとする提案もなされている。その例を特許文献２に見ることができる。   On the other hand, air conditioners for homes use a heat pump system and a separate type that is divided into an outdoor unit and an indoor unit. When cooling operation is performed with such an air conditioner, drain water is generated on the indoor unit side. Normally, drain water is merely drained to the outdoors, but proposals have been made to use this drain water to improve the condensation performance of the outdoor unit-side heat exchanger. An example of this can be seen in US Pat.

特許文献２に記載された空気調和機では、室内機で発生したドレン水を室外機のバケットに溜め、所定量のドレン水が貯留された時点でバケットを貯留姿勢から放流姿勢に姿勢変更し、放流されたドレン水を一旦筐体に受けた後下方に流下させ、室外機側熱交換器の大気取り入れ面に沿ってドレン水を滴下させることにより、冷房時の運転エネルギー省力化を図っている。   In the air conditioner described in Patent Document 2, the drain water generated in the indoor unit is stored in the bucket of the outdoor unit, and when the predetermined amount of drain water is stored, the bucket is changed in posture from the storage posture to the discharge posture, Once drained drain water is received by the housing, it is allowed to flow downward and dripping the drain water along the air intake surface of the outdoor unit-side heat exchanger to reduce the operating energy during cooling. .

特開２０１０−２４９３８８号公報JP 2010-249388 A 特許第３８６１２１９号公報Japanese Patent No. 3861219

本発明は、サイドフロー方式のパラレルフロー型熱交換器を、その表面への水かけが容易な構造とするとともに、その構造上の特徴を生かして、室内機で発生したドレン水を室外機側熱交換器の凝縮性能の向上に役立てようとするものである。   The present invention provides a side flow parallel flow heat exchanger having a structure in which water can be easily applied to the surface, and by taking advantage of the structure, drain water generated in the indoor unit is removed from the outdoor unit side. It is intended to improve the condensation performance of the heat exchanger.

本発明に係るパラレルフロー型熱交換器は、２本の垂直方向ヘッダパイプと、前記両ヘッダパイプを連結する複数の水平方向偏平チューブを備えるサイドフロー方式のパラレルフロー型熱交換器であって、上部に前記偏平チューブと平行な受水槽が形成され、前記受水槽に形成された導水孔から滴下した水が当該熱交換器の表面伝いに流下することを特徴としている。   A parallel flow type heat exchanger according to the present invention is a side flow type parallel flow type heat exchanger comprising two vertical header pipes and a plurality of horizontal flat tubes connecting the two header pipes, A water receiving tank parallel to the flat tube is formed in the upper part, and water dripped from a water guide hole formed in the water receiving tank flows down along the surface of the heat exchanger.

上記構成のパラレルフロー型熱交換器において、前記導水孔は前記受水槽の長さ方向に沿って所定間隔で複数個配置されていることが好ましい。   In the parallel flow heat exchanger having the above-described configuration, it is preferable that a plurality of the water introduction holes are arranged at predetermined intervals along the length direction of the water receiving tank.

上記構成のパラレルフロー型熱交換器において、前記受水槽は前記偏平チューブの全長をカバーする長さであることが好ましい。   In the parallel flow heat exchanger configured as described above, it is preferable that the water receiving tank has a length that covers the entire length of the flat tube.

上記構成のパラレルフロー型熱交換器において、前記偏平チューブに取り付けられるコルゲートフィンのうち、最上位に位置するコルゲートフィンに取り付けられるサイドシートが受水槽として形成されることが好ましい。   In the parallel flow heat exchanger configured as described above, it is preferable that a side sheet attached to the corrugated fin located at the uppermost position among the corrugated fins attached to the flat tube is formed as a water receiving tank.

本発明に係る空気調和機は、室外機と室内機を備え、室外機に上記構造のパラレルフロー型熱交換器を搭載し、当該パラレルフロー型熱交換器の前記受水槽に前記室内機で発生したドレン水を導くことを特徴としている。   An air conditioner according to the present invention includes an outdoor unit and an indoor unit, the parallel flow type heat exchanger having the above structure is mounted on the outdoor unit, and is generated in the water receiving tank of the parallel flow type heat exchanger in the indoor unit. It is characterized by guiding drained water.

本発明によると、上部の受水槽に水を注ぐことにより、パラレルフロー型熱交換器の表面に偏り無く水をかけることができる。そしてこのパラレルフロー型熱交換器を空気調和機の室外機に搭載し、室内機で発生したドレン水を前記受水槽に導くことにより、冷房運転時に凝縮器として用いられている前記パラレルフロー型熱交換器の凝縮性能を向上させることができる。   According to the present invention, water can be poured evenly on the surface of the parallel flow heat exchanger by pouring water into the upper water receiving tank. The parallel flow heat exchanger is mounted on an outdoor unit of an air conditioner, and drain water generated in the indoor unit is guided to the water receiving tank so that the parallel flow heat is used as a condenser during cooling operation. The condensation performance of the exchanger can be improved.

本発明に係る空気調和機の概略構成図で、冷房運転時の状態を示すものである。It is a schematic block diagram of the air conditioner which concerns on this invention, and shows the state at the time of air_conditionaing | cooling operation. 本発明に係る空気調和機の概略構成図で、暖房運転時の状態を示すものである。It is a schematic block diagram of the air conditioner which concerns on this invention, and shows the state at the time of heating operation. 本発明の実施形態に係る空気調和機の制御ブロック図である。It is a control block diagram of the air conditioner concerning the embodiment of the present invention. 本発明に係るパラレルフロー型熱交換器の実施形態を示す概略構成図である。It is a schematic structure figure showing an embodiment of a parallel flow type heat exchanger concerning the present invention. 図４のＶ−Ｖ線に沿った断面図である。It is sectional drawing along the VV line of FIG. 図５の一部分の拡大断面図である。It is an expanded sectional view of a part of FIG. 受水槽に形成される導水孔の第１実施形態を示す上面図である。It is a top view which shows 1st Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第２実施形態を示す上面図である。It is a top view which shows 2nd Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第３実施形態を示す上面図である。It is a top view which shows 3rd Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第４実施形態を示す上面図である。It is a top view which shows 4th Embodiment of the water guide hole formed in a water receiving tank. 受水槽に形成される導水孔の第５実施形態を示す上面図である。It is a top view which shows 5th Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第６実施形態を示す上面図である。It is a top view which shows 6th Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第７実施形態を示す上面図である。It is a top view which shows 7th Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第８実施形態を示す上面図である。It is a top view which shows 8th Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第９実施形態を示す上面図である。It is a top view which shows 9th Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第１０実施形態を示す上面図である。It is a top view which shows 10th Embodiment of the water guide hole formed in a water receiving tank. 受水槽に形成される導水孔の第１１実施形態を示す上面図である。It is a top view which shows 11th Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第１２実施形態を示す上面図である。It is a top view which shows 12th Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第１３実施形態を示す上面図である。It is a top view which shows 13th Embodiment of the water conveyance hole formed in a water receiving tank. 受水槽に形成される導水孔の第１４実施形態を示す上面図である。It is a top view which shows 14th Embodiment of the water conveyance hole formed in a water receiving tank. 図５と同様の拡大断面図で、受水槽の断面の変形態様を示すものである。It is an expanded sectional view similar to FIG. 5, and shows the deformation | transformation aspect of the cross section of a water receiving tank. 受水槽の断面形状のさらなる変形態様を示す断面図である。It is sectional drawing which shows the further deformation | transformation aspect of the cross-sectional shape of a water receiving tank. 受水槽の断面形状のさらなる変形態様を示す断面図である。It is sectional drawing which shows the further deformation | transformation aspect of the cross-sectional shape of a water receiving tank. 受水槽の断面形状のさらなる変形態様を示す断面図である。It is sectional drawing which shows the further deformation | transformation aspect of the cross-sectional shape of a water receiving tank. 受水槽の断面形状のさらなる変形態様を示す断面図である。It is sectional drawing which shows the further deformation | transformation aspect of the cross-sectional shape of a water receiving tank. 受水槽の断面形状のさらなる変形態様を示す断面図である。It is sectional drawing which shows the further deformation | transformation aspect of the cross-sectional shape of a water receiving tank.

