JP3764442B2

JP3764442B2 - Stabilizers for air conditioners, cross-flow fans and cross-flow fans

Info

Publication number: JP3764442B2
Application number: JP2003150588A
Authority: JP
Inventors: 尚史池田; 光宏代田; 利彰吉川
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2002-09-05
Filing date: 2003-05-28
Publication date: 2006-04-05
Anticipated expiration: 2023-05-28
Also published as: JP2004150789A

Description

【０００１】
【発明の属する技術分野】
この発明はクロスフローファンを用いた空気調和機に関するもので、詳しくはクロスフローファンに近接、対向して位置し、クロスフローファンの吸込側流路と吹出側流路を分離するスタビライザーの形状に係わり、送風特性や騒音特性を向上し、さらに部品の成形時のバラツキを抑制することによる空気調和機の品質を向上させるスタビライザーの形状に関するものである。
また、この発明は、クロスフローファンを用いた貫流送風機にも適用される。
【０００２】
【従来の技術】
以下、従来のクロスフローファンを搭載した空気調和機について説明する。従来のクロスフローファンを搭載した空気調和機の一例として、例えば特開平１０−２９２９２６号公報「空気調和機」に記載されたものがある。図３０は特開平１０−２９２９２６号公報に記載された空気調和機の縦断面図、図３１は図３０の要部断面図である。
【０００３】
従来のクロスフローファンを搭載した空気調和機を示す図３０、図３１において、１は空気調和機本体、２ａは開閉可能な前面吸込グリル、２ｂは上部吸込グリル、３は前面吸込グリル２ａ及び上部吸込グリル２ｂから吸込まれた部屋１０の空気を熱交換する熱交換器、４はファン回転方向へ向いた複数の翼を有するクロスフローファン、５はクロスフローファン４の下流側に位置し熱交換器３で熱交換された空気を部屋１０へ送風するための吹出口１４へ向けた吹出側流路１３を構成するケーシング、６はクロスフローファン４に近接、対向して位置し、クロスフローファン４の吸込側流路１２と吹出側流路１３を分離するスタビライザー、６ａはスタビライザー６のクロスフローファン４の回転方向Ａに延びたスタビライザー６の舌部、６ｂはスタビライザーの舌部６ａに設けられた左右に延びる突起部、７、８は吹出口１４に設けられた左右風向ベーン、上下風向ベーンである。
【０００４】
スタビライザーの舌部６ａのファン対向面６ｃは、図３１で示すように、クロスフローファン４から所定の間隔で離間した曲率半径Ｒによって、クロスフローファン４と同心状の略曲面形状で形成されるとともに、略曲面形状のファン対向面６ｃのファン回転方向途中にクロスフローファン４に対向して左右に延びる突起部６ｂを設けた構成となっており、これによってスタビライザーの舌部６ａを中心に循環渦ａが発生しなくなり、送風特性や騒音特性が低下しないよう防止できるというものである。
【０００５】
【特許文献１】
特開平１０−２９２９２６号公報
【０００６】
【発明が解決しようとする課題】
しかしながら、上記特開平１０−２９２９２６号公報に記載された従来のクロスフローファンを用いた空気調和機において、運転時間が経過し除塵フィルタ９にホコリが堆積した場合や、吸込グリルの開口面積が小さくなるなど通風抵抗が大きくなる場合、循環渦ａは大きくなり、スタビライザーの舌部６ａのファン対向面６ｃがクロスフローファン４から所定の間隔で離間した曲率半径Ｒによって、クロスフローファン４と同心状の略曲面形状で形成されるとともに、略曲面形状部のファン対向面６ｃのファン回転方向途中にクロスフローファン４に対向して左右に延びる突起部６ｂを設けた構成となっているため、スタビライザーの舌部６ａのファン対向面６ｃに接する循環渦ａの接点が不安定になる。
【０００７】
さらに突起部６ｂのスタビライザーの舌部６ａのファン対向面６ｃからの突出高さＨｓが、クロスフローファン４の各翼４ａの外周端４ｂに接する外周円Ｄとスタビライザーの舌部のファン対向面６ｃの最小隙間寸法Ｇ１に対し小さく、つまりクロスフローファン４の各翼４ａの外周端４ｂに接する外周円Ｄと突起部６ｂ間の隙間Ｇ２が大きいと循環渦ａが突起部６ｂでファン内部方向へ変向されないため、循環渦ａの挙動が不安定になってしまう。
【０００８】
その結果、送風特性、騒音特性がともに急激に悪化してしまうとともに、特に冷房時、部屋１０の空気が吹出口１４からクロスフローファン４へ向け逆流、着露し、部屋１０に向け着露水が飛散してしまう恐れがあり空気調和機の品質が低下してしまう。
【０００９】
また、ホコリ等が除塵フィルタ９に堆積していない場合でも、スタビライザーの舌部６ａのファン対向面６ｃ上のファン回転方向途中にクロスフローファン４に対向して突起部６ｂが左右に同形状で延びる構成となっているため、循環渦ａのクロスフローファン４への再流入点４ｃがファン長さ方向でほぼ同位置なため、翼４ａは長さ方向で同様なタイミングで圧力変動を受け、さらに循環渦ａがスタビライザーのファン対向面６ｃに衝突するタイミングも同様なため翼４ａへ同時期に圧力変動を受けるため回転音が発生し聴感が悪くなる恐れがあった。
【００１０】
この発明は上記のような問題点を解消するためになされたもので、ホコリ等の除塵フィルタでの堆積や吸込グリルの開口面積縮小による通風抵抗の増加に対し送風特性や騒音特性の悪化を抑制し、さらに冷房時、部屋の空気の吹出口からクロスフローファンへの逆流、着露による着露水の飛散を防止し空気調和機の品質低下を防止し、そして回転音の抑制により聴感が良い空気調和機を得ることを目的とする。
【００１１】
また、ホコリ等により吸込口の開口面積縮小による通風抵抗の増加に対し送風特性や騒音特性の悪化を抑制し、さらに部屋の空気の吹出口からクロスフローファンへの逆流を防止し、そして回転音の抑制により聴感が良い貫流送風機及びクロスフローファンのスタビライザーを得ることを目的とする。
【００１２】
【課題を解決するための手段】
この発明に係る空気調和機は、クロスフローファンと、このクロスフローファンの吸込側流路と吹出側流路を分離するスタビライザーとを有する空気調和機において、スタビライザーにクロスフローファンの回転方向に延びて形成され、クロスフローファン対向面がクロスフローファンの回転方向へ向け徐々にクロスフローファン外周円との隙間が小さくなるように形成された舌部と、クロスフローファン外周円と舌部の隙間が最小となる舌部先端部にクロスフローファン内部へ向け突出して形成され、クロスフローファンとの最小隙間部となるファン軸方向に直交する断面形状が略三角形の突起部と、を備え、突起部の舌部のクロスフローファン対向面からの突出高さＨｓが、クロスフローファン外周円と舌部のクロスフローファン対向面との最小隙間寸法Ｇ１に対し２５〜３５％とし、突起部の頂角が５０゜〜７５゜となるように形成したことを特徴とする。
【００１３】
【発明の実施の形態】
以下、この発明の実施の形態を図面に基づいて説明する。空気調和機としては、前面吸込グリル及び上部吸込グリルを有する形態のものを例として説明するが、本発明はこれに限定されるものではない。
【００１４】
実施の形態１．
この発明に係る貫流送風機は、クロスフローファンと、このクロスフローファンの吸込側流路と吹出側流路を分離するスタビライザーとを有する貫流送風機において、スタビライザーにクロスフローファンの回転方向に延びて形成され、クロスフローファン対向面がクロスフローファンの回転方向へ向け徐々にクロスフローファン外周円との隙間が小さくなるように形成された舌部と、クロスフローファン外周円と舌部の隙間が最小となる舌部先端部にクロスフローファン内部へ向け突出して形成され、クロスフローファンとの最小隙間部となるファン軸方向に直交する断面形状が略三角形の突起部と、を備え、突起部の舌部のクロスフローファン対向面からの突出高さＨｓが、クロスフローファン外周円と舌部のクロスフローファン対向面との最小隙間寸法Ｇ１に対し２５〜３５％とし、突起部の頂角が５０゜〜７５゜となるように形成したことを特徴とする。
【００１５】
この発明に係る貫流送風機は、スタビライザーの舌部をクロスフローファンの回転方向へ向け徐々にクロスフローファン外周円との隙間が小さくなるように形成し、突起部の舌部のクロスフローファン対向面からの突出高さＨｓが、クロスフローファン外周円と舌部のクロスフローファン対向面との最小隙間寸法Ｇ１に対し２５〜３５％とし、突起部の頂角が５０゜〜７５゜となるように形成したことにより、ホコリ等により吸込口の開口面積縮小による通風抵抗の増加に対し送風特性や騒音特性の悪化を抑制し、さらに部屋の空気の吹出口からクロスフローファンへの逆流を防止し、そして回転音の抑制により聴感が良い貫流送風機を提供できる。
【００１６】
この発明に係るクロスフローファンのスタビライザーは、クロスフローファンの吸込側流路と吹出側流路を分離するクロスフローファンのスタビライザーにおいて、クロスフローファンの回転方向に延びて形成され、クロスフローファン対向面がクロスフローファンの回転方向へ向け徐々にクロスフローファン外周円との隙間が小さくなるように形成された舌部と、クロスフローファン外周円と舌部の隙間が最小となる舌部先端部にクロスフローファン内部へ向け突出して形成され、クロスフローファンとの最小隙間部となるファン軸方向に直交する断面形状が略三角形の突起部と、を備え、突起部の舌部のクロスフローファン対向面からの突出高さＨｓが、クロスフローファン外周円と舌部のクロスフローファン対向面との最小隙間寸法Ｇ１に対し２５〜３５％とし、突起部の頂角が５０゜〜７５゜となるように形成したことを特徴とする。
【００１７】
この発明に係るクロスフローファンのスタビライザーは、スタビライザーの舌部をクロスフローファンの回転方向へ向け徐々にクロスフローファン外周円との隙間が小さくなるように形成し、突起部の舌部のクロスフローファン対向面からの突出高さＨｓが、クロスフローファン外周円と舌部のクロスフローファン対向面との最小隙間寸法Ｇ１に対し２５〜３５％とし、突起部の頂角が５０゜〜７５゜となるように形成したことにより、クロスフローファンの循環渦が安定し、空気の逆流や、圧力変動による回転音の増大を抑制できる。
【００１８】
以下、請求項１及び上記発明の具体的な実施の形態を詳細に説明する。
図１〜４は実施の形態１を示す図で、図１は空気調和機の構成を示す外観図、図２は空気調和機の縦断面図、図３，４は空気調和機のスタビライザーの舌部近傍を拡大した要部拡大図である。
【００１９】
図１、２において、１は部屋１０の壁１０ａに取付けられた空気調和機本体、２ａは開閉可能な前面吸込グリル、２ｂは上部吸込グリル、９は部屋１０の空気中の大きなホコリを除去する網状の除塵フィルタ、３は前面吸込グリル２ａ及び上部吸込グリル２ｂから吸込まれた部屋１０の空気を熱交換する熱交換器、４はファン回転方向へ向いた複数の翼を有するクロスフローファン、５はクロスフローファン４の下流側に位置し熱交換器３で熱交換された空気を部屋１０へ送風するための吹出口１４へ向けた吹出側流路１３を構成するケーシング、６はクロスフローファン４に近接、対向して位置し、クロスフローファン４の吸込側流路１２と吹出側流路１３を分離するスタビライザー、６ａはスタビライザー６のクロスフローファン４の回転方向Ａ（時計方向）に延びたスタビライザー６の舌部、６ｂはスタビライザーの舌部６ａに設けられた左右に延びる突起部、７、８は吹出口１４に設けられた左右風向ベーン、上下風向ベーンである。
