JP2018096635A - Air conditioner - Google Patents

Air conditioner Download PDF

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JP2018096635A
JP2018096635A JP2016242813A JP2016242813A JP2018096635A JP 2018096635 A JP2018096635 A JP 2018096635A JP 2016242813 A JP2016242813 A JP 2016242813A JP 2016242813 A JP2016242813 A JP 2016242813A JP 2018096635 A JP2018096635 A JP 2018096635A
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heat exchanger
plate fin
plate
air conditioner
protrusion
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JP6739001B2 (en
Inventor
一彦 丸本
Kazuhiko Marumoto
一彦 丸本
健二 名越
Kenji Nagoshi
健二 名越
憲昭 山本
Kensho Yamamoto
憲昭 山本
崇裕 大城
Takahiro Oshiro
崇裕 大城
拓也 奥村
Takuya Okumura
拓也 奥村
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Priority to JP2016242813A priority Critical patent/JP6739001B2/en
Priority to MYPI2019002122A priority patent/MY195659A/en
Priority to PCT/JP2017/041016 priority patent/WO2018110186A1/en
Priority to CN201780071215.4A priority patent/CN109996994B/en
Publication of JP2018096635A publication Critical patent/JP2018096635A/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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning

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

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioner which has high heat exchange efficiency, which is compact and which has high performance.SOLUTION: An air conditioner includes a heat exchanger 5 provided in a body, and a water receiving tray 7 arranged below the heat exchanger. The heat exchanger is the plate fin lamination type heat exchanger which is constituted by laminating plate fins 11, and it is installed being inclined with respect to a perpendicular, and also, out of protrusions 18 forming gaps between the plate fins of the plate fin lamination type heat exchanger, protrusions 18aa arrayed on a lower side end edge of the plate fins are provided further inside than a gap dimension between plate fins than an end edge. Thereby, the heat exchanger can improve heat exchange efficiency by achieving reduced diameter of a flow passage cross sectional area, can prevent dripping of dew condensation water with the protrusions forming gaps in the plate fin lamination being a starting point, can suppress gutter width of the water receiving tray for receiving the dew condensation water, and can achieve suppression of performance deterioration caused by compactification of equipment, increase in air passage resistance and the like.SELECTED DRAWING: Figure 10

Description

本発明は、空気調和機、特に熱交換器の熱交換性能を上げるべくプレートフィン積層型熱交換器を用いたときに生じる結露水用水受皿の大型化や機器全体の性能低下を抑制した空気調和機に関するものである。   The present invention relates to an air conditioner, particularly an air conditioner that suppresses an increase in the size of a water tray for condensed water and a decrease in the performance of the entire device when a plate fin laminated heat exchanger is used to increase the heat exchange performance of the heat exchanger. Related to the machine.

一般に空気調和機は、圧縮機によって圧縮した冷媒を凝縮器や蒸発器等の熱交換器に循環させ空気と熱交換させて冷房もしくは暖房を行うが、その熱交換器は本体内の風路に傾斜設置してあり、冷房時等に熱交換器に結露水が生じるのでこの結露水を受ける水受皿が設けてある（例えば、特許文献１参照）。   In general, an air conditioner circulates a refrigerant compressed by a compressor through a heat exchanger such as a condenser or an evaporator and exchanges heat with air for cooling or heating, but the heat exchanger is connected to an air passage in the main body. Since it is installed at an inclination and condensed water is generated in the heat exchanger during cooling, a water tray for receiving the condensed water is provided (for example, see Patent Document 1).

図１１は特許文献１記載の空気調和機を示し、この空気調和機は、本体１００の上面に吸込口１０１を、下面に吹出口１０２を設け、この本体１００内に上から下に通風させる風路１０３を形成し、この風路１０３の上部に熱交換器１０４を傾斜設置するとともに送風装置１０５を配備して構成してある。そして、上記風路１０３内に傾斜設置されている熱交換器１０４の下方には冷却時等に生じる熱交換器からの結露水を受ける水受皿１０６が設置してある。   FIG. 11 shows an air conditioner described in Patent Document 1. This air conditioner is provided with a suction port 101 on the upper surface of the main body 100 and an air outlet 102 on the lower surface, and the air is passed through the main body 100 from above to below. A passage 103 is formed, and a heat exchanger 104 is installed at an inclination above the air passage 103 and a blower 105 is provided. A water tray 106 for receiving condensed water from the heat exchanger generated at the time of cooling or the like is installed below the heat exchanger 104 that is inclinedly installed in the air passage 103.

このような空気調和機において、その性能や省エネ性はまず熱交換器１０４の熱交換効率に大きく左右される。従って、熱交換器１０４は高効率化が強く求められている。   In such an air conditioner, the performance and energy saving performance are greatly affected by the heat exchange efficiency of the heat exchanger 104. Therefore, high efficiency is strongly demanded for the heat exchanger 104.

この熱交換器１０４の高効率化は、従来、フィン群に貫通させた伝熱管を細径化することによって進められている。   Conventionally, the efficiency of the heat exchanger 104 has been increased by reducing the diameter of a heat transfer tube that penetrates the fin group.

しかしながら、上記伝熱管の細径化には限度があるため、熱交換効率の向上及び小型化は限界に近づきつつある。   However, since there is a limit to reducing the diameter of the heat transfer tube, improvement in heat exchange efficiency and downsizing are approaching the limits.

そこで、出願人はプレートフィンを積層して構成した熱交換器、所謂プレートフィン積層型熱交換器を用いることによって、熱交換器の高効率化を推進することを試みた。   Therefore, the applicant tried to promote the improvement of the efficiency of the heat exchanger by using a so-called plate fin laminated heat exchanger, which is configured by laminating plate fins.

このプレートフィン積層型熱交換器は、プレートフィンの中に形成された流路を流れる冷媒と、積層されたプレートフィンの間を流れる空気との間で熱交換を行うもので、プレートフィンに凹状溝をプレス成形して流路を形成しているので、当該流路の断面積をフィンチューブ型の伝熱管に比べさらに小さくでき、熱交換効率を向上させることができる。   This plate fin laminated heat exchanger exchanges heat between the refrigerant flowing in the flow path formed in the plate fin and the air flowing between the laminated plate fins. Since the channel is formed by press-molding the groove, the cross-sectional area of the channel can be further reduced as compared with the fin tube type heat transfer tube, and the heat exchange efficiency can be improved.

特開２０１６−９５０３８号公報JP-A-2006-95038

しかしながら、上記プレートフィン積層型熱交換器は、積層された各プレートフィン間の隙間を形成するための突起が複数列設してあって、その一部の突起はプレートフィンの長辺の端縁に沿って列設してある。   However, the plate fin laminated heat exchanger has a plurality of protrusions for forming gaps between the stacked plate fins, and some of the protrusions are edges of the long sides of the plate fins. Are lined up along the line.