図１から図７に基づき、本発明に係るパラレルフロー型熱交換器５０、及びそれを室外機に搭載した空気調和機１についての説明を行う。   Based on FIGS. 1-7, the parallel flow type heat exchanger 50 which concerns on this invention, and the air conditioner 1 which mounted it in the outdoor unit are demonstrated.

サイドフロー方式のパラレルフロー型熱交換器５０の基本構造を図４に示す。図４では紙面上側が熱交換器の上側、紙面下側が熱交換器の下側となる。パラレルフロー型熱交換器５０は、２本の垂直方向ヘッダパイプ５１、５２と、その間に配置される複数の水平方向偏平チューブ５３を備える。ヘッダパイプ５１、５２は水平方向に間隔を置いて平行に配置され、偏平チューブ５３は垂直方向に所定ピッチで配置されている。実際に機器に搭載する段階では、熱交換器５０は設計の要請に従って様々な角度に据え付けられるから、本明細書における「垂直方向」「水平方向」は厳格に解釈されるべきものではない。単なる方向の目安として理解されるべきである。   The basic structure of the side flow parallel flow heat exchanger 50 is shown in FIG. In FIG. 4, the upper side of the paper is the upper side of the heat exchanger, and the lower side of the paper is the lower side of the heat exchanger. The parallel flow heat exchanger 50 includes two vertical header pipes 51 and 52 and a plurality of horizontal flat tubes 53 disposed therebetween. The header pipes 51 and 52 are arranged in parallel at intervals in the horizontal direction, and the flat tubes 53 are arranged at a predetermined pitch in the vertical direction. Since the heat exchanger 50 is installed at various angles according to design requirements at the stage of actually mounting on equipment, the “vertical direction” and “horizontal direction” in this specification should not be interpreted strictly. It should be understood as a mere measure of direction.

偏平チューブ５３は金属を押出成型した細長い成型品であり、図５に示す通り、内部には冷媒を流通させる冷媒通路５４が形成されている。偏平チューブ５３は長手方向である押出成型方向を水平にする形で配置されるので、冷媒通路５４の冷媒流通方向も水平になる。冷媒通路４４は断面形状及び断面面積の等しいものが図５の左右方向に複数個並び、そのため偏平チューブ５３の垂直断面はハーモニカ状を呈している。各冷媒通路５４はヘッダパイプ５１、５２の内部に連通する。   The flat tube 53 is an elongated molded product obtained by extruding a metal, and as shown in FIG. 5, a refrigerant passage 54 through which a refrigerant flows is formed. Since the flat tube 53 is arranged so that the extrusion molding direction, which is the longitudinal direction, is horizontal, the refrigerant flow direction of the refrigerant passage 54 is also horizontal. A plurality of refrigerant passages 44 having the same cross-sectional shape and cross-sectional area are arranged in the left-right direction in FIG. 5, and therefore the vertical cross-section of the flat tube 53 has a harmonica shape. Each refrigerant passage 54 communicates with the header pipes 51 and 52.

偏平チューブ５３の偏平面にはコルゲートフィン５５が取り付けられる。上下に並ぶコルゲートフィン５５のうち、最上段のものと最下段のものの外側にはサイドプレート５６が配置される。なお上部のサイドプレートの符号は「５６ａ」とされている。サイドプレート５６ａの構造は下部のサイドプレート５６と異なっているが、それについては後で説明する。また、フィン５５の形状はコルゲートに限られない。他の形状であってもよい。   Corrugated fins 55 are attached to the flat surface of the flat tube 53. Of the corrugated fins 55 arranged vertically, side plates 56 are arranged outside the uppermost and lowermost ones. In addition, the code | symbol of the upper side plate is set to "56a". The structure of the side plate 56a is different from that of the lower side plate 56, which will be described later. Further, the shape of the fin 55 is not limited to the corrugated. Other shapes may be used.

ヘッダパイプ５１、５２、偏平チューブ５３、コルゲートフィン５５、及びサイドプレート５６、５６ａはいずれもアルミニウム等熱伝導の良い金属からなり、偏平チューブ５３はヘッダパイプ５１、５２に対し、コルゲートフィン５５は偏平チューブ５３に対し、サイドプレート５６、５６ａはコルゲートフィン５５に対し、それぞれロウ付けまたは溶着で固定される。   The header pipes 51 and 52, the flat tubes 53, the corrugated fins 55, and the side plates 56 and 56a are all made of a metal having good heat conductivity such as aluminum. The flat tubes 53 are flat with respect to the header pipes 51 and 52. The side plates 56 and 56a are fixed to the corrugated fin 55 by brazing or welding to the tube 53, respectively.

ヘッダパイプ５１の内部は、１個の仕切部Ｐ１により２個の区画Ｓ１、Ｓ２に仕切られている。仕切部Ｐ１は複数の偏平チューブ５３を複数の偏平チューブグループに区分する。区画Ｓ１には合計２４本の偏平チューブ５３のうち１２本からなる偏平チューブグループが接続され、区画Ｓ２にも１２本の偏平チューブ５３からなる偏平チューブグループが接続される。   The inside of the header pipe 51 is partitioned into two sections S1 and S2 by one partition portion P1. The partition part P1 divides the plurality of flat tubes 53 into a plurality of flat tube groups. A flat tube group consisting of 12 out of a total of 24 flat tubes 53 is connected to the section S1, and a flat tube group consisting of 12 flat tubes 53 is connected to the section S2.