【００２０】
上記のように構成されたクロスフローファン４を搭載した空気調和機において、図１、図２に示すようにクロスフローファン４がＡ方向に回転すると、着脱可能な前面吸込グリル２ａと上部吸込グリル２ｂから部屋１０の空気を吸い込み、空気中の大きなホコリを除塵フィルタ９で除去された後、熱交換器３で冷却または温められ、その後クロスフローファン４に吸い込まれる。そしてクロスフローファン４から吹出口１４へ向け吹き出された空気は左右風向ベーン７、上下風向ベーン８により部屋１０の上下、左右方向に吹き分けられる。
【００２１】
また図３、図４において、クロスフローファン４の回転方向Ａにクロスフローファン４に沿う方向の凹曲面で延びたスタビライザーの舌部６ａのファン対向面６ｃのファン回転方向Ａ上流側端部である舌部開始部６ｃ１とクロスフローファン４の各翼４ａの外周端４ｂに接するファン外周円Ｄとの最近接距離である隙間Ｇｃは、スタビライザーの舌部６ａのファン対向面６ｃのファン回転方向Ａ下流側端部である舌部先端部６ｃ２とファン外周円Ｄとの最近接距離で、ファン外周円Ｄとファン対向面６ｃと最小隙間である隙間Ｇ１に比べ大きく、つまりファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃの隙間Ｇが回転方向Ａに行くに従い小さくなるように形成されている。
【００２２】
さらにスタビライザー舌部６ａに設けられた突起部６ｂは、舌部先端部６ｃ２上にファン内部へ向け突出し、スタビライザー舌部６ａのファン対向面６ｃから突起部頂点６ｂ１まで突出高さＨｓを高さとする略三角形で、ファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃとの最小隙間寸法Ｇ１に対し突出高さＨｓが任意高さとなるようスタビライザーの舌部６ａ全体が形成されている。
【００２３】
このようにスタビライザーの舌部６ａを形成することにより、従来の空気調和機のスタビライザーの舌部６ａのようなクロスフローファン４から所定の間隔で離間した曲率半径Ｒによって、クロスフローファン４と同心状の略曲面形状で略曲面形状のファン対向面６ｃのファン回転方向途中にクロスフローファン４に対向して左右に延びる突起部６ｂを設けた構成時に比べ、循環渦ａは突起部６ｂで急激にファン内部へ再流入することなく、本発明のようにファン外周円Ｄとスタビライザー舌部のファン対向面６ｃの隙間Ｇが回転方向Ａに行くに従い小さくなるように形成されているのでファン対向面６ｃ、略三角形状の突起部６ｂで徐々に再流入するため循環渦ａの挙動が安定し、各翼４ａを通過する貫流渦ｂも安定する。
【００２４】
しかし除塵フィルタ９にホコリが堆積していき通風抵抗が増加した場合、ファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃとの最小隙間寸法Ｇ１に対しスタビライザー舌部先端部６ｃ２上に設けられた略三角形の突起部６ｂの突出高さＨｓが低すぎたり、頂角θが大きすぎると、循環渦ａが突起部６ｂを乗り越え循環渦ａは大きくなり不安定ぎみになり、吹出口１４から部屋１０の空気が逆流する。また突出高さＨｓが高すぎたり、頂角θが小さすぎると、突起部６ｂで急激に循環渦ａが変向され不安定な挙動になるとともに、翼４ａが急激に圧力変動を受け回転音が発生し騒音値が悪化する。
【００２５】
そこで、突出高さＨｓと、ファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃとの最小隙間寸法Ｇ１の関係及び突起部の頂角θに最適範囲が存在する。
【００２６】
図５は、ファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃとの最小隙間寸法Ｇ１に対する突起部６ｂの突出高さＨｓの比率Ｈｓ／Ｇ１が変化したときの同一風量時の騒音値の変化を示した図で、実線は除塵フィルタにホコリが無いとき、破線は除塵フィルタにホコリが堆積しているときの特性である。図５のように比率Ｈｓ／Ｇ１が２０％以上４０％以下であれば騒音値は改善傾向である。
【００２７】
また図６は突起部６ｂの頂角θ変化時の同一風量時の騒音値の変化を示した図で、図５同様実線は除塵フィルタにホコリが無いとき、破線は除塵フィルタにホコリが堆積しているときの特性である。図６のように頂角θが５０゜〜８０°であれば騒音値は改善傾向である。
【００２８】
さらに図７は、比率Ｈｓ／Ｇ１変化時の吹出口１４へ部屋１０の空気が逆流するまでの運転可能時間を示した図で、図に示すように比率Ｈｓ／Ｇ１が２５％以上３５％以下であれば運転可能時間の延長が図れる。
【００２９】
そしてさらに図８は、突起部６ｂの頂角θ変化時の吹出口１４へ部屋１０の空気が逆流するまでの運転可能時間を示した図で、図８に示すように頂角θが７５゜以下であれば運転可能時間の延長が図れる。
【００３０】
以上の結果より、比率Ｈｓ／Ｇ１が２５％〜３５％で、突起部の頂角θが５０゜〜７５゜であれば、除塵フィルタ９にホコリが堆積していっても騒音値が急激に悪化することなく、また従来に比べ空気調和機の運転可能時間の延長が図れることから、除塵フィルタの掃除時期の延長が可能であるとともに、吹出口１４から逆流しずらいのでクロスフローファン４への着露水の飛散の心配がないので高品質な空気調和機が得られる。
【００３１】
また、通風抵抗が増加しても特性が悪化しずらいことから、除塵フィルタ９の他に、図９のようにさらに微細な多孔質状の空気清浄フィルタ１１を配設可能となり、除塵フィルタ９を通過した微細なホコリをさらに除去でき、さらに清潔な空調された空気を部屋１０へ送風できる空気調和機が得られる。
【００３２】
さらに、図１０のように、空気調和機の正面に位置し開閉可能な前面吸込グリルの格子を減少させ開口面積を小さくでき、前面吸込グリルに平坦部を増加できるので、従来格子状であるため拭き掃除しづらかったものが、容易に拭き掃除可能となることから清潔な空気調和機が得られる。
【００３３】
実施の形態２．
この発明に係る空気調和機は、突起部がクロスフローファンの長手方向で異方向を向くように形成されたことを特徴とする。
【００３４】
この発明に係る空気調和機は、突起部がクロスフローファンの長手方向で異方向を向くように形成されたことにより、循環渦がクロスフローファンへ再流入するとき、ファン長さ方向で同位置で再流入することがなく、回転音が低下し聴感が改善されるので、聴感がよく静粛な空気調和機が得られる。
【００３５】
また、この発明に係る空気調和機は、クロスフローファンは支持板からファン回転方向へ向く複数の翼が延出したコマを複数連接、固着して形成され、各コマの１／３以上毎に突起部が、クロスフローファンの長手方向で異方向を向くように形成されたことを特徴とする。
【００３６】
また、この発明に係る空気調和機は、クロスフローファンは支持板からファン回転方向へ向く複数の翼が延出したコマを複数連接、固着して形成され、各コマの１／３以上毎に突起部が、クロスフローファンの長手方向で異方向を向くように形成されたことにより、回転音がさらに低減する。
【００３７】
この発明に係る貫流送風機は、突起部がクロスフローファンの長手方向で異方向を向くように形成されたことを特徴とする。
【００３８】
この発明に係る貫流送風機は、突起部がクロスフローファンの長手方向で異方向を向くように形成されたことにより、循環渦がクロスフローファンへ再流入するとき、ファン長さ方向で同位置で再流入することがなく、回転音が低下し聴感が改善されるので、聴感がよく静粛な貫流送風機が得られる。
【００３９】
また、この発明に係る貫流送風機は、クロスフローファンは支持板からファン回転方向へ向く複数の翼が延出したコマを複数連接、固着して形成され、各コマの１／３以上毎に突起部が、クロスフローファンの長手方向で異方向を向くように形成されたことを特徴とする。
【００４０】
また、この発明に係る貫流送風機は、クロスフローファンは支持板からファン回転方向へ向く複数の翼が延出したコマを複数連接、固着して形成され、各コマの１／３以上毎に突起部が、クロスフローファンの長手方向で異方向を向くように形成されたことにより、回転音がさらに低減する。
【００４１】
この発明に係るクロスフローファンのスタビライザーは、突起部がクロスフローファンの長手方向で異方向を向くように形成されたことを特徴とする。
【００４２】
この発明に係るクロスフローファンのスタビライザーは、突起部がクロスフローファンの長手方向で異方向を向くように形成されたことにより、循環渦がクロスフローファンへ再流入するとき、ファン長さ方向で同位置で再流入することがなく、回転音が低下し聴感が改善される。
【００４３】
また、この発明に係るクロスフローファンのスタビライザーは、クロスフローファンは支持板からファン回転方向へ向く複数の翼が延出したコマを複数連接、固着して形成され、各コマの１／３以上毎に突起部が、クロスフローファンの長手方向で異方向を向くように形成されたことを特徴とする。
【００４４】
また、この発明に係るクロスフローファンのスタビライザーは、クロスフローファンは支持板からファン回転方向へ向く複数の翼が延出したコマを複数連接、固着して形成され、各コマの１／３以上毎に突起部が、クロスフローファンの長手方向で異方向を向くように形成されたことにより、回転音がさらに低減する。
【００４５】
以下、上記発明の具体的な実施の形態を詳細に説明する。
図１１〜１３は実施の形態２を示す図で、図１１は空気調和機の構成を示す縦断面図、図１２は図１１の矢視Ｅ図、図１３は図１２の各スタビライザー断面における拡大図である。尚本実施の形態におけるスタビライザー６の形状以外の構成は前述した実施の形態１と同様であるため、同一の符号を付して説明を省略する。
【００４６】
図１１において、６はクロスフローファン４に近接、対向して位置し、クロスフローファン４の吸込側流路１２と吹出側流路１３を分離するスタビライザー、６ａはスタビライザー６のクロスフローファン４の回転方向Ａに延びたスタビライザー６の舌部、６ｂはスタビライザーの舌部６ａの舌部先端部６ｃ２に設けられ、左右に延びる略三角形の突起部である。また突起部６ｂの突出高さＨｓと、ファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃとの最小隙間寸法Ｇ１の比率Ｈｓ／Ｇ１が２５％〜３５％で、突起部の頂角θが５０゜〜７５゜の範囲内である。
【００４７】
また図１１の矢視Ｅ図である図１２において、クロスフローファン４は円形支持板４ｄから複数の翼４ａが延出したコマ４ｅが複数連接、固着されて形成され、スタビライザー６の略三角形の突起部６ｂの突起部頂点６ｂ１は、図１３の断面Ｊ−Ｊ、Ｋ−Ｋのように各コマ４ｅごとに異方向を向いている。
【００４８】
このようにスタビライザーの突起部６ｂを形成することにより、従来のようにクロスフローファン４の長さ方向で同位置に突起部６ｂを有する場合に比べ、循環渦ａがクロスフローファン４へ再流入するとき、ファン長さ方向で同位置で再流入することがないので、図１４のように従来に比べ回転音が低下し聴感が改善される。
【００４９】
さらに、スタビライザー６の略三角形の突起部６ｂの突起部頂点６ｂ１は、図１２の断面Ｌ−Ｌ、Ｍ−Ｍ部、断面Ｌ−Ｌ、Ｊ−Ｊ、Ｍ−Ｍ部のように各コマ４ｅの半分、１／３ごとに異方向を向いている場合、さらに回転音が低減するが、図１５のように１コマに対しそれよりも突起部６ｂの方向を細かく変化させても回転音のピーク値のさらなる低減は小さくなる。
【００５０】
以上のようにスタビライザーの突起部６ｂを形成することにより、聴感がよく静粛な空気調和機が得られる。