そのため、このプレートフィン積層型熱交換器を使用すると、熱交換器に結露した水滴が傾斜設置した熱交換器の下側となる端縁（以下、下側端縁と称す）に沿って流下する際
、前記プレートフィンの下側端縁に列接した突起に触れて引っ掛かり重力でそのまま当該突起部分から下方へと滴下してしまう。 Therefore, when this plate fin laminated heat exchanger is used, water droplets condensed on the heat exchanger flow down along the lower edge (hereinafter referred to as the lower edge) of the heat exchanger inclined. At this time, the projections in contact with the lower edge of the plate fin are touched and caught by gravity and dropped downward from the projection portion.

したがって、この熱交換器を傾斜させて設置する際には熱交換器下方に設置する水受皿が熱交換器の傾斜幅一杯の大きなものとなってしまい、機器の大型化や風路抵抗増等による性能劣化を招くという課題が生じる。   Therefore, when this heat exchanger is installed at an inclination, the water tray installed below the heat exchanger becomes a large one with the full width of the heat exchanger, resulting in an increase in equipment size, an increase in airway resistance, etc. The problem of incurring performance degradation due to.

本発明はこのような課題を解決すべくなしたもので、高い熱交換効率を持ち、かつ、コンパクトで高性能な空気調和機とすることを目的としたものである。   The present invention has been made to solve such problems, and aims to provide a compact and high-performance air conditioner having high heat exchange efficiency.

本発明は、上記目的を達成するため、本体内の風路に設置した熱交換器はプレートフィンを積層するとともに当該プレートフィンに設けた突起によりプレートフィン間に隙間を形成して構成したプレートフィン積層型熱交換器とし、かつこのプレートフィン積層型熱交換器を垂線に対し傾斜させて設置するとともに、前記プレートフィン積層型熱交換器のプレートフィン下側端縁に列設した突起は当該下側端縁より内部に設けた構成としてある。   In order to achieve the above object, the present invention provides a plate fin in which a heat exchanger installed in an air passage in a main body is formed by laminating plate fins and forming a gap between plate fins by projections provided on the plate fins. A laminated heat exchanger is installed, and the plate fin laminated heat exchanger is inclined with respect to the vertical line, and the protrusions arranged on the lower edge of the plate fin of the plate fin laminated heat exchanger A configuration is provided inside the side edge.

これにより、この熱交換器は、流路断面積の細径化を図って熱交換効率を向上することができるとともに、傾斜設置したプレートフィンの下側端縁に設けられている突起部分から結露水が滴下するのを防止でき、結露水を受ける水受皿を小型化して機器のコンパクト化や風路抵抗増による性能劣化等を抑制することができる。   As a result, this heat exchanger can improve the heat exchange efficiency by reducing the diameter of the cross-sectional area of the flow path, and at the same time, dew condensation occurs from the protruding portion provided on the lower edge of the plate fin that is installed at an angle. Water can be prevented from dripping, and a water receiving tray that receives condensed water can be reduced in size to suppress downsizing of equipment and performance deterioration due to increased air path resistance.

本発明は、上記構成により、高い熱交換効率を持ち、かつ、コンパクトで高性能な空気調和機とすることができる。   According to the above configuration, the present invention can provide a compact and high-performance air conditioner having high heat exchange efficiency.

本発明の実施の形態１における空気調和機の概略断面図Schematic sectional view of an air conditioner according to Embodiment 1 of the present invention. 同空気調和機の熱交換器を示す斜視図The perspective view which shows the heat exchanger of the air conditioner 同熱交換器を分離して示す斜視図A perspective view showing the heat exchanger separately. 同熱交換器の主体を成すプレートフィン積層体の一部を切断して示す斜視図The perspective view which cut | disconnects and shows a part of plate fin laminated body which comprises the main body of the same heat exchanger 同プレートフィン積層体を構成するプレートフィンの平面図Plan view of plate fins constituting the plate fin laminate 同プレートフィンの拡大平面図Enlarged plan view of the plate fin 同プレートフィンの一部を拡大して示す分解斜視図The exploded perspective view which expands and shows a part of the plate fin 同プレートフィンに設けた突起を示す拡大斜視図Enlarged perspective view showing protrusions provided on the plate fin 同熱交換器の作用を説明する概略斜視図Schematic perspective view for explaining the operation of the heat exchanger 同熱交換器の作用を説明する概略側面図Schematic side view for explaining the operation of the heat exchanger 本発明の実施の形態２における空気調和機の熱交換器を構成するプレートフィンの拡大斜視図The expansion perspective view of the plate fin which comprises the heat exchanger of the air conditioner in Embodiment 2 of this invention 従来の空気調和機を示す概略構成図Schematic configuration diagram showing a conventional air conditioner

第１の発明は、本体内の風路に設置した熱交換器と、前記熱交換器に送風する送風機と、前記熱交換器の下部に設置した水受皿と、を備え、前記熱交換器はプレートフィンを積層するとともに当該プレートフィンに設けた突起によりプレートフィン間に隙間を形成して構成したプレートフィン積層型熱交換器とし、かつこのプレートフィン積層型熱交換器を垂線に対し傾斜させて設置するとともに、前記プレートフィン積層型熱交換器のプレートフィン下側端縁に列設した突起は当該下側端縁より内部に設けた構成としてある。   1st invention is equipped with the heat exchanger installed in the air path in a main body, the air blower ventilated to the said heat exchanger, and the water receiving tray installed in the lower part of the said heat exchanger, The said heat exchanger is A plate fin laminated heat exchanger is formed by laminating plate fins and forming gaps between the plate fins by protrusions provided on the plate fin, and the plate fin laminated heat exchanger is inclined with respect to the vertical line. In addition to the installation, the projections arranged on the lower end edge of the plate fin of the plate fin stacked heat exchanger are provided inside the lower end edge.

これにより、この熱交換器は、流路断面積の細径化を図って熱交換効率を向上することができるとともに、傾斜設置したプレートフィンの下側端縁に設けられている突起部分から結露水が滴下するのを防止でき、結露水を受ける水受皿を小型化して機器のコンパクト化や風路抵抗増による性能劣化等を抑制することができる。   As a result, this heat exchanger can improve the heat exchange efficiency by reducing the diameter of the cross-sectional area of the flow path, and at the same time, dew condensation occurs from the protruding portion provided on the lower edge of the plate fin that is installed at an angle. Water can be prevented from dripping, and a water receiving tray that receives condensed water can be reduced in size to suppress downsizing of equipment and performance deterioration due to increased air path resistance.

