JP3361405B2

JP3361405B2 - Outdoor unit of air conditioner

Info

Publication number: JP3361405B2
Application number: JP07788895A
Authority: JP
Inventors: 秀明鈴木; 宏二和田; 孝柿木
Original assignee: Toshiba Carrier Corp
Current assignee: Toshiba Carrier Corp
Priority date: 1995-04-03
Filing date: 1995-04-03
Publication date: 2003-01-07
Anticipated expiration: 2018-01-07
Also published as: KR100189000B1; KR960038339A; GB2299656B; GB9603896D0; CN1149117A; TW367019U; JPH08270985A; CN1100238C; GB2299656A

Description

【発明の詳細な説明】【０００１】【産業上の利用分野】本発明は、空気調和機の室外ユニ
ットに係り、特に、室外熱交換器構成の改良に関する。【０００２】【従来の技術】普通用いられる空気調和機は、被空調室
に取付けられる室内ユニットと、建屋外部に据付けられ
る室外ユニットとを、冷媒管や電気配線等を介して接続
してなる。室外ユニットは、建屋の壁面に可能な限り近
接して据付けられ、邪魔にならないように配慮される。【０００３】この室外ユニットのユニット本体内部に
は、室外熱交換器、送風機、圧縮機、配管部品および電
気部品箱などが収容配置される。そして、特に室外熱交
換器において、熱交換能力の向上を達成するために熱交
換器の容量を多くすることが検討されている。【０００４】その結果、図８に示すように、平面視で略
Ｌ字状に曲成され、互いにほぼ同形の第１の熱交換器ａ
と第２の熱交換器ｂを並列に配置してなる室外熱交換器
Ｓが案出された。【０００５】なお、筐体であるユニット本体ｃは、その
背面部と側面部に外気吸込み口ｄ，ｅが設けられ、前面
部には吹出し口ｆが設けられる。上記室外熱交換器Ｓは
平面視でＬ字状に形成されるので、上記各外気吸込み口
ｄ，ｅに直接対向する。【０００６】吹出し口ｆには、プロペラファンｇを備え
た送風機ｈが対向して配置されており、図中矢印に示す
ように、各外気吸込み口ｄ，ｅから外気を吸込んで室外
熱交換器Ｓと熱交換させ、吹出し口ｆから吹出すように
なっている。【０００７】【発明が解決しようとする課題】このような第１の熱交
換器ａと第２の熱交換器ｂを備えることによって、見掛
け上は、熱交換器単体のものよりも、熱交換器容量が２
倍に増大する。【０００８】しかしながら、熱交換器容量の２倍化にと
もなって、熱交換能力が単純に２倍にはならない。すな
わち、容量増加に対応して風量も増加させなければ、熱
交換能力は増加せず、この場合には上記送風機ｈおよび
ファンｇをより大型化あるいは回転数を上げて、熱交換
能力に対応した熱交換空気風量を確保しなければならな
い。【０００９】加えて上記プロペラファンｇは、回転軸に
平行な方向である背面側において、その風量と風速は大
である。これに対し、ファンｇの回転軸に垂直な方向で
ある側面側において、風量と風速は小である。【００１０】したがって、図８のように熱交換器Ｓの容
量を増加した場合、風量／風速が比較的少ない側面側に
おける容量増加分に応じた風量を確保するためには、上
記送風機ｈおよびファンｇをさらに大型化したり、ある
いは回転数を上げる必要がある。【００１１】このように送風機ｈおよびファンｇをより
大型化したならば、これにともなってユニット本体ｃも
大型化してしまい、筐体の小型化が望まれる現状ではデ
メリットになる。また、回転数を上げたならば、送風騒
音も増加してしまう。【００１２】このような条件から、図９に示すような室
外熱交換器Ｓａが考えられた。すなわち、第２の熱交換
器ｂのみ先のものと同様、平面視でＬ字状に形成され
る。新たな第１の熱交換器ｊは直状にして、背面部吸込
み口ｄに沿うよう配置される。（図８と同一部品は、同
番号を付して新たな説明を省略）なお説明すれば、第１の熱交換器ｊは第２の熱交換器ｂ
の直状部位に平行に配置される。熱交換空気の気流を基
準にすると、第１の熱交換器ｊは第２の熱交換器ｂの下
流側になる。【００１３】この場合は、側面側の熱交換器を増加せ
ず、背面側の熱交換器容量のみ増加することとなり、熱
交換器容量の増大を図れる。そして、側面側の熱交換器
が少なくなった分、プロペラファンｇの直径を大きくで
き、風量の増加を得られる。【００１４】したがって、筐体寸法を大きくすることな
く、熱交換器容量および風量の増加が可能となる。【００１５】しかるに、背面部の外気吸込み口ｄから吸
込まれた熱交換空気のうち、特に第２の熱交換器ｂの曲
成部を通過した熱交換空気部分は、この下流側に位置す
る第１の熱交換器ｊのＵパイプｋに導かれて乱流の発生
するところとなり、騒音が大きくなるなどの不具合があ
る。【００１６】本発明は、上記事情に鑑みなされたもので
あり、その目的とするところは、熱交換器容量を増加し
て熱交換能力の増大化を図り、併せて熱交換器を通過す
る熱交換空気に対する通風抵抗の均一化による騒音低減
を得られる空気調和機の室外ユニットを提供しようとす
るものである。【００１７】【課題を解決するための手段】上記目的を満足するため
の本発明の空気調和機の室外ユニットは、筐体からな
り、その背面部と少なくとも１つの側面部に外気吸込み
口が開口され、かつ前面部に吹出し口が開口されるユニ
ット本体と、このユニット本体内に配置される室外熱交
換器と、外気吸込み口を介して室外熱交換器へ外気を導
びき、ここで熱交換した後、吹出し口から外部へ吹出す
ため吹出し口に対向して配置されたプロペラファンを備
えた送風機とを具備し、上記室外熱交換器は、狭小の間
隙を存して並設される多数枚のフィンに、冷媒が導かれ
る熱交換パイプを貫通させたフィンドチューブタイプで
あって、背面部と側面部の外気吸込み口に対向するよう