ヘッダパイプ５２の内部は、２個の仕切部Ｐ２、Ｐ３により３個の区画Ｓ３、Ｓ４、Ｓ５に仕切られている。仕切部Ｐ２、Ｐ３は複数の偏平チューブ５３を複数の偏平チューブグループに区分する。区画Ｓ３には合計２４本の偏平チューブ５３のうち４本からなる偏平チューブグループが接続され、区画Ｓ４には１５本の偏平チューブ５３からなる偏平チューブグループが接続され、区画Ｓ５には５本の偏平チューブ５３からなる偏平チューブグループが接続される。   The inside of the header pipe 52 is partitioned into three sections S3, S4, and S5 by two partition portions P2 and P3. The partition parts P2 and P3 divide the plurality of flat tubes 53 into a plurality of flat tube groups. A flat tube group consisting of 4 of the 24 flat tubes 53 in total is connected to the section S3, a flat tube group consisting of 15 flat tubes 53 is connected to the section S4, and 5 pieces are connected to the section S5. A flat tube group consisting of the flat tubes 53 is connected.

上記した偏平チューブ５３の総数、各ヘッダパイプ内部の仕切部の数とそれによって仕切られる区画の数、及び仕切部によって区分される偏平チューブグループ毎の偏平チューブ５３の数は、いずれも単なる例示であり、発明を限定するものではない。   The total number of the flat tubes 53 described above, the number of partition portions inside each header pipe and the number of partitions partitioned thereby, and the number of flat tubes 53 for each flat tube group divided by the partition portions are merely examples. Yes, it does not limit the invention.

区画Ｓ３には冷媒出入パイプ５７が接続される。区画Ｓ５には冷媒出入パイプ５８が接続される。   A refrigerant inlet / outlet pipe 57 is connected to the section S3. A refrigerant inlet / outlet pipe 58 is connected to the section S5.

熱交換器５０の機能は次の通りである。熱交換器５０が凝縮器として用いられるとき、冷媒は冷媒出入パイプ５７を通じて区画Ｓ３に供給される。区画Ｓ３に入った冷媒は区画Ｓ３と区画Ｓ１を連結する４本の偏平チューブ５３を通って区画Ｓ１に向かう。この４本の偏平チューブ５３で編成される偏平チューブグループが冷媒パスＡを構成する。冷媒パスＡはブロック矢印で象徴されている。それ以外の冷媒パスもブロック矢印で象徴させる。   The function of the heat exchanger 50 is as follows. When the heat exchanger 50 is used as a condenser, the refrigerant is supplied to the compartment S3 through the refrigerant inlet / outlet pipe 57. The refrigerant that has entered the compartment S3 travels through the four flat tubes 53 connecting the compartment S3 and the compartment S1 to the compartment S1. The flat tube group formed by the four flat tubes 53 constitutes the refrigerant path A. The refrigerant path A is symbolized by a block arrow. Other refrigerant paths are also symbolized by block arrows.

区画Ｓ１に入った冷媒はそこで折り返し、区画Ｓ１と区画Ｓ４を連結する８本の偏平チューブ５３を通って区画Ｓ４に向かう。この８本の偏平チューブ５３で編成される偏平チューブグループが冷媒パスＢを構成する。   The refrigerant that has entered the section S1 is turned back there, and travels to the section S4 through the eight flat tubes 53 that connect the sections S1 and S4. The flat tube group formed by the eight flat tubes 53 constitutes the refrigerant path B.

区画Ｓ４に入った冷媒はそこで折り返し、区画Ｓ４と区画Ｓ２を連結する７本の偏平チューブ５３を通って区画Ｓ２に向かう。この７本の偏平チューブ５３で編成される偏平チューブグループが冷媒パスＣを構成する。   The refrigerant that has entered the section S4 is turned back there, and travels to the section S2 through the seven flat tubes 53 that connect the sections S4 and S2. The flat tube group formed by the seven flat tubes 53 constitutes the refrigerant path C.

区画Ｓ２に入った冷媒はそこで折り返し、区画Ｓ２と区画Ｓ５を連結する５本の偏平チューブ５３を通って区画Ｓ３に向かう。この５本の偏平チューブ５３で編成される偏平チューブグループが冷媒パスＤを構成する。区画Ｓ５に入った冷媒は冷媒出入パイプ５８より流出する。   The refrigerant that has entered the compartment S2 turns back there, and travels to the compartment S3 through the five flat tubes 53 that connect the compartment S2 and the compartment S5. The flat tube group formed by the five flat tubes 53 constitutes the refrigerant path D. The refrigerant entering the compartment S5 flows out from the refrigerant inlet / outlet pipe 58.

熱交換器５０が蒸発器として用いられるときは、冷媒は冷媒出入パイプ５８を通じて区画Ｓ５に供給される。それ以後の冷媒の流れは、熱交換器５０が凝縮器として用いられるときの冷媒パスを逆に辿る。すなわち冷媒パスＤ→冷媒パスＣ→冷媒パスＢ→冷媒パスＡのルートで冷媒は区画Ｓ１に入り、冷媒出入パイプ５７より流出する。   When the heat exchanger 50 is used as an evaporator, the refrigerant is supplied to the compartment S5 through the refrigerant inlet / outlet pipe 58. Subsequent refrigerant flows follow the refrigerant path when the heat exchanger 50 is used as a condenser. That is, the refrigerant enters the section S <b> 1 through the route of the refrigerant path D → refrigerant path C → refrigerant path B → refrigerant path A and flows out from the refrigerant inlet / outlet pipe 57.

上記熱交換器５０をヒートポンプサイクルの構成要素として用いたセパレート型空気調和機１の概略構成を図１に示す。空気調和機１は室外機１０と室内機３０により構成される。   A schematic configuration of a separate air conditioner 1 using the heat exchanger 50 as a component of a heat pump cycle is shown in FIG. The air conditioner 1 includes an outdoor unit 10 and an indoor unit 30.

室外機１０は、板金製部品と合成樹脂製部品により構成される筐体１１の内部に、圧縮機１２、切替弁１３、室外側熱交換器１４、膨張弁１５、室外側送風機１６などを収納している。切替弁１３は四方弁である。室外側熱交換器１４として熱交換器５０が用いられる。膨張弁１５には開度制御の可能なものが用いられる。室外側送風機はモータにプロペラファンを組み合わせたものである。   The outdoor unit 10 houses a compressor 12, a switching valve 13, an outdoor heat exchanger 14, an expansion valve 15, an outdoor blower 16, and the like in a housing 11 made of sheet metal parts and synthetic resin parts. doing. The switching valve 13 is a four-way valve. A heat exchanger 50 is used as the outdoor heat exchanger 14. As the expansion valve 15, a valve whose opening degree can be controlled is used. The outdoor blower is a combination of a motor and a propeller fan.