【００５１】
実施の形態３．
この発明に係る空気調和機は、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に凹凸形状となるように形成されたことを特徴とする。
【００５２】
この発明に係る空気調和機は、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に凹凸形状となるように形成されたことにより、循環渦がスタビライザーの舌部のファン対向面に接する時間がファン長さ方向で同一ではなくなるため、翼の圧力変動を受ける時間がずれ回転音が低減されるので聴感がよく静粛な空気調和機が得られる。
【００５３】
また、この発明に係る空気調和機は、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に交互に凹凸形状となるように形成されたことを特徴とする。
【００５４】
また、この発明に係る空気調和機は、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に交互に凹凸形状となるように形成されたことにより、さらに聴感がよく静粛な空気調和機が得られる。
【００５５】
また、この発明に係る空気調和機は、凹凸形状の夫々の幅を不等としたことを特徴とする。
【００５６】
また、この発明に係る空気調和機は、凹凸形状の夫々の幅を不等としたことにより、翼の圧力変動を受ける時間が分散するため、さらに回転音が低減される。
【００５７】
この発明に係る貫流送風機は、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に凹凸形状となるように形成されたことを特徴とする。
【００５８】
また、この発明に係る貫流送風機は、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に凹凸形状となるように形成されたことにより、循環渦がスタビライザーの舌部のファン対向面に接する時間がファン長さ方向で同一ではなくなるため、翼の圧力変動を受ける時間がずれ回転音が低減されるので聴感がよく静粛な貫流送風機が得られる。
【００５９】
また、この発明に係る貫流送風機は、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に交互に凹凸形状となるように形成されたことを特徴とする。
【００６０】
また、この発明に係る貫流送風機は、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に交互に凹凸形状となるように形成されたことにより、さらに聴感がよく静粛な空気調和機が得られる。
【００６１】
また、この発明に係る貫流送風機は、凹凸形状の夫々の幅を不等としたことを特徴とする。
【００６２】
また、この発明に係る貫流送風機は、凹凸形状の夫々の幅を不等としたことにより、翼の圧力変動を受ける時間が分散するため、さらに回転音が低減される。
【００６３】
この発明に係るクロスフローファンのスタビライザーは、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に凹凸形状となるように形成されたことを特徴とする。
【００６４】
また、この発明に係るクロスフローファンのスタビライザーは、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に凹凸形状となるように形成されたことにより、循環渦がスタビライザーの舌部のファン対向面に接する時間がファン長さ方向で同一ではなくなるため、翼の圧力変動を受ける時間がずれ回転音が低減される。
【００６５】
また、この発明に係るクロスフローファンのスタビライザーは、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に交互に凹凸形状となるように形成されたことを特徴とする。
【００６６】
また、この発明に係るクロスフローファンのスタビライザーは、スタビライザーのクロスフローファン対向面がクロスフローファン長さ方向に交互に凹凸形状となるように形成されたことにより、さらに回転音が低減される。
【００６７】
また、この発明に係るクロスフローファンのスタビライザーは、凹凸形状の夫々の幅を不等としたことを特徴とする。
【００６８】
また、この発明に係るクロスフローファンのスタビライザーは、凹凸形状の夫々の幅を不等としたことにより、翼の圧力変動を受ける時間が分散するため、さらに回転音が低減される。
【００６９】
以下、上記発明の具体的な実施の形態を詳細に説明する。
図１６〜１８は実施の形態３を示す図で、空気調和機の構成を示す縦断面図、図１７は図１６の矢視Ｆ図、図１８は図１６のスタビライザー断面における拡大図である。尚本実施の形態におけるスタビライザー６の形状以外の構成は前述した実施の形態１と同様であるため、同一の符号を付して説明を省略する。
【００７０】
図１６〜図１８において、クロスフローファン４の回転方向Ａにクロスフローファン４に沿う方向でファン内部方向に中心をもつ凹曲面で延びたスタビライザーの舌部６ａのファン対向面６ｃのファン回転方向Ａの上流側端部である舌部開始部６ｃ１とファン外周円Ｄとの最近接距離である隙間Ｇｃが、スタビライザーの舌部６ａのファン回転方向Ａの下流側端部である舌部先端部６ｃ２とファン外周円Ｄとの最小隙間Ｇ１に比べ大きくなるように形成した凸部６ａ１と、凸部６ａ１と異なるファン内部方向に中心をもつ凹曲面で隙間Ｇ１は同一で隙間Ｇｃより大きな舌部開始部６ｃ３とファン外周円Ｄとの隙間Ｇｄとなるように形成された凹部６ａ２が、図１７のようにクロスフローファン４の長さ方向で凸部６ａ１、凹部６ａ２、…と交互となりスタビライザーの舌部６ａのファン対向面６ｃが凸凹形状となるようにスタビライザーの舌部６ａは形成されている。また突起部６ｂの突出高さＨｓと、ファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃとの最小隙間寸法Ｇ１の比率Ｈｓ／Ｇ１が２５％〜３５％で、突起部の頂角θが５０゜〜７５゜の範囲内である。
【００７１】
このようにスタビライザーの舌部６ａを形成することにより、従来のファン長さ方向で同形状のスタビライザーの舌部６ａのような循環渦ａがスタビライザーの舌部６ａのファン対向面６ｃに接する時間がファン長さ方向で同一ではなくなるため、翼４ａの圧力変動を受ける時間がずれ図１９のように回転音が低減される。
【００７２】
特に図１７のようにスタビライザーの舌部の凸部６ａ１及び凹部６ａ２のファン長さ方向の幅Ｓ１、Ｓ２が不等であると、さらに翼４ａの圧力変動を受ける時間が分散するため、図２０のようにさらに回転音が低減される。
【００７３】
実施の形態４．
この発明に係る空気調和機は、吸込グリル下流側に除塵フィルタを、クロスフローファンの上流側に熱交換器を配置し、除塵フィルタと熱交換器の間に微細な空気浮遊物が除去可能な空気清浄フィルタを配設したことを特徴とする。
【００７４】
この発明に係る空気調和機は、吸込グリル下流側に除塵フィルタを、クロスフローファンの上流側に熱交換器を配置し、除塵フィルタと熱交換器の間に微細な空気浮遊物が除去可能な空気清浄フィルタを配設したことにより、循環渦の挙動は安定しているので、大型の空気清浄フィルタが搭載可能で、除塵フィルタで除去できなかった空気中の微細なホコリや浮遊物を除去可能となり、清潔な空気を送風でき衛生的で高品質な空気調和機が得られる。
【００７５】
以下、上記発明の具体的な実施の形態を詳細に説明する。
図２１は実施の形態４を示す図で、空気調和機の構成を示す縦断面図である。尚本実施の形態における基本構成は前述した実施の形態３と同様であるため、同一の符号を付して説明を省略する。
【００７６】
図２１において、スタビライザーの舌部６ａの略三角形の突起部６ｂの突出高さＨｓと、ファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃとの最小隙間寸法Ｇ１の比率Ｈｓ／Ｇ１が２５％〜３５％で、突起部の頂角θが５０゜〜７５゜の範囲内で、さらに突起部６ｂはファン長さ方向で異方向を向き、そしてスタビライザーのファン対向面６ｃは凸凹形状となるように形成されている。また除塵フィルタ９と熱交換器３の間に微細な空気浮遊物が除去可能な空気清浄フィルタ１１を配設されている。
【００７７】
従来の空気調和機では、本発明のようなスタビライザーの舌部形状でないので、クロスフローファン４の通風抵抗が増加すると循環渦ａの挙動が不安定になりやすかったため、通風抵抗が高い空気清浄フィルタ１１を小さな状態でしか搭載できなかった。しかし本発明により循環渦ａの挙動は安定しているので、大型な空気清浄フィルタ１１を搭載可能である。
【００７８】
以上の結果、大型の空気清浄フィルタが搭載可能なので、除塵フィルタで除去できなかった空気中の微細なホコリや浮遊物を除去可能となり、清潔な空気を送風でき衛生的で高品質な空気調和機を得られる。
【００７９】
実施の形態５．
この発明に係る空気調和機は、前面に前面吸込グリルと、上部に上部吸込グリルとを有し、前面吸込グリルの通風抵抗が上部吸込グリルの通風抵抗より大きいことを特徴とする。
【００８０】
この発明に係る空気調和機は、前面に前面吸込グリルと、上部に上部吸込グリルとを有し、前面吸込グリルの通風抵抗が上部吸込グリルの通風抵抗より大きいことにより、前面吸込グリル表面の壁面が占める割合が増加しても安定な運転可能で、従来のような格子グリルにくらべホコリが付着しずらく、その結果、清潔な空気を送風でき、かつ衛生的で高品質な空気調和機が得られる。
【００８１】
以下、上記発明の具体的な実施の形態を詳細に説明する。
図２２、２３は実施の形態５を示す図で、図２２は空気調和機の構成を示す外観図、図２３は空気調和機の縦断面図である。尚本実施の形態における基本構成は前述した実施の形態４と同様であるため、同一の符号を付して説明を省略する。
【００８２】
図２２、２３において、スタビライザーの舌部６ａの略三角形の突起部６ｂの突出高さＨｓと、ファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃとの最小隙間寸法Ｇ１の比率Ｈｓ／Ｇ１が２５％〜３５％で、突起部の頂角θが５０゜〜７５゜の範囲内で、さらに突起部６ｂはファン長さ方向で異方向を向き、そしてスタビライザーのファン対向面６ｃは凸凹形状となるように形成されている。また除塵フィルタ９と熱交換器３の間に微細な空気浮遊物が除去可能な空気清浄フィルタ１１を配設されている。
【００８３】
従来の空気調和機では、本発明のようなスタビライザーの舌部形状でないため、クロスフローファン４の通風抵抗が増加すると循環渦ａの挙動が不安定になりやすかったため、通風抵抗が高く大型の空気清浄フィルタ１１を搭載できないだけでなく、空気調和機の正面に位置する前面吸込グリル２ａの通風抵抗が上部吸込グリル２ｂの通風抵抗より大きい状態だと急激に空力特性が悪化するとともに、吹出口１４から空気がクロスフローファン４へ逆流してしまった。
【００８４】
しかし本発明のようにスタビライザーの舌部６ａを形成することにより循環渦ａの挙動は安定しているので、空気調和機の正面に位置する前面吸込グリル２ａの通風抵抗が上部吸込グリル２ｂの通風抵抗より大きい状態でも安定して送風できる。
【００８５】
以上の結果、大型の空気清浄フィルタ１１が搭載可能なので、除塵フィルタ９で除去できなかった空気中の微細なホコリを除去可能となり、さらに前面吸込グリル２ａの開口部を小さくでき、前面吸込グリル２ａ表面の壁面が占める割合が増加しても安定な運転可能で、また従来のような格子グリルにくらべホコリが付着しずらい。その結果、清潔な空気を送風でき、かつ衛生的で高品質な空気調和機が得られる。