第２の発明は、特に第１の発明において、前記突起はプレートフィンの下側端縁より前記プレートフィン間の隙間分寸法より内部に設けた構成としてある。   According to a second aspect of the invention, in particular, in the first aspect of the invention, the protrusion is provided in the interior from the lower end edge of the plate fin from the size of the gap between the plate fins.

これにより結露水がプレートフィンの下側端縁のフィンプレート積層間の隙間に跨って流下するようなことがあっても突起に触れるようなことが無くなって、そのままの勢いで下方部分へと流下していき、突起に引っかかって当該突起部分から滴下するのを防止でき、より確実な滴下防止を実現することができる。   As a result, even if the condensed water flows down across the gap between the fin plate stacks at the lower edge of the plate fin, it does not touch the protrusions and flows down to the lower part as it is. As a result, it is possible to prevent the projection from being caught by the projection and dripping from the projection portion, thereby realizing more reliable dripping prevention.

第３の発明は、特に、第１または第２の発明において、前記突起はその頂部を略球面状とした構成としてある。   According to a third aspect of the invention, in particular, in the first or second aspect of the invention, the protrusion has a substantially spherical shape at the top.

これにより、プレートフィンの下側端縁を流下する結露水の一部が突起に触れるようなことがあっても突起の頂部が略球面状となっているから当該頂部から離れやすくなってそのままプレートフィンの下側端縁に沿って流下するようになり、突起を起点とした結露水の滴下を更に確実に防止することができる。   As a result, even if some of the condensed water flowing down the lower edge of the plate fin touches the protrusion, the top of the protrusion is substantially spherical, so it is easy to move away from the top, and the plate is left as it is. It flows down along the lower end edge of the fin, and the dripping of condensed water starting from the protrusion can be prevented more reliably.

第４の発明は、特に、第１〜第３のいずれか１つの発明において、前記突起はプレートフィンの下側端縁の少なくとも鉛直下方に水受皿が存在しない部分の突起を当該下側端縁より内部に設けた構成としてある。   According to a fourth aspect of the present invention, in particular, in any one of the first to third aspects, the protrusion is a protrusion of a portion where no water pan is present at least vertically below the lower end edge of the plate fin. The configuration is provided more inside.

これにより、鉛直下方に水受皿が存在する部分のプレートフィンの下側端縁の突起は下側端縁直近に設けて比較的強度の弱いフィン端縁の強度を向上させその剛性を高めることができる。そして、この突起を端縁直近に設けたことによって突起の内部側に位置する熱交換有効面積を増大させることもでき、その分熱交換効率を向上させることができる。すなわち、プレートフィンの剛性と熱交換効率の向上を両立させることができる。   As a result, the projection on the lower edge of the plate fin where the water tray is present vertically below is provided in the vicinity of the lower edge to improve the strength of the relatively weak fin edge and increase its rigidity. it can. And by providing this protrusion in the vicinity of the edge, the heat exchange effective area located on the inner side of the protrusion can be increased, and the heat exchange efficiency can be improved accordingly. That is, both the rigidity of the plate fins and the improvement of the heat exchange efficiency can be achieved.

第５の発明は、特に、第１〜第４の発明において、前記プレートフィンは下側端縁とともに上側端縁にも突起を列設し、上記上側端縁の突起は当該上側端縁直近に設けた構成としてある。   In a fifth aspect of the present invention, in particular, in the first to fourth aspects of the present invention, the plate fin has a protrusion on the upper edge as well as a lower edge, and the protrusion on the upper edge is in the immediate vicinity of the upper edge. The configuration is provided.

これにより、プレートフィンの上側端縁部分の剛性を高めるとともに熱交換有効面積の増大によって熱交換効率を向上させることができ、より効果的にプレートフィンの剛性と熱交換効率の向上を実現することができる。   As a result, the rigidity of the upper edge portion of the plate fin can be increased and the heat exchange efficiency can be improved by increasing the heat exchange effective area, and the plate fin rigidity and the heat exchange efficiency can be improved more effectively. Can do.

第６の発明は、特に、第１〜第５の発明において、前記熱交換器はそのプレートフィンの下側端縁部分が風路の上流側に位置するように配置した構成としてある。   In a sixth aspect of the invention, in particular, in the first to fifth aspects of the invention, the heat exchanger is arranged such that the lower end edge portion of the plate fin is located on the upstream side of the air passage.

これにより、風路内を流れる空気の流れによってプレートフィンの下側端縁を流下する結露水の重力による落下作用を抑制でき、結露水はよりプレートフィンの下方部分まで流下してから滴下するようになる。したがって、水受皿をよりコンパクトなものにすることができるとともに、プレートフィンの下側端縁直近に設ける突起の数を多くして剛性と熱交換効率向上効果をより高めることができる。   As a result, it is possible to suppress the dropping action due to the gravity of the dew condensation water flowing down the lower edge of the plate fin by the air flow flowing in the air passage, and the dew condensation water flows down to the lower part of the plate fin and then drops. become. Therefore, the water tray can be made more compact, and the number of projections provided in the vicinity of the lower end edge of the plate fin can be increased to further increase the rigidity and heat exchange efficiency improvement effect.

以下、本発明の実施の形態について、図面を参照して詳細に説明する。なお、以下に説明する実施の形態は一例であり、本発明はこの実施の形態により限定されるものではない
。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The embodiment described below is an example, and the present invention is not limited to this embodiment.

（実施の形態１）
図１は本発明の実施の形態１における空気調和機の概略断面図である。 (Embodiment 1)
FIG. 1 is a schematic sectional view of an air conditioner according to Embodiment 1 of the present invention.

本実施形態の空気調和機は、図示しないが圧縮機、四方弁、熱源側熱交換器、膨張弁、利用側熱交換器、四方弁、圧縮機の順に冷媒を循環させ、熱源側熱交換器を凝縮器とし、利用側熱交換器を蒸発器として作用させる冷房運転を行える。また、四方弁を切替えることによって、この空気調和機は、圧縮機、四方弁、利用側熱交換器、膨張弁、熱源側熱交換器、四方弁、圧縮機の順に冷媒を循環させ、利用側熱交換器を凝縮器とし、熱源側熱交換器を蒸発器として作用させる暖房運転を行える。   Although not shown, the air conditioner of the present embodiment circulates refrigerant in the order of the compressor, the four-way valve, the heat source side heat exchanger, the expansion valve, the use side heat exchanger, the four way valve, and the compressor, and the heat source side heat exchanger Can be used as a condenser, and a cooling operation can be performed by using the use side heat exchanger as an evaporator. In addition, by switching the four-way valve, this air conditioner circulates the refrigerant in the order of the compressor, the four-way valve, the use side heat exchanger, the expansion valve, the heat source side heat exchanger, the four way valve, and the compressor. Heating operation can be performed in which the heat exchanger acts as a condenser and the heat source side heat exchanger acts as an evaporator.