室外機１０は２本の冷媒配管１７、１８で室内機３０に接続される。冷媒配管１７は冷房運転時には液体冷媒が流れ、冷媒配管１８に比較して細い管が用いられている。そのため冷媒配管１７は「液管」「細管」などと称されることがある。冷媒配管１８には冷房運転時、気体冷媒が流れ、冷媒配管１７に比較して太い管が用いられている。そのため冷媒配管１８は「ガス管」「太管」などと称されることがある。冷媒には例えばＨＦＣ系のＲ４１０ＡやＲ３２等が用いられる。   The outdoor unit 10 is connected to the indoor unit 30 through two refrigerant pipes 17 and 18. Liquid refrigerant flows through the refrigerant pipe 17 during the cooling operation, and a pipe that is thinner than the refrigerant pipe 18 is used. Therefore, the refrigerant pipe 17 may be referred to as “liquid pipe”, “narrow pipe”, or the like. A gas refrigerant flows through the refrigerant pipe 18 during the cooling operation, and a pipe that is thicker than the refrigerant pipe 17 is used. Therefore, the refrigerant pipe 18 may be referred to as “gas pipe”, “thick pipe”, or the like. For example, HFC R410A or R32 is used as the refrigerant.

室外機１０の内部の冷媒配管で、冷媒配管１７に接続される冷媒配管には二方弁１９が設けられ、冷媒配管１８に接続される冷媒配管には三方弁２０が設けられる。二方弁１９と三方弁２０は、室外機１０から冷媒配管１７、１８が取り外されるときに閉じられ、室外機１０から外部に冷媒が漏れることを防ぐ。室外機１０から、あるいは室内機３０を含めた冷凍サイクル全体から、冷媒を回収する必要があるときは、三方弁２０を通じて回収が行われる。   In the refrigerant pipe inside the outdoor unit 10, a two-way valve 19 is provided in the refrigerant pipe connected to the refrigerant pipe 17, and a three-way valve 20 is provided in the refrigerant pipe connected to the refrigerant pipe 18. The two-way valve 19 and the three-way valve 20 are closed when the refrigerant pipes 17 and 18 are removed from the outdoor unit 10 to prevent the refrigerant from leaking from the outdoor unit 10 to the outside. When it is necessary to recover the refrigerant from the outdoor unit 10 or the entire refrigeration cycle including the indoor unit 30, the recovery is performed through the three-way valve 20.

室内機３０は、合成樹脂製部品により構成される筐体３１の内部に、室内側熱交換器３２、室内側送風機３３などを収納している。室内側熱交換器３２は、３個の熱交換器３２Ａ、３２Ｂ、３２Ｃを、室内側送風機３３を覆う屋根のように組み合わせたものである。熱交換器３２Ａ、３２Ｂ、３２Ｃのいずれかまたは全部を熱交換器５０で構成することも可能である。室内側送風機３３はモータにクロスフローファンを組み合わせたものである。   The indoor unit 30 houses an indoor heat exchanger 32, an indoor blower 33, and the like in a housing 31 formed of synthetic resin parts. The indoor heat exchanger 32 is a combination of three heat exchangers 32 </ b> A, 32 </ b> B, and 32 </ b> C like a roof that covers the indoor blower 33. Any or all of the heat exchangers 32 </ b> A, 32 </ b> B, and 32 </ b> C can be configured by the heat exchanger 50. The indoor blower 33 is a combination of a motor and a cross flow fan.

空気調和機１の運転制御を行う上で、各所の温度を知ることが不可欠である。この目的のため、室外機１０と室内機３０に温度検出器が配置される。室外機１０においては、室外側熱交換器１４に温度検出器２１が配置され、圧縮機１２の吐出部となる吐出管１２ａに温度検出器２２が配置され、圧縮機１２の吸入部となる吸入管１２ｂに温度検出器２３が配置され、膨張弁１５と二方弁１９の間の冷媒配管に温度検出器２４が配置され、筐体１１の内部の所定箇所に外気温測定用の温度検出器２５が配置される。室内機３０においては、室内側熱交換器３２に温度検出器３４が配置される。温度検出器２１、２２、２３、２４、２５、３４はいずれもサーミスタにより構成される。   In order to control the operation of the air conditioner 1, it is indispensable to know the temperature of each place. For this purpose, temperature detectors are arranged in the outdoor unit 10 and the indoor unit 30. In the outdoor unit 10, a temperature detector 21 is disposed in the outdoor heat exchanger 14, and a temperature detector 22 is disposed in the discharge pipe 12 a serving as the discharge unit of the compressor 12, and the suction serving as the suction unit of the compressor 12. A temperature detector 23 is disposed in the pipe 12 b, a temperature detector 24 is disposed in the refrigerant pipe between the expansion valve 15 and the two-way valve 19, and a temperature detector for measuring the outside air temperature at a predetermined location inside the housing 11. 25 is arranged. In the indoor unit 30, a temperature detector 34 is disposed in the indoor heat exchanger 32. Each of the temperature detectors 21, 22, 23, 24, 25, and 34 is formed of a thermistor.

空気調和機１の全体制御を司るのは図３に示す制御部４０である。制御部４０は
室内温度が使用者によって設定された目標値に達するように制御を行う。 The control unit 40 shown in FIG. 3 controls the overall control of the air conditioner 1. The control unit 40 performs control so that the room temperature reaches a target value set by the user.

制御部４０は圧縮機１２、切替弁１３、膨張弁１５、室外側送風機１６、及び室内側送風機３３に対し動作指令を発する。また制御部４０は温度検出器２１〜２５、及び温度検出器３４からそれぞれの検出温度の出力信号を受け取る。制御部４０は温度検出器２１〜２５及び温度検出器３４からの出力信号を参照しつつ、圧縮機１２、室外側送風機１６、及び室内側送風機３３に対し運転指令を発し、切替弁１３と膨張弁１５に対しては状態切り替えの指令を発する。   The control unit 40 issues operation commands to the compressor 12, the switching valve 13, the expansion valve 15, the outdoor fan 16, and the indoor fan 33. The control unit 40 receives output signals of the detected temperatures from the temperature detectors 21 to 25 and the temperature detector 34. While referring to the output signals from the temperature detectors 21 to 25 and the temperature detector 34, the control unit 40 issues an operation command to the compressor 12, the outdoor fan 16, and the indoor fan 33, and the expansion valve 13 and the expansion valve 13 are expanded. A command for switching the state is issued to the valve 15.

図１は空気調和機１が冷房運転あるいは除霜運転を行っている状態を示す。この時圧縮機１２は冷房時循環、すなわち圧縮機１２から吐出された冷媒が先に室外側熱交換器１４に入る循環様式で冷媒を循環させる。   FIG. 1 shows a state in which the air conditioner 1 is performing a cooling operation or a defrosting operation. At this time, the compressor 12 circulates the refrigerant in a cooling mode, that is, a circulation mode in which the refrigerant discharged from the compressor 12 first enters the outdoor heat exchanger 14.