平面視で略Ｌ状に折り曲げ形成されるとともに送風機を
囲むように配置された第１の熱交換器と、第１の熱交換
器における熱交換空気の上流側で、背面部の外気吸込み
口との間に背面部外気吸込み口に沿う直状部分と並行に
介設され、平面視で直状に形成される第２の熱交換器と
からなり、上記第１の熱交換器における側面部の外気吸
込み口に対向する部分のフィンピッチを、背面部の外気
吸込み口に対向する部分のフィンピッチよりも細かく設
定した。【００１８】【００１９】【００２０】【００２１】【００２２】【００２３】さらに、上記第１の熱交換器において、側
面部の外気吸込み口に対向する部分のフィンピッチを、
背面部の外気吸込み口に対向する部分のフィンピッチよ
りも細かく設定した。【００２４】【作用】上記室外熱交換器は、第１の熱交換器がユニッ
ト本体の背面部と側面部の外気吸込み口に対向するよう
平面視で折り曲げ形成され、かつ送風機を囲むよう配置
され、第２の熱交換器は、第１の熱交換器の上流側で、
背面部の外気吸込み口との間に介設され、平面視で直状
に形成される。【００２５】したがって、プロペラファンの直進方向の
送風量が多い背面側に２列の熱交換器を配置し、側面側
に１列の熱交換器を配置することとなり、背面側と側面
側において通風抵抗が均一化して送風量と熱交換器の熱
交換量のバランスをとることができ、熱交換能力の増大
化が図れる。また、送風機に面する側には、側面側から
背面側に至る熱交換器がＬ字状で連続形成され、熱交換
器を通過した風が端板部分で乱流が発生することがな
く、騒音低減が図れる。【００２６】【実施例】以下、本発明の一実施例を、図面を参照して
説明する。【００２７】図１に、空気調和機を構成する室外ユニッ
トを示す。【００２８】ユニット本体１は、前面部、後板および底
板を一体に組合わせた筐体である。この前面部にはベル
マウス２が設けられ、熱交換空気の吹出し口３が形成さ
れる。背面部と一方の側面部には熱交換空気の吸込み口
４，５が設けられる。【００２９】ユニット本体１内には、吸込み口４，５に
沿うようにして室外熱交換器６が配置される。【００３０】上記室外熱交換器６は、背面部と側面部の
外気吸込み口４，５に対向するよう平面視で略Ｌ字状に
折り曲げ形成される第１の熱交換器７と、この第１の熱
交換器における背面部外気吸込み口４に沿う直状部分に
並行で、かつ背面部外気吸込み口側に沿って配置される
直状の第２の熱交換器８とから構成される。【００３１】各熱交換器７，８とも、狭小の間隙を存し
て並設される多数枚のフィン９…に、そして、一側端の
フィン９から突出する熱交換パイプ１０部分はＵ字状１
１に折り曲げ形成され、他側端のフィン９から突出する
熱交換パイプ１０部分は図示しないＵベンドを介して連
通される、いわゆるフィンドチューブタイプである。【００３２】第１の熱交換器７の他側端フィン９と、第
２の熱交換器８の両側端フィン９，９は、背面部外気吸
込み口４の他側端もしくは両側端に正しく対向してい
る。また、第１の熱交換器７の一側端フィン９は、側面
部外気吸込み口５の一側端に正しく対向している。【００３３】このことから、各熱交換器７，８における
熱交換パイプ１０のＵ字状部１１およびＵベンド部分は
全て外気吸込み口４，５から外れた部分に対向してお
り、いずれも後述するように、各吸込み口から導入され
る外気に直接さらされることはない。【００３４】上記吹出し口３と室外熱交換器６を構成す
る第１の熱交換器７との間に、室外送風機１２が介設さ
れる。この送風機１２は、熱交換器７側に設けられる支
持台１３に支持されるファンモータ１４と、このモータ
の回転軸に嵌着され、かつベルマウス２に形成される吹
出し口３と対向するプロペラファン１５とからなる。【００３５】そして、ファンモータ１４の駆動によって
プロペラファン１５が回転すると、図に矢印で示すよう
に、背面部および側面部の外気吸込み口４，５から外気
がユニット本体１内に導かれ、室外熱交換器６を介して
ユニット本体１内を横断し、かつ吹出し口３からユニッ
ト本体外へ吹出されるようになっている。【００３６】ユニット本体１内における熱交換空気の流
れから、背面部外気吸込み口４を対象としてみると、上
流側に第２の熱交換器８が位置し、この下流側に第１の
熱交換器７の吸込み口４対向部分が位置することにな
る。【００３７】図２に示すように、第１の熱交換器７を構
成する熱交換パイプ１０Ｐａの直径φｄa は、第２の熱
交換器８を構成する熱交換パイプ１０Ｐｂの直径φｄb
よりも大に設定される。なお、互いの熱交換パイプ１０
Ｐａ，１０Ｐｂのパイプピッチは同一であり、互いに熱
交換空気の気流方向に沿って並行に配置される。【００３８】再び図１に示すように、上記ユニット本体
１内には、第１の熱交換器７側端部とベルマウス２近傍
とに亘って仕切り板１６が設けられ、ユニット本体１内
部を二分している。【００３９】一方の空間室に上記室外熱交換器６および
室外送風機１２が配置される熱交換室１７が形成され
る。他方の空間室には圧縮機１８が配置されていて、圧
縮機室１９が形成される。さらに、圧縮機室１９側部に
は室内ユニットから延出される冷媒管を接続するための
パックドバルブ２０が設けられる。圧縮機１２の上方部
位には、インバ−タなどを収納した電気部品箱やリアク
タなどの電気部品（いずれも図示しない）が配置され
る。【００４０】このようにして構成される空気調和機の室
外ユニットであって、圧縮機１８の運転駆動が開始され
るとともに室外送風機１２の駆動が開始される。両外気
吸込み口４，５から外気がユニット本体１内に導かれ、
室外熱交換器６に導かれる冷媒と熱交換をなす。【００４１】室外熱交換器６に導かれる冷媒は、冷房運
転時には凝縮し、暖房運転時には蒸発して、それぞれ導
出される。背面部外気吸込み口４からユニット本体１内
に導かれる外気は、はじめ第２の熱交換器８と熱交換
し、ついで第１の熱交換器７と熱交換して、吹出し口３
から吹出される。側面部外気吸込み口５からユニット本
体１内に導かれる外気は、ここには第２の熱交換器８が
存在しないところから、第１の熱交換器７と熱交換して
吹出し口３から吹出される。【００４２】しかして、第１の熱交換器７と第２の熱交
換器８とから構成される室外熱交換器６の熱交換容量の