【００８６】
以上の実施の形態では、空気調和機に本発明を適用した例を説明したが、クロスフローファンを用いた貫流送風機にも本発明は適用可能であり、ホコリ等により吸込口の開口面積縮小による通風抵抗の増加に対し送風特性や騒音特性の悪化を抑制し、さらに部屋の空気の吹出口からクロスフローファンへの逆流を防止し、そして回転音の抑制により聴感が良い貫流送風機を提供できる。
【００８７】
実施の形態６．
図２４〜２７は実施の形態６を示す図で、図２４は空気調和機の構成を示す外観図、図２５は除塵フィルタ９にホコリが堆積したり、冷房時のクロスフローファン４の通風抵抗が増加した時の突起部６ｂの動作を示したスタビライザー６近傍の部分拡大図、図２６は暖房時や除塵フィルタ９にホコリが堆積していないクロスフローファン４の通風抵抗が大きくない通常運転時のスタビライザー６近傍の部分拡大縦断面図、図２７は空気調和機本体１の上下風向ベーン８の表面に配設された結露センサー１５の部分拡大図である。
【００８８】
尚、本実施の形態におけるスタビライザー６の形状以外の構成は前述した実施の形態１と同様であるため、同一の符号を付して説明を省略する。
【００８９】
図２４において、空気調和機本体１の吹出口１４に設けられた上下風向ベーン８の表面には、結露センサー１５が配設されている。結露センサー１５が結露を検出すると、制御部１６に信号が出力される。
【００９０】
結露センサー１５は、例えば数本の細線の銅線１５ａを上下風向ベーン８の長手方向に近接して張られた構成である。例えば、図２７に示すように、上下風向ベーン８の駆動用モータ１８側端部の中心付近から長手方向に延出した直線条の銅線１５ａと、上下風向ベーン８の他方の端部から長手方向に延出した略Ｕ字状の銅線１５ａとで構成される。これらの直線条の銅線１５ａと、略Ｕ字状の銅線１５ａとの間に水滴が付着するとその間が通電状態となるので、制御部１６に信号が出力される。
【００９１】
上下風向ベーン８に配設される結露センサー１５として、数本の細線の銅線１５ａを上下風向ベーン８の長手方向に近接して張られた構成のものを示したが、これに限定されるものではない。
【００９２】
図２５、図２６において、スタビライザー６は、クロスフローファン４に近接、対向して位置し、クロスフローファン４の吸込側流路１２と吹出側流路１３を分離する。スタビライザー６は、クロスフローファン４の回転方向Ａ（時計方向）に延びたスタビライザーの舌部６ａを有する。スタビライザーの舌部６ａには、クロスフローファン４の回転方向Ａ下流側の舌部先端部６ｃ２に、空気調和機本体１の左右に延びて形成された、クロスフローファン４側に凸の略三角形の突起部６ｂが設けられている。
【００９３】
また図２５、図２６において、クロスフローファン４の回転方向Ａにクロスフローファン４に沿う方向の凹曲面で延びたスタビライザーの舌部６ａのファン対向面６ｃのファン回転方向Ａ上流側端部である舌部開始部６ｃ１とクロスフローファン４の各翼４ａの外周端４ｂに接するファン外周円Ｄとの最近接距離である隙間Ｇｃは、スタビライザーの舌部６ａのファン対向面６ｃのファン回転方向Ａ下流側端部である舌部先端部６ｃ２とファン外周円Ｄとの最近接距離で、ファン外周円Ｄとファン対向面６ｃと最小隙間である隙間Ｇ１に比べ大きく、つまりファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃの隙間Ｇが回転方向Ａに行くに従い小さくなるように形成されている。
【００９４】
略三角形の突起部６ｂは、ファン上流側辺６ｅとファン下流側辺６ｆの２辺で構成される。この２辺で形成される略三角形の、クロスフローファン４側の突起部頂点６ｂ１の頂角をθとする。突起部６ｂはファン上流側辺６ｅのスタビライザー側端点６ｅ１がスタビライザー６に連結し、突起部頂点６ｂ１が屈曲点となる。
【００９５】
略三角形の突起部６ｂは、空気調和機の運転状態により頂角θが変化するように、スタビライザー側端点６ｅ１を起点、突起部頂点６ｂ１を屈曲点としてファン下流側辺６ｆ、ファン上流側辺６ｅが可動する。
【００９６】
また、熱交換器３が冷媒により冷却され結露水が付着する運転（冷房、除湿運転）をする場合、また吹出側流路１３壁面に取付けられた結露を感知する結露センサー１５の銅線１５ａが、結露水により通電され結露を感知して制御部１６に信号が出力された場合、さらに除塵フィルタ９にホコリが堆積しクロスフローファン４の通風抵抗が増加し、除塵フィルタ９の前後に取付けられた差圧センサー１７（図２６）の圧力値が所定値になり制御部１６に信号が出力された場合、図２６の状態から図２５に示すように突起部６ｂの頂角θが小さく、かつ突起部６ｂのスタビライザー舌部６ａのファン対向面６ｃから突起部頂点６ｂ１までの突出高さＨｓがファン外周円Ｄとスタビライザー舌部６ａの対向面６ｃとの最小隙間寸法Ｇ１に対し２５％〜３５％で、かつ略三角形の突起部の頂角θが５０〜７５°となるように突起部６ｂの二辺であるファン下流側辺６ｆ、ファン上流側辺６ｅがクロスフローファン４の回転方向Ａの逆方向へ移動しθが小さくなる。
【００９７】
その結果、クロスフローファン外周円Ｄと突起部頂点６ｂ１までの最小隙間Ｇ２（＝Ｇ１−Ｈｓ）が通常運転時に対し小さくなると共に、ファン上流側辺６ｅがクロスフローファン４方向へ傾斜し突起部頂点６ｂ１が吹出側流路１３側へ移動するため、スタビライザー６とクロスフローファン４の間の隙間Ｇを通過する吹出側流路１３から吸込側流路１２へ流れる循環渦ａが吹出側流路１３側へ移行するとともに小さくなり、ファンの吹出側における動圧が増加し吹出流れが安定する。
【００９８】
このようにスタビライザー６の突起部６ｂが可動することにより、比率Ｈｓ／Ｇ１を２５％〜３５％に維持しつつ、さらに頂角θを小さくできるため、図５、図６のように通風抵抗が増加しても従来に比べ低騒音で、図７、図８のように突起部６ｂが固定されているときに比べ通風抵抗が増加してもさらに運転可能時間の延長が図れ、除塵フィルタ９の掃除時期がさらに延長できるとともに、クロスフローファン４の運転が不安定にならないので吹出口１４から逆流してファンで着露し、この着露水が部屋へ飛散することを防止できるので、さらに高品質な空気調和機が得られる。
【００９９】
また冷房・除湿運転時、湿度が高い室内空気と温度が低い空気調和機の吹出口１４からの吹出流れが合流し、結露しやすい上下風向ベーン８の表面に結露センサー１５が配設されているので、結露を即座に感知でき制御部１６へ信号を出力することができ、図２６の状態から図２５のように結露防止の制御へ移行して着露水が部屋へ飛散することっを防止できるので、さらに高品質な空気調和機が得られる。
【０１００】
実施の形態７．
図２８、２９は実施の形態７を示す図で、図２８は除塵フィルタ９にホコリが堆積したり、冷房時のクロスフローファン４の通風抵抗が増加した時の導風板１９の動作を示したスタビライザー６近傍の部分拡大図、図２９は暖房時や除塵フィルタ９にホコリが堆積していないクロスフローファン４の通風抵抗が大きくない通常運転時のスタビライザー６近傍の部分拡大縦断面図である。
【０１０１】
尚、本実施の形態におけるスタビライザー６の形状以外の構成は前述した実施の形態１と同様であるため、同一の符号を付して説明を省略する。
【０１０２】
図２８、２９において、スタビライザー６は、クロスフローファン４に近接、対向して位置し、クロスフローファン４の吸込側流路１２と吹出側流路１３を分離する。スタビライザー６は、クロスフローファン４の回転方向Ａ（時計方向）に延びたスタビライザーの舌部６ａを有する。スタビライザーの舌部６ａには、クロスフローファン４の回転方向Ａ下流側の舌部先端部６ｃ２に、空気調和機本体１の左右に延びて形成された導風板１９が設けられている。舌部先端部６ｃ２との連結部が導風板１９の屈曲点１９ａで、屈曲点１９ａを軸に導風板１９は可動する。
【０１０３】
また図２８、図２９において、クロスフローファン４の回転方向Ａにクロスフローファン４に沿う方向の凹曲面で延びたスタビライザーの舌部６ａのファン対向面６ｃのファン回転方向Ａ上流側端部である舌部開始部６ｃ１とクロスフローファン４の各翼４ａの外周端４ｂに接するファン外周円Ｄとの最近接距離である隙間Ｇｃは、スタビライザーの舌部６ａのファン対向面６ｃのファン回転方向Ａ下流側端部である舌部先端部６ｃ２とファン外周円Ｄとの最近接距離で、ファン外周円Ｄとファン対向面６ｃと最小隙間である隙間Ｇ１に比べ大きく、つまりファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃの隙間Ｇが回転方向Ａに行くに従い小さくなるように形成されている。
【０１０４】
また、図２８のように熱交換器３が冷媒により冷却され結露水が付着する運転（冷房、除湿運転）をする場合、また吹出側流路１３壁面に取付けられた結露を感知する結露センサー１５の銅線１５ａが結露水により通電され結露を感知し制御部１６に信号が出力された場合、さらにまた除塵フィルタ９にホコリが堆積しクロスフローファン４の通風抵抗が増加し除塵フィルタ９の前後に取付けられた差圧センサー１７の圧力値が所定値になり制御部１６に信号が出力された場合、図２９の状態から図２８に示すように導風板１９は屈曲点１９ａを軸に、導風板１９の自由端１９ｂがファン内部方向へ移動するように傾斜する。
【０１０５】
このとき導風板１９のスタビライザー舌部６ａのファン対向面６ｃから導風板自由端１９ｂまでの突出高さＨｓがファン外周円Ｄとスタビライザー舌部６ａの対向面６ｃとの最小隙間寸法Ｇ１に対し２５％〜３５％となるように傾斜する。
【０１０６】
その結果クロスフローファン外周円Ｄと突起部頂点６ｂ１までの最小隙間Ｇ２（＝Ｇ１−Ｈｓ）が通常運転時に対し小さくなると共に、導風板１９がクロスフローファン４方向へ傾斜することにより、スタビライザー６とクロスフローファン４の間の隙間Ｇを通過する吹出側流路１３から吸込側流路１２へ流れる循環渦ａが吹出側流路１３側へ移行するとともに小さくなり、ファンの吹出側における動圧が増加し吹出流れが安定する。
【０１０７】
このようにスタビライザー６の導風板１９が、比率Ｈｓ／Ｇ１を２５％〜３５％の範囲に維持しつつ可動することにより、図５のように通風抵抗が増加しても従来に比べ低騒音で、図７のように突起部６ｂが固定されているときに比べ通風抵抗が増加してもさらに運転可能時間の延長が図れ、除塵フィルタ９の掃除時期がさらに延長できるとともに、クロスフローファン４の運転が不安定にならないので吹出口１４から逆流しファンで着露し、この着露水が部屋へ飛散することが防止できるのでさらに高品質な空気調和機が得られる。
【０１０８】
また冷房・除湿運転時、湿度が高い室内空気と温度が低い空気調和機の吹出口１４からの吹出流れが合流し結露しやすい上下風向ベーン８の表面に結露センサー１５が配設されているので、結露を即座に感知でき制御部１６へ信号を出力でき図２９の状態から図２８のように結露防止の制御へ移れ着露水が部屋へ飛散することが防止できるのでさらに高品質な空気調和機が得られる。
【０１０９】
【発明の効果】
この発明に係る空気調和機は、スタビライザーの舌部をクロスフローファンの回転方向へ向け徐々にクロスフローファン外周円との隙間が小さくなるように形成し、突起部の舌部のクロスフローファン対向面からの突出高さＨｓが、クロスフローファン外周円と舌部のクロスフローファン対向面との最小隙間寸法Ｇ１に対し２５〜３５％とし、突起部の頂角が５０゜〜７５゜となるように形成したことにより、除塵フィルタにホコリが堆積していっても騒音値が急激に悪化することなく、また従来に比べ空気調和機の運転可能時間の延長が図れることから、除塵フィルタの掃除時期の延長が可能であるとともに、吹出口から逆流しずらいのでクロスフローファンへの着露水の飛散の心配がない高品質な空気調和機が得られる。