圧縮機１２から吐出された高温高圧の冷媒は室外側熱交換器１４に入り、そこで室外空気との熱交換が行われる。冷媒は室外空気に対し放熱を行い、凝縮する。凝縮して液状となった冷媒は室外側熱交換器１４から膨張弁１５に入り、そこで減圧される。減圧後の冷媒は室内側熱交換器３２に送られ、膨張して低温低圧となり、室内側熱交換器３２の表面温度を下げる。表面温度の下がった室内側熱交換器３２は室内空気から吸熱し、これにより室内空気は冷やされる。吸熱後、低温の気体状の冷媒は圧縮機１２に戻る。室外側送風機１６によって生成された気流が室外側熱交換器１４からの放熱を促進し、室内側送風機３３によって生成された気流が室内側熱交換器３２の吸熱を促進する。   The high-temperature and high-pressure refrigerant discharged from the compressor 12 enters the outdoor heat exchanger 14 where heat exchange with outdoor air is performed. The refrigerant dissipates heat to the outdoor air and condenses. The refrigerant that is condensed to become liquid enters the expansion valve 15 from the outdoor heat exchanger 14 and is decompressed there. The decompressed refrigerant is sent to the indoor heat exchanger 32, expands to a low temperature and low pressure, and lowers the surface temperature of the indoor heat exchanger 32. The indoor side heat exchanger 32 whose surface temperature has been lowered absorbs heat from the room air, thereby cooling the room air. After the heat absorption, the low-temperature gaseous refrigerant returns to the compressor 12. The air flow generated by the outdoor blower 16 promotes heat radiation from the outdoor heat exchanger 14, and the air flow generated by the indoor blower 33 promotes heat absorption of the indoor heat exchanger 32.

図２は空気調和機１が暖房運転を行っている状態を示す。この時は切替弁１３が切り替えられて冷房運転時と冷媒の流れが逆になる。圧縮機１２は暖房時循環、すなわち圧縮機１２から吐出された冷媒が先に室内側熱交換器３２に入る循環様式で冷媒を循環させる。   FIG. 2 shows a state where the air conditioner 1 is performing a heating operation. At this time, the switching valve 13 is switched to reverse the refrigerant flow during the cooling operation. The compressor 12 circulates the refrigerant in a circulation mode during heating, that is, in a circulation mode in which the refrigerant discharged from the compressor 12 first enters the indoor heat exchanger 32.

圧縮機１２から吐出された高温高圧の冷媒は室内側熱交換器３２に入り、そこで室内空気との熱交換が行われる。冷媒は室内空気に対し放熱を行い、室内空気は暖められる。放熱し、凝縮して液状となった冷媒は室内側熱交換器３２から膨張弁１５に入り、そこで減圧される。減圧後の冷媒は室外側熱交換器１４に送られ、膨張して低温低圧となり、室外側熱交換器１４の表面温度を下げる。表面温度の下がった室外側熱交換器１４は室外空気から吸熱する。吸熱後、低温の気体状の冷媒は圧縮機１２に戻る。室内側送風機３３によって生成された気流が室内側熱交換器３２からの放熱を促進し、室外側送風機１６によって生成された気流が室外側熱交換器１４による吸熱を促進する。   The high-temperature and high-pressure refrigerant discharged from the compressor 12 enters the indoor heat exchanger 32 where heat exchange with the indoor air is performed. The refrigerant dissipates heat to the room air, and the room air is warmed. The refrigerant that has dissipated heat and has become liquid by condensing enters the expansion valve 15 from the indoor heat exchanger 32 and is decompressed there. The decompressed refrigerant is sent to the outdoor heat exchanger 14 and expands to a low temperature and low pressure, thereby lowering the surface temperature of the outdoor heat exchanger 14. The outdoor heat exchanger 14 whose surface temperature has dropped absorbs heat from outdoor air. After the heat absorption, the low-temperature gaseous refrigerant returns to the compressor 12. The air flow generated by the indoor fan 33 promotes heat dissipation from the indoor heat exchanger 32, and the air flow generated by the outdoor fan 16 promotes heat absorption by the outdoor heat exchanger 14.

室外側熱交換器１４を構成するパラレルフロー型熱交換器５０の上部には、外部から供給される水を受け止める受水槽６０が設けられる。受水槽６０は偏平チューブ５３と平行に延び、偏平チューブ５３の全長をカバーする長さとされる。受水槽６０は偏平チューブ５３と大体同じ長さであればよく、偏平チューブ５３から多少はみ出す長さであっても、あるいは偏平チューブ５３に少し届かない長さであっても、特に問題はない。   A water receiving tank 60 for receiving water supplied from the outside is provided on the upper part of the parallel flow heat exchanger 50 constituting the outdoor heat exchanger 14. The water receiving tank 60 extends in parallel with the flat tube 53 and has a length that covers the entire length of the flat tube 53. The water receiving tank 60 may be approximately the same length as the flat tube 53, and there is no particular problem even if it is a length that slightly protrudes from the flat tube 53 or a length that does not reach the flat tube 53 a little.

受水槽６０の底部には導水孔６１が形成されている。導水孔６１は受水槽６０の長さ方向に沿って所定間隔で複数個配置される。図４から図６に示すパラレルフロー型熱交換器５０では、上部のサイドプレート４１ａが角張った樋形の断面とされ、このサイドプレート５６ａが受水槽６０を構成する。サイドプレートは生産性の理由からパラレルフロー型熱交換器に必要な部材であるため、サイドプレートと受水槽を一体化することで省資源化が可能である。また、サイドプレートを樋形などの断面形状にすることで強度が上がり、熱交換器自体の信頼性向上効果も期待できる。   A water introduction hole 61 is formed at the bottom of the water receiving tank 60. A plurality of water introduction holes 61 are arranged at predetermined intervals along the length direction of the water receiving tank 60. In the parallel flow type heat exchanger 50 shown in FIGS. 4 to 6, the upper side plate 41 a has a square-shaped cross section, and the side plate 56 a constitutes the water receiving tank 60. Since the side plate is a member necessary for the parallel flow type heat exchanger for the reason of productivity, it is possible to save resources by integrating the side plate and the water receiving tank. Moreover, the strength is increased by making the side plate into a cross-sectional shape such as a bowl, and the reliability improvement effect of the heat exchanger itself can be expected.

冷房運転時、室内側熱交換器３２で発生したドレン水はドレンホース３５を経由して受水槽６０に注がれる。ドレン水を注がれた受水槽６０からは、導水孔６１を通じてその直下のコルゲートフィン５５の複数の箇所に水が注がれる。水を注がれたコルゲートフィン５５からは、その正面側の縁及び背面側の縁から水が流れ出す。その水は下方のコルゲートフィン５５に向かって落下する。   During the cooling operation, drain water generated in the indoor heat exchanger 32 is poured into the water receiving tank 60 via the drain hose 35. From the water receiving tank 60 into which drain water has been poured, water is poured into a plurality of locations of the corrugated fins 55 directly below the water guiding holes 61. From the corrugated fins 55 into which water has been poured, water flows out from the edge on the front side and the edge on the back side. The water falls toward the lower corrugated fin 55.