増大とともに、以下に述べるような送風量の増大にとも
ない、図８に示すような単純に熱交換容量を２倍にした
だけの従来のもの以上の熱交換能力の増大が見込まれる
上に、図９に示すような配置のものに比べ送風騒音の低
減も達成される。【００４３】すなわち、室外送風機１２を構成するプロ
ペラファン１５は、ファンの回転軸に平行な方向である
ユニット本体１背面部方向の風量／風速は大であり、こ
れに対してファンの回転軸に垂直な方向であるユニット
本体側面部方向の風量／風速は小である。【００４４】本発明においては、ユニット本体１背面部
の外気吸込み口４に対向して、第２の熱交換器８および
第１の熱交換器７を配置し、側面部吸込み口５に対して
は第１の熱交換器７のみ配置してある。【００４５】すなわち、ファン１５の風量／風速が大な
る位置に対向して二組の熱交換器をに配置し、ファンの
風量／風速が小なる位置に対向して一組の熱交換器を配
置したので、ほぼ二倍の熱交換器容量の増大化と、それ
に見合う熱交換能力の増大化が得られることとなる。【００４６】そして、風速が大である背面側に通風抵抗
となる熱交換器を増やし、風速が小である側面側には熱
交換器を増やさないので、各外気吸込み口４，５から各
熱交換器７，８を介してファン１５に流入する熱交換空
気の風速は均一化され、これまでのような風速のアンバ
ランスによって生じていた送風騒音が低減される。【００４７】特に、上流側に位置する第２の熱交換器８
は、そのＵ字状部１１およびリターンベンドが背面部外
気吸込み口４から外れた位置にあり、吸込み口から導入
される外気に直接さらされないところから乱流が発生せ
ず、したがって騒音低減に寄与する構造となる。【００４８】なお、図２に示すように、下流側に位置す
る第１の熱交換器７の熱交換パイプ１０Ｐａの直径φｄ
a を大、上流側に位置する第２の熱交換器８の熱交換パ
イプ１０Ｐｂの直径φｄb を小に形成した。【００４９】先に説明したように、プロペラファン１５
において、風速が側面側＜背面側であるが、その差は２
倍には至らない。たとえば、第２の熱交換器８の熱交換
パイプ直径を第１の熱交換器７の熱交換パイプ直径に同
一に合わせ、しかも互いの位置を異ならせたいわゆる千
鳥状に配置すると、通風抵抗は略２倍になってしまう。
そして、今度は風速が側面側＞背面側となり、再び風速
がアンバランスになって騒音が発生する。【００５０】本発明においては、風速の速い背面側にの
み熱交換器を増加するのだが、上流側の第２の熱交換器
８の熱交換パイプ直径φｄb を小、下流側の第１の熱交
換器７の熱交換パイプ直径φｄa を大に形成することに
より、通風抵抗を極力抑制することを可能化して、側面
側＜背面側の風速を保持し騒音低減を得る。【００５１】そしてまた、各熱交換器７，８の熱交換パ
イプ１０Ｐａ，１０Ｐｂを気流の方向に平行に配置した
ので、さらに通風抵抗の抑制に寄与することとなる。【００５２】なお、このようにして熱交換パイプ１０Ｐ
ａ，１０Ｐｂを平行に配置すると、上流側の熱交換パイ
プ１０Ｐｂの真後ろに下流側の熱交換パイプ１０Ｐａが
配置されることになり、上流側の熱交換パイプ１０Ｐｂ
による温度境界層が発達して下流側の熱交換パイプ１０
Ｐａでの熱交換効率が低下するように思われるが、上流
側の熱交換パイプ直径φｄb が下流側熱交換パイプ直径
φｄa に比較して小さいことと、第１，第２の熱交換器
７，８を構成するフィン９…が互いに完全に分離してい
るから、熱交換効率の低下はない。逆に通風抵抗が増加
しない分だけメリットが大きい。【００５３】本発明において、上記室外熱交換器６が、
冷房運転時に凝縮器として作用する場合、先に冷媒を第
１の熱交換器７に導き、ついで第２の熱交換器８に導く
ように設定してある。【００５４】すなわち、室外熱交換器６を凝縮器とする
と、この流入側において冷媒は圧縮機１８から吐出され
た後であるから、過熱ガス状態になっている。この熱交
換器６と熱交換されることによって、冷媒状態が過熱ガ
スから気液二相、過冷却状態へと相変化していく。【００５５】この場合、過熱ガス、あるいは乾き度が大
きい二相状態（ガスが占める割合が大きい）では圧力損
失が大きいが、先に冷媒が導かれる第１の熱交換器７の
熱交換パイプ直径φｄa を大きく設定したので、圧力損
失が増大することなく、熱交換効率を損なうことがな
い。【００５６】一方、熱交換器６の流出側においては、冷
媒は凝縮して気液二相冷媒もしくは液冷媒となってお
り、乾き度が小さい。このような状態の冷媒では圧力損
失が小さいので、熱交換パイプ直径を細くしても充分に
熱交換効率を上げられる。すなわち、流出側である第２
の熱交換器８の熱交換パイプ直径φｄb を小さく設定し
たことに一致する。【００５７】したがって、先に述べたような本発明の第
１，第２の熱交換器７，８構成と、冷媒の導通方向の設
定により、室外熱交換器６におけるさらなる熱交換効率
の向上が得られることとなる。【００５８】図３に示すような室外熱交換器６Ａであっ
てもよい。下流側に位置する第１の熱交換器７Ａの熱交
換パイプ１０Ｐａの直径φｄa を大、上流側に位置する
第２の熱交換器８Ａの熱交換パイプ１０Ｐｂの直径φｄ
b を小に形成することを前提として、互いの熱交換器７
Ａ，８Ａの熱交換パイプ１０Ｐａ，１０Ｐｂを千鳥状に
配置する。【００５９】この場合、少なくとも従来の室外熱交換器
よりも通風抵抗を低減させることができ、風量の増加が
得られる。そして、熱交換器単位面積あたりの風速が上
がって熱交換効率の向上につながる。【００６０】図４に示すような室外熱交換器６Ｂであっ
てもよい。下流側に位置する第１の熱交換器７Ｂの熱交
換パイプ１０Ｐａの直径φｄa を大、上流側に位置する
第２の熱交換器８Ｂの熱交換パイプ１０Ｐｂの直径φｄ
b を小に形成することを前提として、第１の熱交換器７
Ｂの熱交換パイプピッチＰＰｃを大、第２の熱交換器８
Ｂの熱交換パイプピッチＰＰｄを小に設定してもよい。【００６１】この場合、室外熱交換器６Ｂ全体としての
通風抵抗の増加が避けられず、風量の低下がみられる
が、特に第２の熱交換器８Ｂにおける熱交換パイプ１０
Ｐａの本数が増加するので、熱交換性能の向上を得られ
る。【００６２】図５に示すような、室外熱交換器６におけ