そして、この空気調和機は、室内ユニットと室外ユニットを配管で接続したセパレート式空気調和機となっており、室内ユニットには、利用側熱交換器等が収納され、室外ユニットには、圧縮機、四方弁、膨張弁、熱源側熱交換器等が収納されている。   This air conditioner is a separate air conditioner in which an indoor unit and an outdoor unit are connected by piping. The indoor unit stores a use-side heat exchanger and the like, and the outdoor unit includes a compressor. A four-way valve, an expansion valve, a heat source side heat exchanger, and the like are housed.

上記のように構成された空気調和機の室内ユニットとなる本体１は、図１に示すように、本実施の形態では下面に吸込口２、前面に吹出口３を備え、前記吸込口２と吹出口３との間に略Ｌ字状の風路４を有している。そして、上記風路４には利用側熱交換器となる熱交換器５と送風機６が設けてある。   As shown in FIG. 1, the main body 1 serving as an indoor unit of an air conditioner configured as described above includes a suction port 2 on the lower surface and a blower port 3 on the front surface in the present embodiment. A substantially L-shaped air passage 4 is provided between the air outlet 3 and the air outlet 3. The air passage 4 is provided with a heat exchanger 5 and a blower 6 which are use side heat exchangers.

上記熱交換器５は垂線に対し傾斜させて配置してあり、その下端部には熱交換器５で結露した結露水を受ける水受皿７が設けてある。   The heat exchanger 5 is arranged to be inclined with respect to the vertical line, and a water tray 7 for receiving condensed water condensed by the heat exchanger 5 is provided at a lower end portion thereof.

次に、図２〜図１０を用いて上記熱交換器５の構成を説明する。   Next, the structure of the said heat exchanger 5 is demonstrated using FIGS.

図２は空気調和機の熱交換器を示す斜視図、図３は同熱交換器を分離して示す斜視図、図４は同熱交換器の主体を成すプレートフィン積層体の一部を切断して示す斜視図、図５は同プレートフィン積層体を構成するプレートフィンの平面図、図６は同プレートフィンの拡大平面図、図７は同プレートフィンの一部を拡大して示す分解斜視図、図８は同プレートフィンに設けた突起を示す拡大斜視図、図９は同熱交換器の作用を説明する概略斜視図、図１０は同熱交換器の作用を説明する概略側面図である。   FIG. 2 is a perspective view showing a heat exchanger of an air conditioner, FIG. 3 is a perspective view showing the heat exchanger separately, and FIG. 4 is a partial cut of a plate fin laminate constituting the main body of the heat exchanger. 5 is a plan view of plate fins constituting the plate fin laminate, FIG. 6 is an enlarged plan view of the plate fins, and FIG. 7 is an exploded perspective view showing a part of the plate fins in an enlarged manner. 8 is an enlarged perspective view showing protrusions provided on the plate fin, FIG. 9 is a schematic perspective view for explaining the operation of the heat exchanger, and FIG. 10 is a schematic side view for explaining the operation of the heat exchanger. is there.

本実施の形態の熱交換器５は、図２、図３に示すように、長方形の板状である複数のプレートフィン１１を積層して構成され、その積層方向の両側（図２、図３では左側及び右側）には、プレートフィン１１と平面視が略同一形状のエンドプレート１２ａ、１２ｂが設けられている。エンドプレート１２ａ、１２ｂは、剛性を有する板材で形成されており、例えばアルミニウム、アルミニウム合金、ステンレスなどの金属材を研削により金属加工して形成されている。   As shown in FIGS. 2 and 3, the heat exchanger 5 of the present embodiment is configured by laminating a plurality of plate fins 11 each having a rectangular plate shape, and both sides in the laminating direction (FIGS. 2 and 3). The left and right sides are provided with end plates 12a and 12b having substantially the same shape as the plate fin 11 in plan view. The end plates 12a and 12b are formed of a rigid plate material, and are formed by metal processing such as aluminum, aluminum alloy, and stainless steel by grinding.

なお、上記エンドプレート１２ａ、１２ｂ、複数のプレートフィン１１は積層された状態でロウ付け接合されて一体化し、熱交換器の主体を成すプレートフィン積層体１３を構成している。   The end plates 12a and 12b and the plurality of plate fins 11 are joined together by brazing in a laminated state to constitute a plate fin laminated body 13 constituting the main body of the heat exchanger.

また、上記プレートフィン１１は内部に第１流体である冷媒が流れる複数の並行した冷媒流路群を有しており、この冷媒流路群は略Ｕ字状に形成されていて、これと繋がる流入側ヘッダ流路１４、出口側ヘッダ流路１５は、プレートフィン積層体１３の一方側（図１では左側）のエンドプレート１２ａの一端部側に設けてある。   The plate fin 11 has a plurality of parallel refrigerant flow path groups through which the refrigerant as the first fluid flows, and the refrigerant flow path groups are formed in a substantially U shape and are connected to this. The inflow side header channel 14 and the outlet side header channel 15 are provided on one end side of the end plate 12a on one side (left side in FIG. 1) of the plate fin laminate 13.

詳述すると、上記プレートフィン１１は、図５〜図７に示すように、複数の並行した冷
媒流路１６とこれに繋がる流入側ヘッダ流路１４および出口側ヘッダ流路１５を形成した一対の板状部材１７ａ、１７ｂ（図７参照）を向い合せにロウ付け接合して構成してあり、複数の冷媒流路１６は略Ｕ字状に形成されていてこれに繋がる流入側ヘッダ流路１４と出口側ヘッダ流路１５とが一端部側に纏まった形となっている。 More specifically, as shown in FIGS. 5 to 7, the plate fin 11 includes a pair of refrigerant flow paths 16 that are parallel to each other, and an inflow side header flow path 14 and an outlet side header flow path 15 that are connected to the parallel flow paths 16. The plate-like members 17a and 17b (see FIG. 7) are brazed and joined to face each other, and the plurality of refrigerant flow paths 16 are formed in a substantially U shape and connected to the inflow side header flow path 14 And the outlet-side header flow path 15 are gathered on one end side.

そして、上記構成のプレートフィン１１は、図４に示すように多数積層して図２、図３に示すプレートフィン積層体１３を構成しており、各プレートフィン１１同士の間には当該プレートフィン１１の長辺両端部及び冷媒流路１６間に列設した複数の突起１８によって空気が流れる隙間１９を形成している。   The plate fins 11 having the above-described configuration are laminated in a large number as shown in FIG. 4 to form the plate fin laminate 13 shown in FIGS. 2 and 3, and the plate fins 11 are arranged between the plate fins 11. A gap 19 through which air flows is formed by a plurality of protrusions 18 arranged between both ends of the long side 11 and the refrigerant flow path 16.