熱交換器５０は、送風方向の上流側においても下流側においてもコルゲートフィン５５の端が偏平チューブ５３の縁より突き出しており、最上段のコルゲートフィン５５の縁から落下したドレン水は、送風方向上流側のコルゲートフィン５５の端と送風方向下流側のコルゲートフィン５５の端の両方を濡らす。ドレン水は上下に積み重なったコルゲートフィン５５を上段側より下段側へと順次流下する。ドレン水は流下途中で蒸発し、気化熱で熱交換器５０を冷却する。これにより、冷房運転時に凝縮器として機能している熱交換器５０の凝縮圧力が大幅に低下し、凝縮性能が大幅に向上する。   In the heat exchanger 50, the end of the corrugated fin 55 protrudes from the edge of the flat tube 53 on both the upstream side and the downstream side in the blowing direction, and the drain water falling from the edge of the uppermost corrugated fin 55 is blown in the blowing direction. Both the end of the corrugated fin 55 on the upstream side and the end of the corrugated fin 55 on the downstream side in the air blowing direction are wetted. The drain water sequentially flows down the corrugated fins 55 stacked vertically from the upper side to the lower side. The drain water evaporates in the middle of the flow and cools the heat exchanger 50 with the heat of vaporization. As a result, the condensation pressure of the heat exchanger 50 functioning as a condenser during the cooling operation is greatly reduced, and the condensation performance is greatly improved.

サイドプレート５６ａにより構成される受水槽６０はヘッダパイプ５１、５２の間隔に等しい長さとなっているから、熱交換器５０の表面に偏り無く水をかけることができる。   Since the water receiving tank 60 constituted by the side plate 56a has a length equal to the interval between the header pipes 51 and 52, water can be poured onto the surface of the heat exchanger 50 without any deviation.

熱交換器５０の表面を伝って流下するドレン水が、熱交換器５０の下端に達する前に全部蒸発するのが望ましいが、熱交換器５０の下端まで液体の形を保ち、熱交換器５０の下端から滴下するドレン水も存在する。そのようなドレン水を受け止めるドレンパンを室外機１０の筐体１１の内部に配置し、受け止めたドレン水を適宜外部に廃棄できるようにしておくのがよい。   It is desirable that all drain water flowing down along the surface of the heat exchanger 50 evaporates before reaching the lower end of the heat exchanger 50, but the liquid form is maintained up to the lower end of the heat exchanger 50, and the heat exchanger 50 There is also drain water dripping from the lower end of. It is preferable that a drain pan for receiving such drain water is disposed inside the housing 11 of the outdoor unit 10 so that the drain water received can be appropriately discarded to the outside.

また、ドレンホース３５を経由して受水槽６０に注がれたドレン水が、受水槽６０全体に行き渡るように、受水槽６０の内部底面に傾斜を設けてもよい。その際、受水槽６０の底部の厚みを変えて内部底面に傾斜をつけてもよいし、熱交換器５０全体をドレンホース３５側のヘッダパイプ５２が他方のヘッダパイプ５１よりも高くなるように傾斜させてもよいし、さらには、室外機１０全体を同様に傾斜させてもよい。ただしいずれの場合の傾斜具合もドレン水が流れる程度であればよく、目に見えるほど傾斜させる必要はない。   Moreover, you may provide an inclination in the inner bottom face of the water receiving tank 60 so that the drain water poured into the water receiving tank 60 via the drain hose 35 may be distributed throughout the water receiving tank 60. At that time, the bottom of the water receiving tank 60 may be changed to incline the inner bottom surface, and the header pipe 52 on the drain hose 35 side of the entire heat exchanger 50 may be higher than the other header pipe 51. The entire outdoor unit 10 may be similarly inclined. However, the inclination in any case is sufficient if drain water flows, and it is not necessary to incline so as to be visible.

図７から図１９に導水孔６１の様々な実施形態を示す。   Various embodiments of the water guiding hole 61 are shown in FIGS.

図７に示す第１実施形態では、導水孔６１は長軸の方向が受水槽６０の長さ方向に一致する楕円形とされており、この導水孔６１が複数個、受水槽６０の長さ方向に沿って一定間隔で配置されている。なお楕円形は長円形（陸上トラックの形状）であってもよい。楕円形が長円形であってもよいことは以後の実施形態についても同じである。   In the first embodiment shown in FIG. 7, the water guide hole 61 is an oval shape whose major axis coincides with the length direction of the water receiving tank 60. They are arranged at regular intervals along the direction. The ellipse may be an oval (land track shape). The oval shape may be an oval shape as well in the following embodiments.

図８に示す第２実施形態では、導水孔６１は長軸の方向が受水槽６０の長さ方向と直角な楕円形とされており、この導水孔６１が複数個、受水槽６０の長さ方向に沿って一定間隔で配置されている。   In the second embodiment shown in FIG. 8, the water guide hole 61 has an elliptical shape whose major axis is perpendicular to the length direction of the water receiving tank 60, and the length of the water receiving tank 60 is plural. They are arranged at regular intervals along the direction.

図９に示す第３実施形態では、導水孔６１は円形とされており、この導水孔６１が複数個、受水槽６０の長さ方向に沿って一定間隔で配置されている。   In the third embodiment shown in FIG. 9, the water guide holes 61 are circular, and a plurality of the water guide holes 61 are arranged at regular intervals along the length direction of the water receiving tank 60.

図１０に示す第４実施形態では、導水孔６１は三角形とされており、この導水孔６１が複数個、受水槽６０の長さ方向に沿って一定間隔で配置されている。   In the fourth embodiment shown in FIG. 10, the water guiding holes 61 are triangular, and a plurality of the water guiding holes 61 are arranged at regular intervals along the length direction of the water receiving tank 60.

図１１に示す第５実施形態では、導水孔６１は正方形とされており、この導水孔６１が複数個、受水槽６０の長さ方向に沿って一定間隔で配置されている。   In the fifth embodiment shown in FIG. 11, the water conveyance holes 61 are square, and a plurality of the water conveyance holes 61 are arranged at regular intervals along the length direction of the water receiving tank 60.

図１２に示す第６実施形態では、導水孔６１は第１実施形態と同様の楕円形とされており、この導水孔６１が複数個、受水槽６０の長さ方向に沿って２列に配置されている。各列における導水孔６１の間隔は一定である。   In the sixth embodiment shown in FIG. 12, the water guide holes 61 have an elliptical shape similar to that of the first embodiment, and a plurality of the water guide holes 61 are arranged in two rows along the length direction of the water receiving tank 60. Has been. The interval between the water guide holes 61 in each row is constant.