【図面の簡単な説明】
【図１】実施の形態１を示す図で、空気調和機の構成を示す外観図である。
【図２】実施の形態１を示す図で、空気調和機の縦断面図である。
【図３】実施の形態１を示す図で、空気調和機のスタビライザーの舌部近傍を拡大した要部拡大図である。
【図４】実施の形態１を示す図で、空気調和機のスタビライザーの舌部近傍を拡大した要部拡大図である。
【図５】実施の形態１を示す図で、除塵フィルタにホコリがある時とない時における、ファン外周円Ｄとスタビライザーの舌部６ａのファン対向面６ｃとの最小隙間寸法Ｇ１に対する突起部６ｂの突出高さＨｓの比率Ｈｓ／Ｇ１が変化したときの同一風量時の騒音値の変化を示した図である。
【図６】実施の形態１を示す図で、除塵フィルタにホコリがある時とない時における、突起部６ｂの頂角θ変化時の同一風量時の騒音値の変化を示した図である。
【図７】実施の形態１を示す図で、除塵フィルタにホコリがある時とない時における、比率Ｈｓ／Ｇ１変化時の吹出口１４へ部屋１０の空気が逆流するまでの運転可能時間を示した図である。
【図８】実施の形態１を示す図で、除塵フィルタにホコリがある時とない時における、突起部６ｂの頂角θ変化時の吹出口１４へ部屋１０の空気が逆流するまでの運転可能時間を示した図である。
【図９】実施の形態１を示す図で、微細な空気清浄フィルタ１１を搭載したときの空気調和機の縦断面図である。
【図１０】実施の形態１を示す図で、空気調和機の正面に位置し開閉可能な前面吸込グリルの格子を減少させ開口面積を小さくしたときの空気調和機の外観図である。
【図１１】実施の形態２を示す図で、空気調和機の構成を示す縦断面図である。
【図１２】実施の形態２を示す図で、図１１の矢視Ｅ図である。
【図１３】実施の形態２を示す図で、図１２の各スタビライザー断面における拡大図である。
【図１４】実施の形態２を示す図で、従来と本発明に係る空気調和機における周波数特性図である。
【図１５】実施の形態２を示す図で、１コマに対しそれよりも突起部６ｂの方向を細かく変化させた場合の回転音ピーク値の変化図である。
【図１６】実施の形態３を示す図で、空気調和機の構成を示す縦断面図である。
【図１７】実施の形態３を示す図で、図１６の矢視Ｆ図である。
【図１８】実施の形態３を示す図で、図１７の各スタビライザー断面における拡大図である。
【図１９】実施の形態３を示す図で、スタビライザーの舌部６ａのファン対向面６ｃが凸凹形状となる場合の周波数特性図である。
【図２０】実施の形態３を示す図で、スタビライザーの舌部の凸部６ａ１及び凹部６ａ２のファン長さ方向の幅Ｓ１、Ｓ２が不等である場合の周波数特性図である。
【図２１】実施の形態４を示す図で、空気調和機の構成を示す縦断面図である。
【図２２】実施の形態５を示す図で、空気調和機の構成を示す外観図である。
【図２３】実施の形態５を示す図で、図２２の縦断面図である。
【図２４】実施の形態６を示す図で、空気調和機の構成を示す外観図である。
【図２５】実施の形態６を示す図で、除塵フィルタ９にホコリが堆積したり、冷房時のクロスフローファン４の通風抵抗が増加した時の突起部６ｂの動作を示したスタビライザー６近傍の部分拡大図である。
【図２６】実施の形態６を示す図で、暖房時や除塵フィルタ９にホコリが堆積していないクロスフローファン４の通風抵抗が大きくない通常運転時のスタビライザー６近傍の部分拡大縦断面図である。
【図２７】実施の形態６を示す図で、空気調和機本体１の上下風向ベーン８の表面に配設された結露センサー１５の部分拡大図である。
【図２８】実施の形態７を示す図で、除塵フィルタ９にホコリが堆積したり、冷房時のクロスフローファン４の通風抵抗が増加した時の導風板１９の動作を示したスタビライザー６近傍の部分拡大図である。
【図２９】実施の形態７を示す図で、暖房時や除塵フィルタ９にホコリが堆積していないクロスフローファン４の通風抵抗が大きくない通常運転時のスタビライザー６近傍の部分拡大縦断面図である。
【図３０】従来の空気調和機の縦断面図である。
【図３１】図３０の要部断面図である。
【符号の説明】
１空気調和機本体、２ａ前面吸込グリル、２ｂ上部吸込グリル、３熱交換器、４クロスフローファン、４ａ翼、４ｂ翼の外周端、４ｃ再流入点、４ｄ円形支持板、４ｅコマ、５ケーシング、６スタビライザー、６ａ舌部、６ａ１凸部、６ａ２凹部、６ｂ突起部、６ｂ１突起部頂点、６ｃ１舌部開始部、６ｃ２舌部先端部、６ｃ３舌部開始部、６ｅファン上流側辺、６ｅ１スタビライザー側端点、６ｆファン下流側辺、７左右風向ベーン、８上下風向ベーン、９除塵フィルタ、１０部屋、１０ａ壁、１１空気清浄フィルタ、１２吸込側流路、１３吹出側流路、１４吹出口、１５結露センサー、１５ａ銅線、１６制御部、１７差圧センサー、１８駆動用モータ、１９導風板、１９ａ屈曲点、１９ｂ自由端。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an air conditioner using a crossflow fan, and more specifically, it is located near and opposite the crossflow fan, and has a stabilizer shape that separates the suction-side flow path and the blow-off-side flow path of the crossflow fan. In particular, the present invention relates to the shape of a stabilizer that improves the quality of an air conditioner by improving air blowing characteristics and noise characteristics, and further suppressing variations in molding of parts.
Further, the present invention is also applied to a once-through fan using a cross flow fan.
[0002]
[Prior art]
Hereinafter, a conventional air conditioner equipped with a cross flow fan will be described. As an example of an air conditioner equipped with a conventional cross flow fan, there is one described in Japanese Patent Application Laid-Open No. 10-292926, “Air Conditioner”. 30 is a longitudinal sectional view of an air conditioner described in Japanese Patent Laid-Open No. 10-292926, and FIG. 31 is a sectional view of a main part of FIG.
[0003]
30 and 31 showing a conventional air conditioner equipped with a crossflow fan, 1 is an air conditioner body, 2a is a front suction grill that can be opened and closed, 2b is an upper suction grill, and 3 is a front suction grill 2a and an upper part. A heat exchanger for exchanging heat of the air in the room 10 sucked from the suction grill 2b, 4 is a cross flow fan having a plurality of blades directed in the fan rotation direction, and 5 is located downstream of the cross flow fan 4 for heat exchange. A casing constituting a blow-out side flow path 13 directed to a blow-out opening 14 for blowing air exchanged in the chamber 3 into the room 10, 6 is located close to and opposed to the cross-flow fan 4. 4 is a stabilizer that separates the suction side flow path 12 and the discharge side flow path 13, and 6 a is a tongue portion of the stabilizer 6 that extends in the rotational direction A of the cross flow fan 4 of the stabilizer 6, b is protrusion extending horizontally provided in the tongue portion 6a of the stabilizer, 7, 8 horizontal wind vanes provided in the air outlet 14, a vertical airflow direction vane.
[0004]
As shown in FIG. 31, the fan facing surface 6 c of the tongue portion 6 a of the stabilizer is formed in a substantially curved shape concentric with the cross flow fan 4 by a radius of curvature R spaced from the cross flow fan 4 at a predetermined interval. In addition, a projecting portion 6b extending left and right facing the cross flow fan 4 is provided in the middle of the fan rotation direction of the substantially curved fan facing surface 6c, thereby circulating around the tongue portion 6a of the stabilizer. It is possible to prevent the vortex a from being generated and preventing the air blowing characteristics and noise characteristics from being deteriorated.