上記突起１８は隣接するプレートフィン１１同士を接合しており、プレートフィン１１を連結する機能も備えている。   The protrusion 18 joins adjacent plate fins 11 and has a function of connecting the plate fins 11.

なお、冷媒流路１６は板状部材１７ａ、１７ｂに凹状溝によって形成してあり、容易に細径化できるようになっている。   The refrigerant flow path 16 is formed by concave grooves in the plate-like members 17a and 17b so that the diameter can be easily reduced.

また、冷媒流路１６のうち流入側ヘッダ流路１４に繋がる往路側冷媒流路１６ａと出口側ヘッダ流路１５に繋がる復路側冷媒流路１６ｂとの間にはこれら両者間の熱移動を防止すべくスリット溝２０が形成してある。   Further, between the refrigerant flow path 16, heat transfer between the forward path refrigerant flow path 16 a connected to the inflow side header flow path 14 and the return path side refrigerant flow path 16 b connected to the outlet side header flow path 15 is prevented. A slit groove 20 is formed as much as possible.

以上のように構成された熱交換器５は、プレートフィン１１間の隙間１９に空気が流れるように傾斜設置されるが、図９、図１０、特に図１０に示すように、傾斜設置したプレートフィン１１の下面側であって、風路４の上流側となる下側端縁に列設した突起１８ａは、全部もしくはその一部、この例では下側端縁の傾斜上方部分に位置する突起１８ａａが下側端縁より内部に位置するように設けてある。   The heat exchanger 5 configured as described above is installed in an inclined manner so that air flows through the gap 19 between the plate fins 11, but as shown in FIGS. The projections 18a arranged on the lower end edge on the lower surface side of the fin 11 on the upstream side of the air passage 4 are all or a part thereof, in this example, the projection located at the inclined upper portion of the lower end edge. 18aa is provided so as to be located inside the lower end edge.

換言すると、この熱交換器５は、傾斜設置した熱交換器５の鉛直下方に水受皿７の開口が存在しない部分、すなわち水受皿７の開口投影範囲外に位置する突起１８ａａをプレートフィン１１の下側端縁より内部に位置する如く設け、水受皿７の開口投影範囲内に位置する突起１８ａｂはプレートフィン１１のフィン下側端縁直近、例えば下側端縁と同一面となるように設けてある。   In other words, the heat exchanger 5 has a portion where the opening of the water receiving tray 7 does not exist vertically below the inclined heat exchanger 5, that is, the protrusion 18 aa located outside the opening projection range of the water receiving tray 7 of the plate fin 11. Provided to be located inside the lower edge, and the protrusion 18ab located within the opening projection range of the water tray 7 is provided in the immediate vicinity of the fin lower edge of the plate fin 11, for example, to be flush with the lower edge. It is.

そして本実施の形態では上記突起１８ａａはプレートフィン１１間の空気が流れる隙間１９の寸法より内部に位置するように設けてある。   In the present embodiment, the protrusion 18aa is provided so as to be positioned inside the dimension of the gap 19 through which the air between the plate fins 11 flows.

さらに、上記プレートフィン１１の上側端縁に列設した突起１８ｂはプレートフィン１１の長辺全域に渡って前記突起１８ａｂと同じようにフィン上側端縁直近に設けてある。   Further, the projection 18b arranged on the upper edge of the plate fin 11 is provided in the vicinity of the fin upper edge in the same manner as the projection 18ab over the entire long side of the plate fin 11.

上記各突起１８ａ、１８ａａ、１８ａｂ、１８ｂの位置関係は図６の拡大平面図に明示している通りである（図中プレートフィン１１の下方が下側端縁、上方が上側端縁となる）。   The positional relationship between the projections 18a, 18aa, 18ab, and 18b is as clearly shown in the enlarged plan view of FIG. 6 (the lower side of the plate fin 11 is the lower side edge and the upper side is the upper side edge in the figure). .

また、上記各突起１８（１８ａ、１８ａａ、１８ａｂ、１８ｂ）の全部もしくは少なくともプレートフィン１１の下側端縁に設けた突起１８ａ（１８ａａ、１８ａｂ）の頂部は略球面状としてある。   Further, all of the projections 18 (18a, 18aa, 18ab, 18b) or at least the tops of the projections 18a (18aa, 18ab) provided on the lower end edge of the plate fin 11 are substantially spherical.

なお、上記熱交換器５の傾斜角度は風路４の構成によって異なり適宜設定すればよいが、結露水の流下（流れ）と滴下の関係を考慮すると垂線に対し２０度〜５０度、好ましくは３０度〜４０度にするのが良い。   The inclination angle of the heat exchanger 5 varies depending on the configuration of the air passage 4 and may be set as appropriate. However, in consideration of the relationship between the flow (flow) of the condensed water and the dripping, it is 20 degrees to 50 degrees, preferably It is good to set it at 30 to 40 degrees.

以上のように構成した空気調和機において、次に結露が発生する冷房運転時の場合を例にしてその作用効果について説明する。   In the air conditioner configured as described above, the operation and effect will be described by taking as an example the case of cooling operation in which condensation occurs next.

まず、冷媒の流れと熱交換作用について説明する。冷媒は、プレートフィン積層体１３の流入側となるヘッダ流路１５から冷媒流路１６群へ流れる。各プレートフィン１１の冷媒流路１６群に流れた冷媒はその往路側となる冷媒流路１６ｂから復路側となる冷媒流路１６ａへと折り返して出口側となるヘッダ流路１４から冷凍システムの冷媒回路へと流れる。   First, the refrigerant flow and heat exchange action will be described. The refrigerant flows from the header flow path 15 on the inflow side of the plate fin laminate 13 to the refrigerant flow path 16 group. The refrigerant that has flowed into the refrigerant flow path 16 group of each plate fin 11 is folded back from the refrigerant flow path 16b on the forward path side to the refrigerant flow path 16a on the return path side, and from the header flow path 14 on the outlet side to the refrigerant of the refrigeration system. It flows into the circuit.

そして、上記冷媒流路１６を流れる際に冷媒は前記プレートフィン積層体１３のプレートフィン積層間の隙間１９を通り抜ける空気と熱交換する。   When the refrigerant flows through the refrigerant flow path 16, the refrigerant exchanges heat with air passing through the gaps 19 between the plate fin stacks of the plate fin stack 13.