図１３に示す第７実施形態では、導水孔６１は第２実施形態と同様の楕円形とされており、この導水孔６１が複数個、受水槽６０の長さ方向に沿って２列に配置されている。各列における導水孔６１の間隔は一定である。   In the seventh embodiment shown in FIG. 13, the water guide holes 61 are formed in the same elliptical shape as in the second embodiment, and a plurality of the water guide holes 61 are arranged in two rows along the length direction of the water receiving tank 60. Has been. The interval between the water guide holes 61 in each row is constant.

図１４に示す第８実施形態では、導水孔６１は第３実施形態と同様の円形とされており、この導水孔６１が複数個、受水槽６０の長さ方向に沿って２列に配置されている。各列における導水孔６１の間隔は一定である。   In the eighth embodiment shown in FIG. 14, the water guide holes 61 have a circular shape similar to that of the third embodiment, and a plurality of the water guide holes 61 are arranged in two rows along the length direction of the water receiving tank 60. ing. The interval between the water guide holes 61 in each row is constant.

図１５に示す第９実施形態では、導水孔６１は第４実施形態と同様の三角形とされており、この導水孔６１が複数個、受水槽６０の長さ方向に沿って２列に配置されている。各列における導水孔６１の間隔は一定である。   In the ninth embodiment shown in FIG. 15, the water guide holes 61 are formed in the same triangle as in the fourth embodiment, and a plurality of water guide holes 61 are arranged in two rows along the length direction of the water receiving tank 60. ing. The interval between the water guide holes 61 in each row is constant.

図１６に示す第１０実施形態では、導水孔６１は第５実施形態と同様の正方形とされており、この導水孔６１が複数個、受水槽６０の長さ方向に沿って２列に配置されている。各列における導水孔６１の間隔は一定である。   In the tenth embodiment shown in FIG. 16, the water guide holes 61 have the same square shape as the fifth embodiment, and a plurality of the water guide holes 61 are arranged in two rows along the length direction of the water receiving tank 60. ing. The interval between the water guide holes 61 in each row is constant.

図１７に示す第１１実施形態では、導水孔６１は長軸の方向が受水槽６０の長さ方向に一致する楕円形のものと円形のものとが交互に、受水槽６０の長さ方向に沿って一定間隔で配置されている。楕円形の導水孔６１と円形の導水孔６１との間隔は一定である。   In the eleventh embodiment shown in FIG. 17, the water guide hole 61 has an elliptical shape and a circular shape alternately in the length direction of the water receiving tank 60, the major axis of which coincides with the length direction of the water receiving tank 60. It is arranged at regular intervals along. The distance between the elliptical water guide hole 61 and the circular water guide hole 61 is constant.

第１から第１１までの実施形態では、導水孔６１の大きさはどの位置でも同じとされる（第１１実施形態では楕円形の導水孔６１はそれら同士で大きさが比較され、円形の導水孔６１はそれら同士で大きさが比較される）。また列内における導水孔６１の間隔は等間隔とされる。しかしながら、ドレンホース３５から遠ざかるにつれ導水孔６１を大きくし、あるいは導水孔６１の間隔を狭くするなどして、ドレンホース３５からの距離にかかわらず等量の水が滴下するようにしてもよい。   In the first to eleventh embodiments, the size of the water guiding hole 61 is the same at any position (in the eleventh embodiment, the elliptical water guiding holes 61 are compared in size, and the circular water guiding hole 61 is compared with each other. The sizes of the holes 61 are compared with each other). The intervals between the water guide holes 61 in the row are equal. However, an equal amount of water may be dripped regardless of the distance from the drain hose 35, for example, by enlarging the water guide holes 61 as the distance from the drain hose 35 or by narrowing the interval between the water guide holes 61.

図１８に示す第１２実施形態では、ドレンホース３５に近い側、すなわち図の右側には円形の導水孔６１が２列に配置され、ドレンホース３５から遠い側、すなわち図の左側には楕円形の導水孔６１が２列に配置される。楕円形の導水孔６１の方が円形の導水孔６１よりも面積が大きいので、この構成だけでもドレンホース３５からの距離差を補償して、滴下水量の均等化が図られることになる。これに加えて、円形の導水孔６１はそれら同士の間、楕円形の導水孔６１はそれら同士の間で、ドレンホース３５から遠ざかるにつれ導水孔６１を大きくし、あるいは導水孔６１の間隔を狭くするなどして、滴下水量の一層の均等化を図るようにしてもよい。   In the twelfth embodiment shown in FIG. 18, circular water guide holes 61 are arranged in two rows on the side close to the drain hose 35, that is, on the right side of the figure, and on the side far from the drain hose 35, that is, on the left side of the figure. Are arranged in two rows. Since the elliptical water guide hole 61 has a larger area than the circular water guide hole 61, even this configuration alone compensates for the distance difference from the drain hose 35 and equalizes the amount of dripped water. In addition to this, the circular water conveyance holes 61 are between them, and the elliptical water conveyance holes 61 are between them. As the distance from the drain hose 35 is increased, the water conveyance holes 61 are increased, or the distance between the water conveyance holes 61 is decreased. For example, the amount of dripping water may be further equalized.

図１９に示す第１３実施形態では、ドレンホース３５に近い側、すなわち図の右側には三角形の導水孔６１が１列に配置され、ドレンホース３５から遠い側、すなわち図の左側には三角形の導水孔６１が２列に配置される。この構成だけでもドレンホース３５からの距離差を補償して、滴下水量の均等化が図られることになる。これに加えて、各列において、ドレンホース３５から遠ざかるにつれ導水孔６１を大きくし、あるいは導水孔６１の間隔を狭くするなどして、滴下水量の一層の均等化を図るようにしてもよい。   In the thirteenth embodiment shown in FIG. 19, triangular water guide holes 61 are arranged in a row on the side close to the drain hose 35, that is, on the right side of the figure, and on the side far from the drain hose 35, that is, on the left side of the figure. The water guide holes 61 are arranged in two rows. Even with this configuration alone, the distance difference from the drain hose 35 is compensated, and the amount of dripping water is equalized. In addition, in each row, the water flow holes 61 may be enlarged as the distance from the drain hose 35 is increased, or the distance between the water flow holes 61 may be narrowed to further equalize the amount of dripped water.