[0005]
[Patent Document 1]
JP-A-10-292926
[0006]
[Problems to be solved by the invention]
However, in the conventional air conditioner using the cross flow fan described in Japanese Patent Laid-Open No. 10-292926, when the operating time has passed and dust has accumulated on the dust removal filter 9, the opening area of the suction grill is small. When the ventilation resistance increases, for example, the circulation vortex a increases, and the fan facing surface 6c of the tongue portion 6a of the stabilizer is concentric with the cross flow fan 4 due to the radius of curvature R spaced from the cross flow fan 4 at a predetermined interval. And a protrusion 6b extending left and right facing the cross flow fan 4 in the middle of the fan rotation direction of the fan facing surface 6c of the substantially curved surface portion. The contact point of the circulating vortex a that contacts the fan facing surface 6c of the tongue 6a becomes unstable.
[0007]
Furthermore, the protrusion height Hs of the protrusion 6b from the fan facing surface 6c of the stabilizer tongue 6a is such that the outer peripheral circle D in contact with the outer peripheral end 4b of each blade 4a of the crossflow fan 4 and the fan facing surface 6c of the stabilizer tongue. When the gap G2 between the outer peripheral circle D contacting the outer peripheral edge 4b of each blade 4a of the crossflow fan 4 and the projection 6b is large, the circulating vortex a is projected toward the fan inside at the projection 6b. Since the direction is not changed, the behavior of the circulating vortex a becomes unstable.
[0008]
As a result, both the air blowing characteristic and the noise characteristic are rapidly deteriorated, and particularly during cooling, the air in the room 10 flows back and dew from the outlet 14 toward the cross flow fan 4, and the dewed water is directed toward the room 10. There is a risk of scattering, and the quality of the air conditioner will deteriorate.
[0009]
Even when dust or the like is not deposited on the dust removal filter 9, the protrusion 6b has the same shape on the left and right, facing the cross flow fan 4 in the fan rotation direction on the fan facing surface 6c of the stabilizer tongue 6a. Since the reflow point 4c of the circulating vortex a into the cross flow fan 4 is substantially the same position in the fan length direction, the blade 4a is subjected to pressure fluctuation at the same timing in the length direction because of the extended configuration. Further, the timing at which the circulating vortex a collides with the fan-facing surface 6c of the stabilizer is the same, so that pressure fluctuations are applied to the blades 4a at the same time, so that a rotating sound is generated and the audibility may be deteriorated.
[0010]
The present invention was made to solve the above-mentioned problems, and suppresses deterioration of air blowing characteristics and noise characteristics against increase in ventilation resistance due to accumulation in dust removal filters such as dust and reduction of the opening area of the suction grille. In addition, during cooling, the backflow from the air outlet of the room to the crossflow fan prevents the splashing of dewed water due to dew condensation, prevents the quality of the air conditioner from deteriorating, and the air is more audible by suppressing the rotating sound. The purpose is to obtain a harmony machine.
[0011]
In addition, it suppresses the deterioration of the ventilation characteristics and noise characteristics against the increase in ventilation resistance due to the reduction of the opening area of the suction port due to dust, etc., further prevents the backflow from the air outlet of the room to the cross flow fan, and the rotating sound It aims at obtaining the stabilizer of a cross flow fan and a cross flow fan with a good audibility by suppression.
[0012]
[Means for Solving the Problems]
An air conditioner according to the present invention is an air conditioner having a cross flow fan and a stabilizer that separates a suction side flow path and a blow side flow path of the cross flow fan, and the stabilizer extends in a rotation direction of the cross flow fan. A tongue part formed so that the gap between the cross flow fan facing surface and the cross flow fan outer circumference circle gradually decreases in the direction of rotation of the cross flow fan, and the gap between the cross flow fan outer circumference circle and the tongue part And a protrusion having a substantially triangular cross-section perpendicular to the fan axial direction, which is formed to protrude toward the inside of the crossflow fan at the tip of the tongue where the cross section is minimum, and is the minimum gap with the crossflow fan. The protrusion height Hs of the tongue portion from the cross flow fan facing surface is the cross flow fan outer circumference circle and the cross flow fan facing surface of the tongue portion. Minimum gap relative dimension G1 set to 25% to 35%, the apex angle of the protrusion is characterized by being formed so that 50 ° to 75 ° of.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. The air conditioner will be described as an example having a front suction grill and an upper suction grill, but the present invention is not limited to this.
[0014]
Embodiment 1 FIG.
A cross-flow fan according to the present invention is a cross-flow fan having a cross-flow fan and a stabilizer that separates a suction-side flow path and a blow-off-side flow path of the cross-flow fan, and the stabilizer is formed to extend in the rotation direction of the cross-flow fan. The cross-flow fan facing surface gradually toward the direction of rotation of the cross-flow fan, and the gap between the outer circle of the cross-flow fan and the gap between the outer circle of the cross-flow fan and the tongue is minimized. A protrusion that protrudes toward the inside of the crossflow fan at the tip of the tongue, and has a substantially triangular cross-section perpendicular to the fan axial direction, which is the smallest gap with the crossflow fan. The protrusion height Hs of the tongue from the cross flow fan facing surface is the outer circumference of the cross flow fan and the cross flow fan facing surface of the tongue. Minimum gap relative dimension G1 set to 25% to 35%, the apex angle of the protrusion is characterized by being formed so that 50 ° to 75 ° of.
[0015]
In the cross-flow fan according to the present invention, the tongue portion of the stabilizer is formed so that the clearance from the outer circle of the cross flow fan gradually decreases in the direction of rotation of the cross flow fan, and the cross flow fan facing surface of the tongue portion of the protrusion portion Projection height Hs is 25 to 35% of the minimum gap dimension G1 between the cross flow fan outer circumference and the cross flow fan facing surface of the tongue, and the apex angle of the projection is 50 ° to 75 °. This prevents the air flow resistance and noise characteristics from deteriorating against the increase in ventilation resistance due to the reduction in the opening area of the suction port due to dust, etc., and prevents backflow from the air outlet of the room to the crossflow fan. In addition, it is possible to provide a once-through fan with good audibility by suppressing rotation noise.
[0016]
A stabilizer for a crossflow fan according to the present invention is a stabilizer for a crossflow fan that separates a suction-side flow path and a blow-out-side flow path of the crossflow fan, and is formed so as to extend in the rotation direction of the crossflow fan. The tongue is formed such that the gap between the outer surface of the cross flow fan and the outer circle of the cross flow fan gradually decreases in the direction of rotation of the cross flow fan, and the tip of the tongue that minimizes the gap between the outer circle of the cross flow fan and the tongue And a protrusion having a substantially triangular cross-section perpendicular to the fan axial direction, which is formed to protrude toward the inside of the cross flow fan and is the smallest gap with the cross flow fan, and the cross flow fan on the tongue of the protrusion The protrusion height Hs from the facing surface is the minimum gap dimension G between the outer circumference of the cross flow fan and the cross flow fan facing surface of the tongue. And 25% to 35% relative to the apex angle of the protrusion is characterized by being formed so that 50 ° to 75 °.
[0017]
The stabilizer of the crossflow fan according to the present invention is formed so that the gap between the stabilizer tongue and the outer circumference of the crossflow fan gradually decreases toward the rotation direction of the crossflow fan, and the crossflow of the tongue of the protrusion is reduced. The protrusion height Hs from the fan facing surface is 25 to 35% of the minimum gap dimension G1 between the outer circumference of the cross flow fan and the cross flow fan facing surface of the tongue, and the apex angle of the protrusion is 50 ° to 75 °. As a result, the circulation vortex of the crossflow fan is stabilized, and the backflow of air and the increase of rotating noise due to pressure fluctuation can be suppressed.
[0018]
Hereinafter, a specific embodiment of the present invention will be described in detail.
1 to 4 are diagrams showing Embodiment 1, FIG. 1 is an external view showing the configuration of an air conditioner, FIG. 2 is a longitudinal sectional view of the air conditioner, and FIGS. 3 and 4 are tongues of a stabilizer of the air conditioner. It is the principal part enlarged view which expanded the part vicinity.
[0019]
1 and 2, 1 is an air conditioner body attached to a wall 10a of a room 10, 2a is a front suction grill that can be opened and closed, 2b is an upper suction grill, and 9 is for removing large dust in the air in the room 10. A net-like dust filter 3 is a heat exchanger for exchanging heat of the air in the room 10 sucked from the front suction grill 2a and the upper suction grill 2b, 4 is a cross flow fan having a plurality of blades directed in the fan rotation direction, 5 Is a casing that forms a blow-out side flow path 13 toward the blow-out port 14 for blowing the air heat-exchanged by the heat exchanger 3 to the room 10 and located on the downstream side of the cross-flow fan 4, and 6 is a cross-flow fan 4, a stabilizer that separates the suction-side flow path 12 and the discharge-side flow path 13 of the cross flow fan 4, and 6 a is a rotation of the cross flow fan 4 of the stabilizer 6. The tongue 6 of the stabilizer 6 extending in the direction A (clockwise), 6b is a left and right protrusion provided on the tongue 6a of the stabilizer, 7 and 8 are the left and right wind vanes, and the up and down wind vanes provided at the outlet 14 It is.
[0020]
In the air conditioner equipped with the cross flow fan 4 configured as described above, when the cross flow fan 4 rotates in the direction A as shown in FIGS. 1 and 2, the detachable front suction grill 2a and the upper suction grill are provided. The air in the room 10 is sucked in from 2 b and large dust in the air is removed by the dust filter 9, then cooled or warmed by the heat exchanger 3, and then sucked into the cross flow fan 4. The air blown out from the cross flow fan 4 toward the air outlet 14 is blown up and down and left and right in the room 10 by the left and right wind direction vanes 7 and the up and down air direction vanes 8.
[0021]
3 and 4, at the upstream end of the fan rotation surface A of the fan facing surface 6c of the stabilizer tongue 6a that extends in the rotation direction A of the cross flow fan 4 along the concave curved surface in the direction along the cross flow fan 4. A gap Gc, which is the closest distance between a certain tongue start portion 6c1 and the fan outer circumference circle D in contact with the outer peripheral edge 4b of each blade 4a of the crossflow fan 4, is the direction of fan rotation of the fan facing surface 6c of the tongue 6a of the stabilizer. A The closest distance between the front end 6c2 of the tongue that is the downstream end and the fan outer circumference circle D is larger than the gap G1 that is the minimum gap between the fan outer circumference D and the fan facing surface 6c. The gap G of the fan facing surface 6c of the tongue portion 6a of the stabilizer is formed so as to become smaller in the rotation direction A.
[0022]
Further, the protrusion 6b provided on the stabilizer tongue 6a protrudes toward the inside of the fan on the tongue tip 6c2, and has a protrusion height Hs from the fan facing surface 6c of the stabilizer tongue 6a to the protrusion vertex 6b1. The entire stabilizer tongue 6a is formed in a substantially triangular shape so that the protruding height Hs is an arbitrary height with respect to the minimum gap dimension G1 between the fan outer circumference D and the fan facing surface 6c of the stabilizer tongue 6a.