この時、上記冷媒が流れる冷媒流路１６はプレートフィン１１に形成した冷媒流路用の凹状溝の断面積を小さくすることによって流路面積の細径化を図ることができ、伝熱管方式の場合に比べその熱交換効率を向上させるとともに小型化を推進することができる。   At this time, the refrigerant flow path 16 through which the refrigerant flows can reduce the diameter of the flow path area by reducing the cross-sectional area of the concave groove for the refrigerant flow path formed in the plate fin 11. Compared to the case, the heat exchange efficiency can be improved and the miniaturization can be promoted.

また、上記熱交換器５はプレートフィン積層間の隙間１９を通り抜ける空気を冷気もしくは暖気に熱交換するが、冷気に熱交換する際には熱交換器５の表面に空気中の水分が結露することがある。この結露水は熱交換器５が傾斜設置してあるので、図９に示すように熱交換器５を構成するプレートフィン１１の下側端縁に沿って下方へと流下するようになる。   Further, the heat exchanger 5 exchanges heat passing through the gaps 19 between the plate fin stacks into cold air or warm air. When heat is exchanged with cold air, moisture in the air is condensed on the surface of the heat exchanger 5. Sometimes. Since the heat exchanger 5 is inclined and installed, the condensed water flows downward along the lower edge of the plate fin 11 constituting the heat exchanger 5 as shown in FIG.

ここで、上記熱交換器５は、プレートフィン積層型熱交換器であるから図１０に示すようにそのプレートフィン１１の端縁部分等にプレートフィン同士間の隙間を形成する突起１８（１８ａ（１８ａａ、１８ａｂ）、１８ｂ）が列設してあるが、結露水が流動するプレートフィン１１の下側端縁の傾斜上方部分に設けてある複数の突起１８ａａは当該下側端縁より内部（奥部）に位置しているから、前記結露水は上記突起１８ａａに触れて引っ掛かることなくプレートフィン１１の下側端縁に沿って下方へと流下する。そしてこの実施の形態ではプレートフィン１１の最下部の突起１８ａｂがフィン下側端縁直近に設けてあるので流下してきた結露水はこの突起１８ａｂに触れて引っ掛かり当該突起部分から下方へと滴下するようになる。   Here, since the heat exchanger 5 is a plate fin laminated type heat exchanger, as shown in FIG. 10, protrusions 18 (18a (18a ( 18aa, 18ab) and 18b) are arranged in a row, but the plurality of protrusions 18aa provided at the inclined upper portion of the lower end edge of the plate fin 11 through which the dew condensation water flows are located on the inner side (rear side) from the lower end edge. Therefore, the condensed water flows downward along the lower edge of the plate fin 11 without being caught by being touched by the protrusion 18aa. In this embodiment, the lowermost protrusion 18ab of the plate fin 11 is provided in the immediate vicinity of the fin lower edge, so that the condensed water that has flowed down is caught by the protrusion 18ab and drops downward from the protrusion. become.

従って、熱交換器５から滴下する結露水を受ける水受皿７は傾斜している熱交換器５の傾斜幅Ｌではなく前記突起１８ａｂまでの幅ｌの狭いものとすることができ、コンパクト化することができる。また、上記の如く水受皿７をコンパクト化できるので、水受皿７の一部が風路４に入り込む形となったり、風路４を狭くせざるを得なくなったりするなどの制約を低減することができ、これが原因で生じる性能劣化等を抑制することもできる。   Therefore, the water receiving tray 7 that receives the dew condensation water dripping from the heat exchanger 5 can be made narrower, not the inclined width L of the inclined heat exchanger 5, but the width l up to the protrusion 18ab, thereby making it compact. be able to. In addition, since the water tray 7 can be made compact as described above, it is possible to reduce restrictions such that a part of the water tray 7 enters the air passage 4 or the air passage 4 has to be narrowed. It is possible to suppress performance degradation caused by this.

また、本実施の形態では、上記した説明から明らかなように、プレートフィン１１の下側端縁に設けた突起１８ａのうち、少なくとも水受皿７と対向しない部分に位置することになる突起１８ａａはプレートフィン１１の下側端縁より内部に設け、水受皿７と対向する部分に位置することになる突起１８ａｂはフィン下側端縁直近に設けた構成となっている。   Further, in the present embodiment, as is clear from the above description, among the protrusions 18a provided on the lower end edge of the plate fin 11, at least the protrusion 18aa that is positioned not facing the water tray 7 is The projection 18ab that is provided inside the lower end edge of the plate fin 11 and is located at a portion facing the water tray 7 is provided in the vicinity of the lower end edge of the fin.

従って、この熱交換器５は、水受皿７と対向する部分のプレートフィン１１の下側端縁の突起１８ａｂが下側端縁直近に位置して比較的強度の弱いフィン端縁の強度を向上させその剛性を高める。そして、この突起１８ａｂを下側端縁直近に設けたことによって突起１８ａｂの更に内部側の熱交換有効面積を増大させることもでき、その分熱交換効率を向上させることができる。   Accordingly, in this heat exchanger 5, the protrusion 18ab on the lower edge of the plate fin 11 facing the water tray 7 is positioned in the immediate vicinity of the lower edge, thereby improving the strength of the relatively weak fin edge. And increase its rigidity. By providing the protrusion 18ab in the vicinity of the lower end edge, the heat exchange effective area on the further inner side of the protrusion 18ab can be increased, and the heat exchange efficiency can be improved accordingly.

詳述すると、図６に示すように、突起をプレートフィン１１の下側端縁直近に設けると、当該下側端縁直近に設けた突起１８ａｂの更に内部側、すなわち冷媒流路１６に近くて熱交換効率が高い熱交換有効面積Ｘは、下側端縁より内部（奥部）に位置するように設けた突起１８ａａの内側の熱交換効率が高い熱交換有効面積Ｙより大きくなる。したがって、その分、熱交換効率が向上する。   More specifically, as shown in FIG. 6, when the protrusion is provided in the vicinity of the lower end edge of the plate fin 11, the protrusion 18 ab provided in the vicinity of the lower end edge further inside, that is, closer to the refrigerant flow path 16. The heat exchange effective area X having a high heat exchange efficiency is larger than the heat exchange effective area Y having a high heat exchange efficiency inside the protrusion 18aa provided so as to be located inside (the back part) from the lower edge. Therefore, the heat exchange efficiency is improved accordingly.

また、突起１８ａ（１８ａａ、１８ａｂ）はそれ自体熱交換に有効に寄与しないので、突起１８ａ（１８ａａ、１８ａｂ）そのものを小さくすればプレートフィン１１の熱交換に寄与する熱交換面積を増加させることができ、熱交換効率を一段と向上させることができる。よって突起１８ａ（１８ａａ、１８ａｂ）はこれ以外の突起１８ｂも含め必要最小限の大きさまで小さくしておくのが好ましい。   Further, since the protrusions 18a (18aa, 18ab) themselves do not contribute effectively to heat exchange, if the protrusions 18a (18aa, 18ab) themselves are made smaller, the heat exchange area contributing to the heat exchange of the plate fins 11 can be increased. And the heat exchange efficiency can be further improved. Therefore, it is preferable that the protrusion 18a (18aa, 18ab) is made small to the minimum necessary size including the other protrusion 18b.