図２０に示す第１４実施形態では、導水孔６１として、受水槽６０の長さ方向に沿ってスリットが設けられる。この構成によると、スリット内で細管現象が発生する。すなわち、受水槽６０に流入するドレン水量が少なくても、スリット内で発生する細管現象によって広範囲にドレン水を到達させることができる。図２０ではスリットの数は１本とされているが、複数本のスリットを並列状態で設けてもよい。また受水槽６０の強度を確保するため、スリットの所々にブリッジ状の部分を設けてもよい。   In the fourteenth embodiment shown in FIG. 20, a slit is provided as the water guide hole 61 along the length direction of the water receiving tank 60. According to this configuration, a capillary phenomenon occurs in the slit. That is, even if the amount of drain water flowing into the water receiving tank 60 is small, the drain water can reach a wide range by a thin tube phenomenon generated in the slit. Although the number of slits is one in FIG. 20, a plurality of slits may be provided in parallel. Moreover, in order to ensure the strength of the water receiving tank 60, bridge-shaped portions may be provided in the slits.

受水槽６０の断面形状は角形に限られない。図２１に示す半円形であってもよい。同じ角形であっても、図２２に示すように片側の縁の高さが低くなっていてもよい。図２３に示すようにＬ字形であってもよい。図２４の受水槽６０は図２３の受水槽６０の変形であって、水平であった底辺が斜めになり、先端がやや持ち上がった形状になっている。図２５の受水槽６０は図２４の受水槽６０のさらに変形で、途中まで水平であった底辺が途中から斜めに持ち上がる形になっている。図２６の受水槽６０は図２１の受水槽６０の変形で、浅い円弧断面とされている。   The cross-sectional shape of the water receiving tank 60 is not limited to a square shape. The semicircle shown in FIG. 21 may be sufficient. Even if it is the same square, as shown in FIG. 22, the height of the edge of one side may be low. It may be L-shaped as shown in FIG. The water receiving tank 60 of FIG. 24 is a modification of the water receiving tank 60 of FIG. 23, and has a horizontal base that is slanted and a tip that is slightly lifted. The water receiving tank 60 of FIG. 25 is a further modification of the water receiving tank 60 of FIG. 24, and the bottom that has been horizontal up to the middle is lifted obliquely from the middle. The water receiving tank 60 in FIG. 26 is a modification of the water receiving tank 60 in FIG. 21 and has a shallow arc cross section.

これまで、ドレン水を受水槽６０に注ぐことのみ説明してきたが、水道水や雨水を受水槽６０に注ぐこととしてもよい。また受水槽６０を上部のサイドプレート５６ａ以外の部材で構成することとしてもよい。   So far, only drain water has been poured into the water receiving tank 60, but tap water or rain water may be poured into the water receiving tank 60. Moreover, it is good also as comprising the water receiving tank 60 with members other than the upper side plate 56a.

以上、本発明の実施形態につき説明したが、本発明の範囲はこれに限定されるものではなく、発明の主旨を逸脱しない範囲で種々の変更を加えて実施することができる。   Although the embodiments of the present invention have been described above, the scope of the present invention is not limited to these embodiments, and various modifications can be made without departing from the spirit of the invention.

本発明はサイドフロー方式のパラレルフロー型熱交換器及びそれを搭載する空気調和機に広く利用可能である。   The present invention can be widely used for a side flow type parallel flow heat exchanger and an air conditioner equipped with the heat exchanger.

１ 空気調和機
１０ 室外機
１１ 筐体
１２ 圧縮機
１３ 切替弁
１４ 室外側熱交換器
１５ 膨張弁
１６ 室外側送風機
３０ 室内機
３１ 筐体
３２ 室内側熱交換器
３３ 室内側送風機
３５ ドレンホース
４０ 制御部
５０ 熱交換器
５１、５２ ヘッダパイプ
５３ 偏平チューブ
５５ コルゲートフィン
５６、５６ａ サイドプレート
６０ 受水槽
６１ 導水孔 DESCRIPTION OF SYMBOLS 1 Air conditioner 10 Outdoor unit 11 Case 12 Compressor 13 Switching valve 14 Outdoor heat exchanger 15 Expansion valve 16 Outdoor fan 30 Indoor unit 31 Case 32 Indoor side heat exchanger 33 Indoor fan 35 Drain hose 40 Control Portion 50 Heat exchanger 51, 52 Header pipe 53 Flat tube 55 Corrugated fin 56, 56a Side plate 60 Water receiving tank 61 Water guide hole

Claims (5)

２本の垂直方向ヘッダパイプと、前記両ヘッダパイプを連結する複数の水平方向偏平チューブを備えるサイドフロー方式のパラレルフロー型熱交換器であって、
上部に前記偏平チューブと平行な受水槽が形成され、前記受水槽に形成された導水孔から滴下した水が当該熱交換器の表面伝いに流下することを特徴とするパラレルフロー型熱交換器。 A side flow parallel flow heat exchanger comprising two vertical header pipes and a plurality of horizontal flat tubes connecting the two header pipes,
A parallel flow heat exchanger, wherein a water receiving tank parallel to the flat tube is formed at an upper portion, and water dripped from a water introduction hole formed in the water receiving tank flows down along the surface of the heat exchanger. 前記導水孔は前記受水槽の長さ方向に沿って所定間隔で複数個配置されていることを特徴とする請求項１に記載のパラレルフロー型熱交換器。   The parallel flow heat exchanger according to claim 1, wherein a plurality of the water introduction holes are arranged at predetermined intervals along the length direction of the water receiving tank. 前記受水槽は前記偏平チューブの全長をカバーする長さであることを特徴とする請求項１または２に記載のパラレルフロー型熱交換器。   The parallel flow heat exchanger according to claim 1 or 2, wherein the water receiving tank has a length covering the entire length of the flat tube. 前記偏平チューブに取り付けられるコルゲートフィンのうち、最上位に位置するコルゲートフィンに取り付けられるサイドシートが受水槽として形成されることを特徴とするパラレルフロー型熱交換器。   Of the corrugated fins attached to the flat tube, a side flow sheet attached to the uppermost corrugated fin is formed as a water receiving tank. 室外機と室内機を備える空気調和機であって、
前記室外機に請求項１から４のいずれかのパラレルフロー型熱交換器を搭載し、当該パラレルフロー型熱交換器の前記受水槽に前記室内機で発生したドレン水を導くことを特徴とする空気調和機。 An air conditioner including an outdoor unit and an indoor unit,
The parallel flow type heat exchanger according to any one of claims 1 to 4 is mounted on the outdoor unit, and drain water generated in the indoor unit is guided to the water receiving tank of the parallel flow type heat exchanger. Air conditioner.
JP2012126740A 2012-06-04 2012-06-04 Parallel flow type heat exchanger and air conditioner equipped with the same Active JP5940895B2 (en)

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CN201380011298.XA CN104136876B (en) 2012-06-04 2013-05-29 Parallel flow heat exchanger and the air conditioner being provided with this parallel flow heat exchanger
PCT/JP2013/064847 WO2013183508A1 (en) 2012-06-04 2013-05-29 Parallel-flow heat exchanger and air conditioner comprising same
MYPI2014002486A MY168586A (en) 2012-06-04 2013-05-29 Parallel-flow heat exchanger and air conditioner comprising same

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