る流路構成であってよい。ここでは、冷房運転時におけ
る凝縮器としての流路構成を示す。【００６３】第１の熱交換器７の一側端部に流入する冷
媒は、そのままこの熱交換器の中間部まで導かれ、ここ
から一旦熱交換器外部へ出て、第２の熱交換器８の一側
端部に流入する。そして、第２の熱交換器８の中間部ま
で導かれ、ここから熱交換器外部へ導出される第１のパ
スＰ1 がある。【００６４】また、第１の熱交換器７の中間部に流入す
る冷媒は、そのままこの熱交換器の他端部まで導かれ、
ここから一旦熱交換器外部へ出て、第２の熱交換器８の
中間部に流入する。そして、第２の熱交換器８の他端部
まで導かれ、ここから熱交換器外部へ導出される第２の
パスＰ2 がある。【００６５】すなわち、第１の熱交換器７と第２の熱交
換器８の熱交換パイプに形成される流路は２パスＰ1 ，
Ｐ2 に設定されており、それぞれのパスに独立して冷媒
が導かれることとなる。【００６６】本発明のように熱交換器容量を増やした場
合に、単純に冷媒流路を１パスに設定すると、流路長が
極めて長くなり圧力損失の増大がある。そこで、圧力損
失の低減を得るために、先に説明したような完全に独立
した２パスの設定をなす。【００６７】それぞれのパスＰ1 ，Ｐ2 における冷媒流
出側が第２の熱交換器８であって、この熱交換パイプ直
径φｄb は第１の熱交換器７における熱交換パイプ直径
φｄa よりも小であるのが前提であり、したがって圧力
損失が小さくてすむので、各パスの途中でさらにパスを
増やす（２パスから４パス）必要がない。【００６８】図６に示すように、第１の熱交換器７Ｃを
構成するフィン９…のフィンピッチＰＰｅを細かく、第
２の熱交換器８Ｃを構成するフィン９…のフィンピッチ
ＰＰｆを粗く設定する。すなわち、第２の熱交換器フィ
ンピッチＰＰｆは第１の熱交換器フィンピッチＰＰｅよ
りも粗い。【００６９】繰り返し説明したように、プロペラファン
１５を用いると側面側の風速よりも背面側の風速が速
い。ただし、２倍の差まではないので、同一直径の熱交
換パイプを配置して通風抵抗を２倍にすると、今度は側
面側＞背面側の風速関係となってしまい、再び風速がア
ンバランスになって騒音が発生する。【００７０】そこで、図に示すように背面部風上側列の
第２の熱交換器８Ｃでの通風抵抗が増大しないようにフ
ィンピッチＰＰｆを粗くすると、側面側と背面側との風
速のバランスがとれて騒音の発生には至らずにすむ。【００７１】図７に示すように、第１の熱交換器７Ｄ
は、背面部外気吸込み口４に対向する対向部７ｅのフィ
ンピッチＰＰｇを粗く、側面部外気吸込み口５に対向す
る対向部７ｆのフィンピッチＰＰｈを細かく設定しても
よい。【００７２】すなわち、第１の熱交換器７Ｄの背面部外
気吸込み口４に沿う部分７ｅに第２の熱交換器８を並設
したので、背面側の通風抵抗が増加する。そこで、背面
側と側面側の通風抵抗を一致させるために、側面側のフ
ィンピッチＰＰｈを細かく設定した。したがって、側面
側と背面側との風速が均一になり、風速の不均一による
騒音の防止に役立つ。【００７３】なお上記各実施例において、第１の熱交換
器７〜７Ｄを平面視でＬ字状に形成したが、これに限定
されるものではなく、プロペラファンを囲むような平面
視でＵ字状に形成しても何ら支障がない。【００７４】【発明の効果】以上説明したように本発明によれば、背
面側と側面側の通風抵抗を一致させるようフィンピッチ
の間隔を設定して、背面側と側面側における通風抵抗を
均一化させたので、送風量と熱交換器の熱交換量のバラ
ンスをとることができ、熱交換能力の増大化が図れる。
そして、送風機に面する側には、側面側から背面側に至
る熱交換器がＬ字状で連続形成され、熱交換器を通過し
た風が端板部分で乱流が発生することがなく、騒音低減
が図れるなどの効果を奏する。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an outdoor unit of an air conditioner, and more particularly to an improvement in an outdoor heat exchanger. 2. Description of the Related Art An air conditioner commonly used is configured by connecting an indoor unit installed in a room to be air-conditioned and an outdoor unit installed in an outdoor part of a building via a refrigerant pipe, electric wiring, or the like. The outdoor unit is installed as close as possible to the wall surface of the building, and care is taken so as not to interfere. [0003] An outdoor heat exchanger, a blower, a compressor, piping parts, an electric parts box and the like are accommodated and arranged inside a unit body of the outdoor unit. In particular, in the outdoor heat exchanger, it has been studied to increase the capacity of the heat exchanger in order to improve the heat exchange capacity. As a result, as shown in FIG. 8, the first heat exchangers a which are bent substantially in an L-shape in plan view and have substantially the same shape as each other.