このように、本実施の形態の如くプレートフィン１１の下側端縁に設ける突起列のうち一つでも下側端縁直近に設ければ、プレートフィン１１の剛性向上と熱交換効率の向上を両立させることができる。   As described above, if one of the protrusion rows provided on the lower end edge of the plate fin 11 is provided in the vicinity of the lower end edge as in the present embodiment, the rigidity of the plate fin 11 and the heat exchange efficiency are improved. Both can be achieved.

また、上記プレートフィン１１の下側端縁より内部に設ける突起１８ａａの下側端縁から内部側への寸法Ｚは、プレートフィン１１同士間の隙間１９（図４参照）の隙間分寸法より内部に設けた構成としてあるから、結露水がプレートフィン１１の下側端縁のフィンプレート１１間の隙間１９に跨って流下してきても、突起１８ａａに触れるようなことがなくそのまま下方部分へと流下していくようになる。したがって、上記水受皿７と対向しない傾斜上方部分に設けてある突起１８ａａに結露水が引っかかるような状態となって当該突起１８ａａを起点として結露水が滴下するのを防止でき、より確実な滴下防止を実現することができる。   Further, the dimension Z from the lower end edge of the projection 18aa provided inside from the lower end edge of the plate fin 11 to the inner side is larger than the dimension of the gap 19 between the plate fins 11 (see FIG. 4). Therefore, even if condensed water flows down across the gap 19 between the fin plates 11 at the lower edge of the plate fin 11, it does not touch the projection 18aa and flows down to the lower portion as it is. Will come to do. Therefore, it is possible to prevent the condensed water from dripping from the protrusion 18aa as a starting point when the condensed water is caught on the protrusion 18aa provided on the inclined upper portion that does not face the water tray 7, and more reliable prevention of dripping. Can be realized.

また、上記各突起１８（１８ａ、１８ａａ、１８ａｂ、１８ｂ）は図８に示すようにその頂部は略球面状としてあるから、プレートフィン１１の下側端縁を流下する結露水の一部が突起１８ａａに触れるようなことがあっても突起１８ａａの頂部が略球面状となっているから当該頂部に引っかかりにくくなりそのままフィン下側端縁に沿って流下し、突起１８ａａを起点とした結露水の滴下をより確実に防止することができる。   Further, since each of the protrusions 18 (18a, 18aa, 18ab, 18b) has a substantially spherical shape as shown in FIG. 8, a part of the condensed water flowing down the lower edge of the plate fin 11 protrudes. Even if it touches 18aa, the top of the projection 18aa has a substantially spherical shape, so it is difficult to get caught by the top and flows down along the lower edge of the fin as it is. Dripping can be prevented more reliably.

また、この熱交換器５は、プレートフィン１１の下側端縁とともに上側端縁にも突起１８ｂを列設し、上記上側端縁の突起１８ｂは上側端縁直近に設けた構成としてあるから、プレートフィン１１の上側端縁部分の剛性を高めるとともに熱交換有効面積の増大によって熱交換効率を向上させることができ、より効果的にプレートフィン１１の剛性向上と熱交換効率の向上を両立させることができる。   Further, this heat exchanger 5 has a configuration in which protrusions 18b are arranged on the upper edge as well as the lower edge of the plate fin 11, and the protrusion 18b on the upper edge is provided in the immediate vicinity of the upper edge. It is possible to increase the rigidity of the upper edge portion of the plate fin 11 and improve the heat exchange efficiency by increasing the heat exchange effective area, and more effectively achieve both the rigidity improvement of the plate fin 11 and the heat exchange efficiency. Can do.

また、この実施の形態では、上記熱交換器５はそのプレートフィン１１の下側端縁部分が風路４の上流側に位置するように配置してあるから、プレートフィン１１の下側端縁を流下する結露水の重力による落下作用が抑制されるようになり、結露水はプレートフィン１１のより下方部分から滴下するようになる。したがって、水受皿７を更にコンパクトなものにすることができる。しかも、プレートフィン１１の下側端縁直近に設ける突起１８ａｂの数を増やして剛性と熱交換効率をより高めることができる。   In this embodiment, the heat exchanger 5 is arranged so that the lower edge portion of the plate fin 11 is located on the upstream side of the air passage 4. The falling action due to the gravity of the dew condensation water flowing down is suppressed, and the dew condensation water drops from the lower part of the plate fin 11. Therefore, the water tray 7 can be made more compact. In addition, the number of protrusions 18ab provided near the lower end edge of the plate fin 11 can be increased to further increase the rigidity and heat exchange efficiency.

（実施の形態２）
図１１は実施の形態２におけるプレートフィンの突起を示し、この実施の形態では、プレートフィン１１に設けた突起１８（１８ａ、１８ａａ、１８ａｂ、１８ｂ）は図１１に示すように冷媒流路１６に沿った形で切り起こし形成し、その切り起こし端縁Ｙがプレートフィン１１の積層間を流れる空気の流れ方向Ｗと対向するようにしてある。 (Embodiment 2)
FIG. 11 shows the projections of the plate fins according to the second embodiment. In this embodiment, the projections 18 (18a, 18aa, 18ab, 18b) provided on the plate fins 11 are formed in the coolant channel 16 as shown in FIG. The cut and raised edge Y is formed so as to face the flow direction W of the air flowing between the stacked plate fins 11.

これにより、この突起１８（１８ａ、１８ａａ、１８ａｂ、１８ｂ）は、プレートフィン積層間の間隔を一定化すると同時に、突起１８（１８ａ、１８ａａ、１８ａｂ、１８ｂ）の下流側に生じがちな死水域を極小とし、かつ、切り起こし端縁Ｙ部分で前縁効果を生じさせることができる。しかも切り起こし端縁Ｙ部分が空気の流れ方向Ｗと対向するので、空気に対する流れ抵抗も小さなものとすることができる。したがって、プレートフィン積層体１３の流路領域における流路抵抗増大を抑制しつつその熱交換効率を一段と向上させることができる。   As a result, the projection 18 (18a, 18aa, 18ab, 18b) stabilizes the interval between the plate fins, and at the same time, forms a dead water area that tends to occur downstream of the projection 18 (18a, 18aa, 18ab, 18b). The leading edge effect can be generated at the cut-and-raised edge Y portion. Moreover, since the cut and raised edge Y portion faces the air flow direction W, the flow resistance against air can be reduced. Accordingly, it is possible to further improve the heat exchange efficiency while suppressing an increase in the flow resistance in the flow path region of the plate fin laminate 13.