[0023]
By forming the stabilizer tongue 6a in this way, the radius of curvature R spaced from the crossflow fan 4 at a predetermined interval, such as the conventional tongue 6a of the air conditioner stabilizer, is concentric with the crossflow fan 4. Compared to the configuration in which the protruding portion 6b extending left and right facing the cross flow fan 4 is provided in the middle of the fan rotation direction of the substantially curved fan-facing surface 6c in the shape of a substantially curved shape, the circulating vortex a is sharper at the protruding portion 6b. Since the gap G between the fan outer circumference D and the fan facing surface 6c of the stabilizer tongue portion decreases in the rotational direction A as in the present invention, the fan facing surface does not flow again into the fan. 6c, since it gradually re-inflows at the substantially triangular projection 6b, the behavior of the circulating vortex a is stabilized, and the through-flow vortex b passing through each blade 4a is also stabilized.
[0024]
However, when dust accumulates on the dust removal filter 9 and the ventilation resistance increases, it is provided on the stabilizer tongue end 6c2 with respect to the minimum gap dimension G1 between the fan outer circumference D and the fan facing surface 6c of the stabilizer tongue 6a. If the protruding height Hs of the substantially triangular protruding portion 6b is too low or the apex angle θ is too large, the circulating vortex a gets over the protruding portion 6b, and the circulating vortex a becomes large and becomes unstable. The air in the room 10 flows backward. On the other hand, if the protrusion height Hs is too high or the apex angle θ is too small, the circulating vortex a is suddenly turned at the protrusion 6b and becomes unstable, and the blade 4a is suddenly subjected to pressure fluctuations and rotating sound. Occurs and the noise level deteriorates.
[0025]
Therefore, there is an optimum range of the protrusion height Hs, the relationship between the fan outer circumference D and the minimum gap dimension G1 between the fan facing surface 6c of the stabilizer tongue 6a and the apex angle θ of the protrusion.
[0026]
FIG. 5 shows the noise value at the same air volume when the ratio Hs / G1 of the protrusion height Hs of the protrusion 6b to the minimum gap dimension G1 between the fan outer circumference D and the fan facing surface 6c of the stabilizer tongue 6a changes. The solid line indicates the characteristics when there is no dust on the dust filter, and the broken line indicates the characteristics when dust is accumulated on the dust filter. If the ratio Hs / G1 is 20% or more and 40% or less as shown in FIG. 5, the noise level is improving.
[0027]
FIG. 6 is a diagram showing a change in the noise value at the same air volume when the apex angle θ of the protrusion 6b is changed. As in FIG. 5, the solid line indicates that there is no dust in the dust filter, and the broken line indicates that dust accumulates on the dust filter. It is a characteristic when As shown in FIG. 6, when the apex angle θ is 50 ° to 80 °, the noise value tends to improve.
[0028]
Further, FIG. 7 is a diagram showing the operable time until the air in the room 10 flows back to the outlet 14 when the ratio Hs / G1 changes. As shown in the figure, the ratio Hs / G1 is 25% or more and 35% or less. If so, the driving time can be extended.
[0029]
Further, FIG. 8 is a diagram showing the operable time until the air in the room 10 flows back to the air outlet 14 when the apex angle θ of the protrusion 6b changes, and the apex angle θ is 75 ° as shown in FIG. If it is below, the driving time can be extended.
[0030]
From the above results, if the ratio Hs / G1 is 25% to 35% and the apex angle θ of the protrusion is 50 ° to 75 °, the noise value is drastically increased even if dust is accumulated on the dust filter 9. Since the operating time of the air conditioner can be extended as compared with the conventional one without deteriorating, it is possible to extend the cleaning time of the dust removing filter and to the cross flow fan 4 because it is difficult to reversely flow from the outlet 14. High quality air conditioner can be obtained because there is no worry of splashing of dew condensation water.
[0031]
Further, since the characteristics are not easily deteriorated even if the ventilation resistance is increased, in addition to the dust removal filter 9, a finer porous air purification filter 11 can be provided as shown in FIG. The air conditioner which can further remove the fine dust which passed through and can blow clean air-conditioned air to the room 10 is obtained.
[0032]
Furthermore, as shown in FIG. 10, since the front suction grill located on the front of the air conditioner can be opened and closed, the opening area can be reduced and the flat area can be increased on the front suction grill. What is difficult to wipe can be easily wiped and cleaned, so a clean air conditioner can be obtained.
[0033]
Embodiment 2. FIG.
The air conditioner according to the present invention is characterized in that the protrusions are formed to face in different directions in the longitudinal direction of the cross flow fan.
[0034]
The air conditioner according to the present invention has the same position in the fan length direction when the circulating vortex re-enters the cross flow fan because the protrusion is formed so as to face in a different direction in the longitudinal direction of the cross flow fan. In this case, the sound is not re-introduced, and the rotational sound is reduced and the audibility is improved, so that an air conditioner having a good audibility and a quietness can be obtained.
[0035]
Further, in the air conditioner according to the present invention, the cross flow fan is formed by connecting and fixing a plurality of pieces in which a plurality of blades extending in the fan rotation direction from the support plate are connected, and every 1/3 or more of each piece. The protrusion is formed so as to face in a different direction in the longitudinal direction of the cross flow fan.
[0036]
Further, in the air conditioner according to the present invention, the cross flow fan is formed by connecting and fixing a plurality of pieces in which a plurality of blades extending in the fan rotation direction from the support plate are connected, and every 1/3 or more of each piece. Since the protrusion is formed so as to face in a different direction in the longitudinal direction of the cross flow fan, the rotational noise is further reduced.
[0037]
The cross-flow fan according to the present invention is characterized in that the protrusion is formed to face in a different direction in the longitudinal direction of the cross flow fan.
[0038]
In the cross-flow fan according to the present invention, when the circulating vortex re-enters the cross flow fan, the protrusion is formed at the same position in the fan length direction because the protrusion is formed to face in a different direction in the longitudinal direction of the cross flow fan. Since it does not re-inflow, the rotational sound is reduced and the audibility is improved, so that a once-through fan with good audibility and silence can be obtained.
[0039]
Further, in the cross-flow fan according to the present invention, the cross flow fan is formed by connecting and fixing a plurality of pieces with a plurality of blades extending from the support plate in the fan rotation direction, and protruding at every 1/3 or more of each piece. The portion is formed to face in a different direction in the longitudinal direction of the cross flow fan.
[0040]
Further, in the cross-flow fan according to the present invention, the cross flow fan is formed by connecting and fixing a plurality of pieces with a plurality of blades extending from the support plate in the fan rotation direction, and protruding at every 1/3 or more of each piece. Since the portion is formed so as to face in a different direction in the longitudinal direction of the cross flow fan, the rotational noise is further reduced.
[0041]
The stabilizer for a crossflow fan according to the present invention is characterized in that the protrusion is formed to face in a different direction in the longitudinal direction of the crossflow fan.
[0042]
The stabilizer of the crossflow fan according to the present invention is such that when the circulating vortex re-enters the crossflow fan, the protrusion is formed in the longitudinal direction of the crossflow fan. There is no re-inflow at the same position, the rotating sound is reduced, and hearing is improved.
[0043]
In addition, the crossflow fan stabilizer according to the present invention is formed by connecting and fixing a plurality of frames in which a plurality of blades extending in the direction of rotation of the fan from the support plate are extended. Each protrusion is formed so as to face in a different direction in the longitudinal direction of the cross flow fan.
[0044]
In addition, the crossflow fan stabilizer according to the present invention is formed by connecting and fixing a plurality of frames in which a plurality of blades extending in the direction of rotation of the fan from the support plate are extended. Each time the protrusion is formed to face in the different direction in the longitudinal direction of the cross flow fan, the rotational noise is further reduced.
[0045]
Hereinafter, specific embodiments of the invention will be described in detail.
11 to 13 are diagrams showing the second embodiment, FIG. 11 is a longitudinal sectional view showing the configuration of the air conditioner, FIG. 12 is an arrow E view of FIG. 11, and FIG. 13 is an enlarged view of each stabilizer section of FIG. FIG. In addition, since structures other than the shape of the stabilizer 6 in this Embodiment are the same as that of Embodiment 1 mentioned above, the same code | symbol is attached | subjected and description is abbreviate | omitted.
[0046]
In FIG. 11, 6 is a stabilizer that is positioned close to and opposite to the cross flow fan 4, and separates the suction side flow path 12 and the blowout side flow path 13 of the cross flow fan 4, and 6 a is the cross flow fan 4 of the stabilizer 6. The tongue 6b of the stabilizer 6 extending in the rotation direction A is a substantially triangular projection provided on the tongue tip 6c2 of the stabilizer tongue 6a and extending left and right. The protrusion height Hs of the protrusion 6b and the ratio Hs / G1 of the minimum gap dimension G1 between the fan outer circumference D and the fan facing surface 6c of the stabilizer tongue 6a is 25% to 35%, and the apex angle of the protrusion θ is in the range of 50 ° to 75 °.
[0047]
In FIG. 12, which is an arrow E view of FIG. 11, the cross flow fan 4 is formed by connecting and fixing a plurality of pieces 4e each having a plurality of blades 4a extending from a circular support plate 4d. The protruding portion apex 6b1 of the protruding portion 6b is directed in a different direction for each frame 4e as shown by the cross sections JJ and KK in FIG.
[0048]
By forming the protrusion 6b of the stabilizer in this way, the circulating vortex a re-enters the cross flow fan 4 as compared to the case where the protrusion 6b is provided at the same position in the length direction of the cross flow fan 4 as in the prior art. In this case, since the reflow does not occur at the same position in the fan length direction, the rotational sound is reduced as compared with the conventional case as shown in FIG.
[0049]
Further, the projection apex 6b1 of the substantially triangular projection 6b1 of the stabilizer 6 corresponds to each frame 4e as shown in the sections LL, MM, LL, JJ, and MM in FIG. If the direction is different every half or 1/3, the rotational noise is further reduced. However, even if the direction of the protrusion 6b is changed more finely than one frame as shown in FIG. Further reduction of the peak value is small.
[0050]
By forming the stabilizer protrusion 6b as described above, an air conditioner having a good audibility and a quietness can be obtained.
[0051]
Embodiment 3 FIG.
The air conditioner according to the present invention is characterized in that the cross flow fan facing surface of the stabilizer is formed to be uneven in the length direction of the cross flow fan.
[0052]
In the air conditioner according to the present invention, the cross flow fan facing surface of the stabilizer is formed to be uneven in the length direction of the cross flow fan, so that the circulation vortex is in contact with the fan facing surface of the tongue portion of the stabilizer. Since they are not the same in the fan length direction, the time for receiving the pressure fluctuations of the blades is shifted and the rotational noise is reduced, so that an air conditioner having a good audibility and a quietness can be obtained.
[0053]
Moreover, the air conditioner according to the present invention is characterized in that the cross flow fan facing surface of the stabilizer is formed so as to be alternately uneven in the length direction of the cross flow fan.