And the second heat exchanger b are arranged in parallel to create an outdoor heat exchanger S. [0005] The unit body c, which is a housing, has outside air inlets d and e on the back and side surfaces thereof, and an outlet f on the front surface. Since the outdoor heat exchanger S is formed in an L-shape in plan view, the outdoor heat exchanger S directly faces each of the outside air suction ports d and e. A blower h provided with a propeller fan g is disposed opposite the outlet f, and as shown by arrows in the drawing, outside air is sucked in from each of the outside air inlets d and e, and an outdoor heat exchanger is provided. The heat is exchanged with S, and the air is blown out from the outlet f. [0007] By providing such a first heat exchanger a and a second heat exchanger b, apparently, the heat exchanger is more heat-exchanged than a single heat exchanger. 2 capacity
Increase by a factor of two. However, with the doubling of the heat exchanger capacity, the heat exchange capacity does not simply double. That is, the heat exchange capacity does not increase unless the air volume is also increased in response to the increase in the capacity. In this case, the blower h and the fan g are made larger or the number of revolutions is increased to cope with the heat exchange capacity. The heat exchange air volume must be secured. [0009] In addition, the propeller fan g has a large air volume and a high air velocity on the back side parallel to the rotation axis. On the other hand, the air volume and the air velocity are small on the side surface that is the direction perpendicular to the rotation axis of the fan g. Therefore, when the capacity of the heat exchanger S is increased as shown in FIG. 8, in order to secure an air volume corresponding to the capacity increase on the side surface where the air volume / air speed is relatively small, the blower h and the fan are required. It is necessary to further increase g or to increase the number of rotations. If the size of the blower h and the fan g is increased, the size of the unit body c is also increased, which is disadvantageous in a situation where a smaller housing is desired. Also, if the number of revolutions is increased, the blowing noise will also increase. Under such conditions, an outdoor heat exchanger Sa as shown in FIG. 9 has been considered. That is, only the second heat exchanger b is formed in an L-shape in plan view, like the previous one. The new first heat exchanger j is straightened and arranged along the rear suction port d. (The same parts as those in FIG. 8 are denoted by the same reference numerals and a new description will be omitted.) If described, the first heat exchanger j is replaced with the second heat exchanger b.
Are arranged in parallel to the straight part of the. On the basis of the airflow of the heat exchange air, the first heat exchanger j is downstream of the second heat exchanger b. In this case, the number of heat exchangers on the side is not increased, and only the capacity of the heat exchanger on the back is increased, so that the capacity of the heat exchanger can be increased. Then, the diameter of the propeller fan g can be increased by an amount corresponding to the decrease in the number of the heat exchangers on the side surfaces, and the air volume can be increased. Therefore, it is possible to increase the capacity of the heat exchanger and the air flow without increasing the size of the housing. However, of the heat exchange air sucked from the outside air suction port d on the back side, the heat exchange air portion that has passed through the curved portion of the second heat exchanger b is particularly located on the downstream side. There is a problem that turbulence is generated by being guided to the U pipe k of the heat exchanger j and noise is increased. The present invention has been made in view of the above circumstances, and an object of the present invention is to increase the capacity of a heat exchanger so as to increase the heat exchange capacity, and also to increase the heat passing through the heat exchanger. It is an object of the present invention to provide an outdoor unit of an air conditioner that can reduce noise by equalizing ventilation resistance to exchange air. An outdoor unit of an air conditioner according to the present invention, which satisfies the above objects, comprises a housing, and has an outside air inlet opening at a back surface and at least one side surface thereof. And a unit body having an outlet opening in the front part, an outdoor heat exchanger disposed in the unit body, and conducting outside air to the outdoor heat exchanger through an outside air suction port, where heat exchange is performed. and then, equipped with a blower having a propeller fan disposed opposite to the air outlet for blowing the air outlet to the outside, the outdoor heat exchanger, a number that is arranged to exist a gap narrowing A fin tube type in which a heat exchange pipe through which a refrigerant is introduced is passed through a single fin, and is formed into a substantially L shape in plan view so as to face an outside air suction port on a back surface and a side surface. I will surround you Between the first heat exchanger and the heat exchange air upstream of the heat exchange air in the first heat exchanger, and in parallel with the straight portion along the back surface outside air suction port. interposed, Ri Do and a second heat exchanger which is formed in a straight shape in plan view, outside air intake of the side surface portion of the first heat exchanger
Adjust the fin pitch at the part facing the
Finer than the fin pitch at the part facing the suction port
Specified. Further, in the first heat exchanger, a fin pitch of a portion of the side surface portion facing the outside air suction port is defined as:
It was set finer than the fin pitch of the part facing the outside air suction port on the back side . The outdoor heat exchanger is formed such that the first heat exchanger is bent in a plan view so as to face the outside air inlets on the rear and side surfaces of the unit body, and is arranged so as to surround the blower. , The second heat exchanger upstream of the first heat exchanger,
It is interposed between the rear side and the outside air suction port, and is formed straight in a plan view. Therefore, the propeller fan in the straight
Two rows of heat exchangers are arranged on the back side with a large amount of air flow,
A row of heat exchangers will be placed on the rear side and side
The ventilation resistance is equalized on the side and the air flow and heat of the heat exchanger
Exchange amount can be balanced, increasing heat exchange capacity
Can be achieved. Also, on the side facing the blower, from the side
The heat exchanger reaching the back side is continuously formed in an L shape, and heat exchange
The wind that has passed through the vessel does not generate turbulence in the end plate portion, and noise can be reduced. An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 shows an outdoor unit constituting an air conditioner. The unit body 1 is a housing in which a front portion, a rear plate, and a bottom plate are integrally combined. A bell mouth 2 is provided on the front surface, and a heat exchange air outlet 3 is formed. Suction ports 4 and 5 for heat exchange air are provided on the back surface and one side surface. An outdoor heat exchanger 6 is arranged in the unit body 1 along the suction ports 4 and 5. The outdoor heat exchanger 6 has a first heat exchanger 7 which is formed in a substantially L-shape in plan view so as to face the outside air inlets 4 and 5 on the rear and side surfaces, The second heat exchanger 8 is arranged in parallel with the straight portion along the backside outside air suction port 4 in the heat exchanger 1 and along the backside outside air suction port side. Each of the heat exchangers 7 and 8 has a large number of fins 9 arranged side by side with a small gap, and a heat exchange pipe 10 projecting from the fin 9 at one end has a U-shape. Condition 1
1 is a so-called finned tube type in which a portion of the heat exchange pipe 10 which is bent and formed and protrudes from the fin 9 at the other end is communicated via a U-bend (not shown ) . The other end fins 9 of the first heat exchanger 7 and the both end fins 9 of the second heat exchanger 8 are correctly opposed to the other end or both end of the back side outside air inlet 4. are doing. One end fin 9 of the first heat exchanger 7 is correctly opposed to one end of the side surface outside air suction port 5. From this, the U-shaped portion 11 and the U-bend portion of the heat exchange pipe 10 in each of the heat exchangers 7 and 8 are all opposed to portions deviated from the outside air inlets 4 and 5, and both will be described later. As such, it is not directly exposed to the outside air introduced from each suction port. An outdoor blower 12 is interposed between the outlet 3 and the first heat exchanger 7 constituting the outdoor heat exchanger 6. The blower 12 includes a fan motor 14 supported on a support 13 provided on the heat exchanger 7 side, a blower fitted to a rotating shaft of the motor, and formed on the bell mouth 2.