さらに、上記突起１８（１８ａ、１８ａａ、１８ａｂ、１８ｂ）の切り起こしは、プレートフィン積層体１３の冷媒流路１６に沿うように形成しているので、冷媒流路１６と交差する方向の冷媒流路間の窪み平面２１から切り起こし用の肉盗みをする必要がなくなる。したがって、突起１８（１８ａ、１８ａａ、１８ａｂ、１８ｂ）を円柱状に***させて形成するものに比べ冷媒流路同士の間の窪み平面寸法を肉盗み寸法不要な分だけ狭いものとすることができ、その分プレートフィン１１、換言すると熱交換器を小型化することができる。   Furthermore, since the protrusion 18 (18a, 18aa, 18ab, 18b) is formed along the refrigerant flow path 16 of the plate fin laminate 13, the refrigerant flow in the direction intersecting with the refrigerant flow path 16 is formed. It is no longer necessary to cut and raise the meat from the hollow plane 21 between the roads. Therefore, compared to the case where the protrusions 18 (18a, 18aa, 18ab, 18b) are formed in a columnar shape, the hollow plane dimension between the refrigerant flow paths can be narrowed by an amount not requiring the meat stealing dimension. Accordingly, the plate fin 11, in other words, the heat exchanger can be reduced in size.

その他の構成、作用効果は実施の形態１と同様であり、説明は省略する。   Other configurations and operational effects are the same as those of the first embodiment, and a description thereof will be omitted.

以上、本発明に係る空気調和機について、上記実施の形態を用いて説明したが、本発明は、これに限定されるものではない。つまり、今回開示された実施の形態はすべての点で例示であって制限的なものではないと考えられるべきであり、本発明の範囲は上記した説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味及び範囲内でのすべての変更が含まれることが意図される。   As mentioned above, although the air conditioner concerning the present invention was explained using the above-mentioned embodiment, the present invention is not limited to this. That is, the embodiment disclosed this time should be considered as illustrative in all points and not restrictive, and the scope of the present invention is indicated by the scope of the claims, not the above description, It is intended that all modifications within the meaning and scope equivalent to the terms of the claims are included.

本発明は、上記実施の形態の説明から明らかなように、高い熱交換効率を持ち、かつ、コンパクトで高性能な空気調和機を提供することができる。よって、家庭用はもちろん、業務用の空気調和機にも広く適用することができる。   As is apparent from the above description of the embodiment, the present invention can provide a compact and high-performance air conditioner having high heat exchange efficiency. Therefore, it can be widely applied to air conditioners for business use as well as home use.

１ 本体
２ 吸込口
３ 吹出口
４ 風路
５ 熱交換器
６ 送風機
７ 水受皿
１１ プレートフィン
１２ａ、１２ｂ エンドプレート
１３ プレートフィン積層体
１４ 流入側ヘッダ流路
１５ 出口側ヘッダ流路
１６ 冷媒流路
１６ａ 往路側冷媒流路
１６ｂ 復路側冷媒流路
１７ａ、１７ｂ 板状部材
１８、１８ａ、１８ａａ、１８ａｂ、１８ｂ 突起
１９ 隙間
２０ スリット溝
２１ 窪み平面
DESCRIPTION OF SYMBOLS 1 Main body 2 Inlet 3 Outlet 4 Air path 5 Heat exchanger 6 Blower 7 Water receiving tray 11 Plate fin 12a, 12b End plate 13 Plate fin laminated body 14 Inlet side header flow path 15 Outlet side header flow path 16 Refrigerant flow path 16a Outbound refrigerant flow path 16b Return path refrigerant flow path 17a, 17b Plate member 18, 18a, 18aa, 18ab, 18b Protrusion 19 Clearance 20 Slit groove 21 Recess plane

Claims (6)

本体内の風路に設置した熱交換器と、前記熱交換器に送風する送風機と、前記熱交換器の下部に設置した水受皿と、を備え、前記熱交換器はプレートフィンを積層するとともに当該プレートフィンに設けた突起によりプレートフィン間に隙間を形成して構成したプレートフィン積層型熱交換器とし、かつこのプレートフィン積層型熱交換器を垂線に対し傾斜させて設置するとともに、前記プレートフィン積層型熱交換器のプレートフィン下側端縁に列設した突起は当該下側端縁より内部に設けた空気調和機。   A heat exchanger installed in an air passage in the body, a blower that blows air to the heat exchanger, and a water tray installed at a lower portion of the heat exchanger, the heat exchanger stacking plate fins The plate fin laminated heat exchanger is configured by forming a gap between the plate fins by the protrusions provided on the plate fin, and the plate fin laminated heat exchanger is installed to be inclined with respect to the vertical line, and the plate An air conditioner in which the protrusions arranged on the lower end edge of the plate fin of the fin-stacked heat exchanger are provided inside the lower end edge. 突起はプレートフィンの下側端縁より前記プレートフィン間の隙間分寸法より内部に設けた請求項１記載の空気調和機。   The air conditioner according to claim 1, wherein the protrusion is provided in an inner portion from a lower end edge of the plate fin than a gap between the plate fins. 突起はその頂部を略球面状とした請求項１または２記載の空気調和機。   The air conditioner according to claim 1 or 2, wherein the protrusion has a substantially spherical top. 突起はプレートフィンの下側端縁の少なくとも鉛直下方に水受皿が存在しない部分の突起を当該下側端縁より内部に設けた請求項１〜３のいずれか１項に記載の空気調和機。   The air conditioner according to any one of claims 1 to 3, wherein the protrusion is provided with a protrusion at a portion where no water tray is present at least vertically below the lower end edge of the plate fin from the lower end edge. プレートフィンは下側端縁とともに上側端縁にも突起を列設し、上記上側端縁の突起は当該上側端縁直近に設けた請求項１〜４のいずれか１項に記載の空気調和機。   The air conditioner according to any one of claims 1 to 4, wherein the plate fin is provided with a protrusion on the upper edge along with the lower edge, and the protrusion on the upper edge is provided in the immediate vicinity of the upper edge. . 熱交換器はそのプレートフィンの下側端縁部分が風路の上流側に位置するように配置した請求項１〜４のいずれか１項に記載の空気調和機。
The air conditioner according to any one of claims 1 to 4, wherein the heat exchanger is disposed such that a lower end edge portion of the plate fin is positioned on the upstream side of the air passage.
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JP2007078280A (en) * 2005-09-15 2007-03-29 Denso Corp Heat exchanger for cooling
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JP2013200119A (en) * 2013-07-02 2013-10-03 Mitsubishi Electric Corp Finned tube heat exchanger and refrigeration cycle apparatus using the same

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