It comprises an outlet 3 and a propeller fan 15 facing the outlet . When the propeller fan 15 is rotated by driving the fan motor 14, the outside air is guided into the unit body 1 from the outside air inlets 4 and 5 on the rear and side surfaces as shown by arrows in the figure, and The air passes through the unit body 1 via the heat exchanger 6 and is blown out of the unit body from the outlet 3. From the flow of the heat exchange air in the unit body 1, when the rear outside air suction port 4 is targeted, the second heat exchanger 8 is located on the upstream side, and the first heat exchanger 8 is located on the downstream side. The portion of the vessel 7 facing the suction port 4 is located. As shown in FIG. 2, the diameter φda of the heat exchange pipe 10Pa constituting the first heat exchanger 7 is different from the diameter φdb of the heat exchange pipe 10Pb constituting the second heat exchanger 8.
Set to greater than The heat exchange pipes 10
The pipe pitches of Pa and 10Pb are the same and are arranged in parallel along the direction of the heat exchange air flow. As shown in FIG. 1 again, a partition plate 16 is provided in the unit main body 1 so as to extend from the end on the first heat exchanger 7 side to the vicinity of the bell mouth 2. Bisected. A heat exchange chamber 17 in which the outdoor heat exchanger 6 and the outdoor blower 12 are arranged is formed in one space chamber. A compressor 18 is arranged in the other space chamber, and a compressor chamber 19 is formed. Further, a packed valve 20 for connecting a refrigerant pipe extending from the indoor unit is provided on the side of the compressor chamber 19. Above the compressor 12, electric parts (not shown) such as an electric part box and a reactor containing an inverter and the like are arranged. In the outdoor unit of the air conditioner thus configured, the driving of the compressor 18 is started and the driving of the outdoor blower 12 is started. Outside air is guided into the unit body 1 from both outside air inlets 4 and 5,
The refrigerant exchanges heat with the refrigerant guided to the outdoor heat exchanger 6. The refrigerant guided to the outdoor heat exchanger 6 condenses during the cooling operation, evaporates during the heating operation, and is discharged. The outside air guided into the unit main body 1 from the back side outside air suction port 4 first exchanges heat with the second heat exchanger 8, then exchanges heat with the first heat exchanger 7, and outputs the air through the outlet 3.
It is blown out from. The outside air guided into the unit main body 1 from the side outside air suction port 5 exchanges heat with the first heat exchanger 7 from a place where the second heat exchanger 8 does not exist, and blows out from the outlet 3. Is done. However, with the increase in the heat exchange capacity of the outdoor heat exchanger 6 composed of the first heat exchanger 7 and the second heat exchanger 8 and the increase in the amount of air blow as described below. It is expected that the heat exchange capacity will be increased more than that of the conventional one simply doubling the heat exchange capacity as shown in FIG. 8, and the blowing noise will be reduced as compared with the arrangement shown in FIG. Is also achieved. In other words, the propeller fan 15 constituting the outdoor blower 12 has a large air flow / speed in the direction parallel to the rotation axis of the fan in the direction toward the back of the unit body 1. The air volume / air velocity in the direction of the unit main body side surface, which is the vertical direction, is small. In the present invention, the second heat exchanger 8 and the first heat exchanger 7 are arranged opposite to the outside air suction port 4 on the back of the unit main body 1. Are arranged only in the first heat exchanger 7. That is, two sets of heat exchangers are arranged opposite to the position where the air volume / wind speed of the fan 15 is large, and one set of heat exchangers is installed opposite the position where the air volume / wind speed of the fan 15 is small. As a result, the heat exchanger capacity is almost doubled, and the heat exchange capacity is correspondingly increased. The number of heat exchangers serving as ventilation resistance is increased on the back side where the wind speed is high, and the number of heat exchangers is not increased on the side surface where the wind speed is low. The wind speed of the heat exchange air flowing into the fan 15 via the exchangers 7 and 8 is made uniform, and the blowing noise caused by the unbalanced wind speed as before is reduced. In particular, the second heat exchanger 8 located on the upstream side
Means that the U-shaped portion 11 and the return bend are located at positions away from the outside air inlet 4 on the rear side, and turbulence does not occur from a place where the U-shaped portion 11 and the return air are not directly exposed to the outside air introduced from the inlet, thus contributing to noise reduction. Structure. As shown in FIG. 2, the diameter φd of the heat exchange pipe 10Pa of the first heat exchanger 7 located on the downstream side is
a is large, and the diameter φdb of the heat exchange pipe 10Pb of the second heat exchanger 8 located on the upstream side is small. As described above, the propeller fan 15
, The wind speed is the side <the back, but the difference is 2
Does not double. For example, if the diameter of the heat exchange pipe of the second heat exchanger 8 is set to be the same as the diameter of the heat exchange pipe of the first heat exchanger 7 and they are arranged in a so-called staggered shape with different positions, the ventilation resistance is reduced. It almost doubles.
Then, the wind speed becomes the side> the back side, and the wind speed becomes unbalanced again, thus generating noise. In the present invention, the number of heat exchangers is increased only on the rear side where the wind speed is fast. However, the diameter of the heat exchange pipe φdb of the second heat exchanger 8 on the upstream side is small, and the first heat exchanger on the downstream side is small. By making the diameter φda of the heat exchange pipe of the exchanger 7 large, it is possible to suppress the ventilation resistance as much as possible, and to maintain the wind speed on the side surface side <the rear surface side to obtain noise reduction. Further, since the heat exchange pipes 10Pa and 10Pb of the heat exchangers 7 and 8 are arranged in parallel to the direction of the air flow, it further contributes to the suppression of the ventilation resistance. The heat exchange pipe 10P
If a and 10Pb are arranged in parallel, the downstream heat exchange pipe 10Pa is arranged immediately behind the upstream heat exchange pipe 10Pb, and the upstream heat exchange pipe 10Pb is arranged.
The temperature boundary layer develops due to the heat exchange pipe 10 on the downstream side.
Although the heat exchange efficiency at Pa seems to be reduced, the upstream heat exchange pipe diameter φdb is smaller than the downstream heat exchange pipe diameter φda, and the first and second heat exchangers 7, Since the fins 9 constituting the fins 8 are completely separated from each other, there is no decrease in the heat exchange efficiency. On the contrary, the merit is great because the ventilation resistance does not increase. In the present invention, the outdoor heat exchanger 6 is
When acting as a condenser during the cooling operation, the refrigerant is first guided to the first heat exchanger 7 and then to the second heat exchanger 8. That is, assuming that the outdoor heat exchanger 6 is a condenser, since the refrigerant is discharged from the compressor 18 on the inflow side, the refrigerant is in a superheated gas state. The heat exchange with the heat exchanger 6 changes the refrigerant state from superheated gas to a gas-liquid two-phase and supercooled state. In this case, the pressure loss is large in the superheated gas or in the two-phase state where the dryness is large (the ratio of the gas is large), but the diameter of the heat exchange pipe of the first heat exchanger 7 to which the refrigerant is introduced first is large. Since φda is set to be large, the pressure loss does not increase and the heat exchange efficiency is not impaired. On the other hand, on the outlet side of the heat exchanger 6, the refrigerant is condensed into a gas-liquid two-phase refrigerant or a liquid refrigerant, and has a low dryness. Since the pressure loss of the refrigerant in such a state is small, the heat exchange efficiency can be sufficiently increased even if the diameter of the heat exchange pipe is reduced. In other words, the second
This corresponds to setting the diameter φdb of the heat exchange pipe of the heat exchanger 8 to be small. Therefore, the heat exchange efficiency in the outdoor heat exchanger 6 can be further improved by setting the first and second heat exchangers 7 and 8 of the present invention as described above and the setting of the direction in which the refrigerant is conducted. Will be obtained. The outdoor heat exchanger 6A as shown in FIG. 3 may be used. The diameter φda of the heat exchange pipe 10Pa of the first heat exchanger 7A located on the downstream side is large, and the diameter φd of the heat exchange pipe 10Pb of the second heat exchanger 8A located on the upstream side is large.
Assuming that b is small, each heat exchanger 7
A, 8A heat exchange pipes 10Pa, 10Pb are arranged in a staggered manner. In this case, the ventilation resistance can be reduced at least as compared with the conventional outdoor heat exchanger, and the air volume can be increased. Then, the wind speed per unit area of the heat exchanger increases, which leads to an improvement in heat exchange efficiency. The outdoor heat exchanger 6B as shown in FIG. 4 may be used. The diameter φda of the heat exchange pipe 10Pa of the first heat exchanger 7B located on the downstream side is large, and the diameter φd of the heat exchange pipe 10Pb of the second heat exchanger 8B located on the upstream side is large.
Assuming that b is small, the first heat exchanger 7
B, the heat exchange pipe pitch PPc is increased, and the second heat exchanger 8
The heat exchange pipe pitch PPd of B may be set small. In this case, an increase in the ventilation resistance of the entire outdoor heat exchanger 6B is unavoidable, and a decrease in the air volume is observed. In particular, the heat exchange pipe 10 in the second heat exchanger 8B is used.
Since the number of Pas increases, the heat exchange performance can be improved. A flow path configuration in the outdoor heat exchanger 6 as shown in FIG. 5 may be used. Here, a flow path configuration as a condenser during the cooling operation is shown. The refrigerant flowing into one end of the first heat exchanger 7 is guided as it is to an intermediate portion of the heat exchanger, from which it temporarily exits outside the heat exchanger, and then flows out of the second heat exchanger. 8 into one end. Then, there is a first path P1 which is guided to an intermediate portion of the second heat exchanger 8 and from which it is led out of the heat exchanger. The refrigerant flowing into the intermediate portion of the first heat exchanger 7 is guided to the other end of the heat exchanger as it is.
From here, it once goes out of the heat exchanger and flows into the intermediate part of the second heat exchanger 8. Then, there is a second path P2 which is guided to the other end of the second heat exchanger 8 and from there to the outside of the heat exchanger. That is, the flow paths formed in the heat exchange pipes of the first heat exchanger 7 and the second heat exchanger 8 have two paths P 1,
P2 is set, and the refrigerant is independently guided to each path. When the capacity of the heat exchanger is increased as in the present invention, if the refrigerant flow path is simply set to one pass, the flow path length becomes extremely long and the pressure loss increases. In order to reduce the pressure loss, two completely independent paths are set as described above. The refrigerant outlet side of each of the paths P 1 and P 2 is the second heat exchanger 8, and the diameter of the heat exchange pipe φdb is smaller than the diameter of the heat exchange pipe φda of the first heat exchanger 7. Since the pressure loss can be reduced, it is not necessary to further increase the number of passes (2 to 4 passes) in the middle of each pass. As shown in FIG. 6, the fin pitch PPe of the fins 9 constituting the first heat exchanger 7C is set fine, and the fin pitch PPf of the fins 9 constituting the second heat exchanger 8C is set coarse. I do. That is, the second heat exchanger fin pitch PPf is coarser than the first heat exchanger fin pitch PPe. As described above, when the propeller fan 15 is used, the wind speed on the back side is higher than the wind speed on the side surface. However, since there is no difference of up to twice, if the ventilation resistance is doubled by arranging heat exchange pipes of the same diameter, the wind speed relationship will now be from the side> the back, and the wind speed will again be unbalanced Noise is generated. Therefore, as shown in the figure, when the fin pitch PPf is made coarse so as not to increase the ventilation resistance in the second heat exchanger 8C in the rearward windward row, the balance of the wind speed between the side surface and the rear surface is achieved. It does not lead to noise generation. As shown in FIG. 7, the first heat exchanger 7D
Alternatively, the fin pitch PPg of the facing portion 7e facing the backside outside air suction port 4 may be set to be coarse, and the fin pitch PPh of the facing portion 7f facing the side portion outside air suction port 5 may be set to be fine. That is, since the second heat exchanger 8 is arranged in parallel with the portion 7e of the first heat exchanger 7D along the back side outside air suction port 4, the ventilation resistance on the back side increases. Therefore, the fin pitch PPh on the side surface is finely set in order to make the ventilation resistance on the back side and the side surface side coincide. Therefore, the wind speeds on the side and rear sides are uniform, which helps to prevent noise due to uneven wind speeds. In each of the above embodiments, the first heat exchangers 7 to 7D are formed in an L shape in plan view. However, the present invention is not limited to this. There is no problem even if it is formed in the shape of a letter. [0074] According to the present invention, as described above, according to the present invention, the back
Fin pitch so that the ventilation resistance on the side and the side is the same
To set the airflow resistance on the rear and side sides.
Because of the uniformity, the amount of air blown and the amount of heat exchange of the heat exchanger can be balanced, and the heat exchange capacity can be increased.
On the side facing the blower, a heat exchanger extending from the side surface to the rear surface is continuously formed in an L shape, so that the wind passing through the heat exchanger does not generate turbulence at the end plate portion, It has effects such as noise reduction.

【図面の簡単な説明】【図１】本発明の一実施例を示し、空気調和機の室外ユ
ニットの概略横断平面図。【図２】同実施例の、室外熱交換器を構成する第１の熱
交換器と第２の熱交換器の一部側面図。【図３】他の実施例の、第１の熱交換器と第２の熱交換
器の一部側面図。【図４】さらに他の実施例の、第１の熱交換器と第２の
熱交換器の一部側面図。【図５】さらに他の実施例の、第１の熱交換器と第２の
熱交換器の側面図。【図６】さらに他の実施例の、第１の熱交換器と第２の
熱交換器の一部正面図。【図７】さらに他の実施例の、室外ユニットの一部の横
断平面図。【図８】従来例の、空気調和機の室外ユニットの概略横
断平面図。【図９】さらに異なる従来例の、空気調和機の室外ユニ
ットの概略横断平面図。【符号の説明】４…（背面部の）外気吸込み口、５…（側面部の）外気
吸込み口、３…吹出し口、１…ユニット本体、６…室外
熱交換器、１２…室外送風機、７…第１の熱交換器、８
…第２の熱交換器。BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic cross-sectional plan view of an outdoor unit of an air conditioner, showing one embodiment of the present invention. FIG. 2 is a partial side view of a first heat exchanger and a second heat exchanger constituting the outdoor heat exchanger of the embodiment. FIG. 3 is a partial side view of a first heat exchanger and a second heat exchanger of another embodiment. FIG. 4 is a partial side view of a first heat exchanger and a second heat exchanger according to still another embodiment. FIG. 5 is a side view of a first heat exchanger and a second heat exchanger according to still another embodiment. FIG. 6 is a partial front view of a first heat exchanger and a second heat exchanger according to still another embodiment. FIG. 7 is a cross-sectional plan view of a part of an outdoor unit according to still another embodiment. FIG. 8 is a schematic cross-sectional plan view of a conventional outdoor unit of an air conditioner. FIG. 9 is a schematic cross-sectional plan view of an outdoor unit of an air conditioner according to still another conventional example. [Description of Signs] 4 ... Outside air suction port (on the back), 5 ... Outside air suction port (on the side), 3 ... Outlet, 1 ... Unit body, 6 ... Outdoor heat exchanger, 12 ... Outdoor blower, 7 ... First heat exchanger, 8
... Second heat exchanger.

───────────────────────────────────────────────────── フロントページの続き (56)参考文献特開昭63−131965（ＪＰ，Ａ) 実開平３−21660（ＪＰ，Ｕ) 実開昭61−181279（ＪＰ，Ｕ) 実開昭54−153055（ＪＰ，Ｕ) 実開平６−64032（ＪＰ，Ｕ) 実開平６−30679（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.⁷，ＤＢ名) F24F 5/00 ──────────────────────────────────────────────────続き Continuation of the front page (56) References JP-A-63-131965 (JP, A) JP-A-3-21660 (JP, U) JP-A-61-181279 (JP, U) JP-A-54 153055 (JP, U) JP 6-64032 (JP, U) JP 6-30679 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F24F 5/00

Claims

(57) [Claims] [Claim 1] It is composed of a housing and has at least one
A unit body having an outside air suction opening on one side and an opening on the front side, an outdoor heat exchanger disposed in the unit body, and the outdoor heat exchange through the outside air suction opening In the outdoor unit of the air conditioner, comprising: The outdoor heat exchanger is a finned tube type in which a plurality of fins arranged side by side with a narrow gap and a heat exchange pipe through which a refrigerant is guided penetrates, A first heat exchanger that is formed to be substantially L-shaped in plan view so as to face the suction port and that is arranged so as to surround the blower, and an upstream side of the heat exchange air in the first heat exchanger, On the back Interposed in parallel with the straight portion along the rear portion outside air suction port between the outside air inlet, Ri Do and a second heat exchanger which is formed in a straight shape in plan view, the first heat exchanger To the outside air suction port on the side
The fin pitch of the facing part to the outside air suction port on the back
An outdoor unit for an air conditioner, characterized in that the fin pitch is set finer than the fin pitch of the opposing portion .