[0054]
In addition, the air conditioner according to the present invention is an air conditioner that is more audible and quieter because the stabilizer facing surface of the cross flow fan is formed to have an uneven shape alternately in the length direction of the cross flow fan. can get.
[0055]
The air conditioner according to the present invention is characterized in that the widths of the concavo-convex shapes are unequal.
[0056]
In addition, since the air conditioner according to the present invention disperses the widths of the concavo-convex shapes, the time for receiving pressure fluctuations of the blades is dispersed, so that the rotational noise is further reduced.
[0057]
The cross-flow fan according to the present invention is characterized in that the cross flow fan facing surface of the stabilizer is formed so as to be uneven in the length direction of the cross flow fan.
[0058]
In the cross-flow fan according to the present invention, the cross flow fan facing surface of the stabilizer is formed to be uneven in the length direction of the cross flow fan, so that the circulating vortex contacts the fan facing surface of the tongue portion of the stabilizer. Since the time is not the same in the fan length direction, the time of receiving pressure fluctuations of the blades is shifted, and the rotating sound is reduced, so that a once-through fan with good audibility and quietness can be obtained.
[0059]
Further, the cross-flow fan according to the present invention is characterized in that the cross flow fan facing surface of the stabilizer is formed so as to be alternately uneven in the length direction of the cross flow fan.
[0060]
In addition, the once-through fan according to the present invention has an air conditioner that is more audible and quieter because the opposing surface of the crossflow fan of the stabilizer is formed in an uneven shape alternately in the length direction of the crossflow fan. It is done.
[0061]
Moreover, the cross-flow fan according to the present invention is characterized in that the widths of the concavo-convex shapes are made unequal.
[0062]
In addition, since the cross flow blower according to the present invention disperses the widths of the concavo-convex shapes, the time for receiving pressure fluctuations of the blades is dispersed, so that the rotational noise is further reduced.
[0063]
The stabilizer for a crossflow fan according to the present invention is characterized in that the crossflow fan facing surface of the stabilizer is formed to have an uneven shape in the lengthwise direction of the crossflow fan.
[0064]
Further, the stabilizer of the cross flow fan according to the present invention is such that the cross flow fan facing surface of the stabilizer is formed to be uneven in the length direction of the cross flow fan, so that the circulating vortex faces the fan of the tongue portion of the stabilizer. Since the time in contact with the surface is not the same in the fan length direction, the time of receiving the blade pressure fluctuation is shifted and the rotational noise is reduced.
[0065]
In addition, the stabilizer for a crossflow fan according to the present invention is characterized in that the crossflow fan facing surface of the stabilizer is formed so as to be alternately uneven in the crossflow fan length direction.
[0066]
Moreover, the stabilizer of the crossflow fan according to the present invention further reduces the rotational noise by forming the stabilizer so that the crossflow fan facing surface of the stabilizer is alternately uneven in the crossflow fan length direction.
[0067]
Moreover, the stabilizer of the crossflow fan according to the present invention is characterized in that the widths of the concavo-convex shapes are unequal.
[0068]
Further, the stabilizer of the cross flow fan according to the present invention disperses the time of receiving pressure fluctuations of the blades due to the uneven widths of the concavo-convex shapes, so that the rotational noise is further reduced.
[0069]
Hereinafter, specific embodiments of the invention will be described in detail.
16 to 18 are views showing the third embodiment, and are longitudinal sectional views showing the configuration of the air conditioner, FIG. 17 is an F view of FIG. 16, and FIG. 18 is an enlarged view of the stabilizer section of FIG. 16. In addition, since structures other than the shape of the stabilizer 6 in this Embodiment are the same as that of Embodiment 1 mentioned above, the same code | symbol is attached | subjected and description is abbreviate | omitted.
[0070]
16-18, the fan rotation direction of the fan facing surface 6c of the stabilizer tongue 6a extending in a concave curved surface centered in the fan internal direction in the rotation direction A of the cross flow fan 4 in the rotation direction A of the cross flow fan 4 A gap Gc, which is the closest distance between the tongue start portion 6c1 that is the upstream end portion of A and the fan outer circumference circle D, is the tip portion of the tongue portion that is the downstream end portion of the stabilizer tongue portion 6a in the fan rotation direction A. A convex portion 6a1 formed to be larger than the minimum gap G1 between the fan 6c2 and the fan outer circumference circle D, and a concave curved surface having a center in the fan internal direction different from the convex portion 6a1, and the gap G1 is the same and is a tongue larger than the gap Gc A concave portion 6a2 formed so as to be a gap Gd between the start portion 6c3 and the fan outer circumference circle D intersects with the convex portions 6a1, the concave portions 6a2,... In the length direction of the cross flow fan 4 as shown in FIG. Tongue 6a of the stabilizer to the fan facing surface 6c of the tongue 6a of the next stabilizer is uneven shape is formed. The protrusion height Hs of the protrusion 6b and the ratio Hs / G1 of the minimum gap dimension G1 between the fan outer circumference D and the fan facing surface 6c of the stabilizer tongue 6a is 25% to 35%, and the apex angle of the protrusion θ is in the range of 50 ° to 75 °.
[0071]
By forming the stabilizer tongue 6a in this way, the time required for the circulating vortex a like the stabilizer tongue 6a of the same shape in the longitudinal direction of the conventional fan to contact the fan facing surface 6c of the stabilizer tongue 6a. Since they are not the same in the fan length direction, the time for receiving pressure fluctuations of the blades 4a is shifted, and the rotational noise is reduced as shown in FIG.
[0072]
In particular, if the widths S1 and S2 in the fan length direction of the convex portion 6a1 and the concave portion 6a2 of the tongue portion of the stabilizer are unequal as shown in FIG. 17, the time for receiving pressure fluctuations of the blades 4a is further dispersed. Thus, the rotational noise is further reduced.
[0073]
Embodiment 4 FIG.
In the air conditioner according to the present invention, a dust filter is disposed on the downstream side of the suction grille, and a heat exchanger is disposed on the upstream side of the cross flow fan, so that fine air suspended matter can be removed between the dust filter and the heat exchanger. An air purifying filter is provided.
[0074]
In the air conditioner according to the present invention, a dust filter is disposed on the downstream side of the suction grille, and a heat exchanger is disposed on the upstream side of the cross flow fan, so that fine air suspended matter can be removed between the dust filter and the heat exchanger. Since the behavior of the circulating vortex is stable due to the installation of the air purification filter, a large air purification filter can be installed, and fine dust and suspended matters in the air that could not be removed by the dust removal filter can be removed. Thus, clean air can be blown and a hygienic and high-quality air conditioner can be obtained.
[0075]
Hereinafter, specific embodiments of the invention will be described in detail.
FIG. 21 shows the fourth embodiment and is a longitudinal sectional view showing the configuration of the air conditioner. The basic configuration in the present embodiment is the same as that of the above-described third embodiment, and thus the same reference numerals are given and description thereof is omitted.
[0076]
In FIG. 21, the ratio Hs / G1 of the minimum clearance dimension G1 between the protrusion height Hs of the substantially triangular protrusion 6b of the tongue 6a of the stabilizer and the fan outer peripheral circle D and the fan facing surface 6c of the stabilizer tongue 6a is In the range of 25% to 35%, the apex angle θ of the protrusion is in the range of 50 ° to 75 °, the protrusion 6b is directed in the opposite direction in the fan length direction, and the fan facing surface 6c of the stabilizer is uneven. It is formed to become. An air purifying filter 11 capable of removing fine air suspended matters is disposed between the dust removal filter 9 and the heat exchanger 3.
[0077]
Since the conventional air conditioner does not have the shape of the tongue of the stabilizer as in the present invention, if the ventilation resistance of the cross flow fan 4 increases, the behavior of the circulating vortex a tends to become unstable. 11 could only be installed in a small state. However, since the behavior of the circulating vortex a is stable according to the present invention, a large air cleaning filter 11 can be mounted.
[0078]
As a result of the above, a large air purification filter can be mounted, so it is possible to remove fine dust and suspended matters in the air that could not be removed by the dust removal filter, and it is possible to blow clean air and provide a hygienic and high quality air conditioner Can be obtained.
[0079]
Embodiment 5. FIG.
The air conditioner according to the present invention has a front suction grill at the front and an upper suction grill at the upper part, and the ventilation resistance of the front suction grill is larger than the ventilation resistance of the upper suction grill.
[0080]
The air conditioner according to the present invention has a front suction grille on the front surface and an upper suction grille on the top, and the airflow resistance of the front suction grille is larger than the airflow resistance of the upper suction grille, so that the wall surface of the front suction grille surface Even if the ratio of the air conditioner increases, stable operation is possible, and dust is less likely to adhere to the grill grille as in the past. As a result, clean air can be blown, and a hygienic and high quality air conditioner can get.
[0081]
Hereinafter, specific embodiments of the invention will be described in detail.
22 and 23 are diagrams showing Embodiment 5, FIG. 22 is an external view showing the configuration of the air conditioner, and FIG. 23 is a longitudinal sectional view of the air conditioner. The basic configuration in the present embodiment is the same as that of the above-described fourth embodiment, and thus the same reference numerals are given and description thereof is omitted.
[0082]
22 and 23, the ratio of the protrusion height Hs of the substantially triangular projection 6b of the tongue portion 6a of the stabilizer to the minimum gap dimension G1 between the fan outer circumference D and the fan facing surface 6c of the stabilizer tongue 6a. When G1 is 25% to 35% and the apex angle θ of the protrusion is in the range of 50 ° to 75 °, the protrusion 6b is directed in a different direction in the fan length direction, and the fan facing surface 6c of the stabilizer is uneven. It is formed to have a shape. An air purifying filter 11 capable of removing fine air suspended matters is disposed between the dust removal filter 9 and the heat exchanger 3.
[0083]
Since the conventional air conditioner does not have the shape of the stabilizer tongue as in the present invention, if the ventilation resistance of the cross flow fan 4 increases, the behavior of the circulating vortex a tends to become unstable. Not only can the clean filter 11 be mounted, but also the aerodynamic characteristics of the front suction grille 2a located in front of the air conditioner are larger than the ventilation resistance of the upper suction grille 2b, the aerodynamic characteristics deteriorate rapidly and the air outlet 14 The air has flowed back to the cross flow fan 4.
[0084]
However, since the behavior of the circulating vortex a is stabilized by forming the tongue portion 6a of the stabilizer as in the present invention, the ventilation resistance of the front suction grill 2a located in front of the air conditioner is the ventilation resistance of the upper suction grill 2b. Even in a state where the resistance is larger than the resistance, the air can be blown stably.
[0085]
As a result, since the large air purification filter 11 can be mounted, it is possible to remove fine dust in the air that could not be removed by the dust removal filter 9, and the opening of the front suction grill 2a can be made smaller, and the front suction grill 2a. Even if the proportion of the surface wall increases, stable operation is possible, and dust is less likely to adhere to the conventional grill grille. As a result, a clean air can be blown and a hygienic and high quality air conditioner can be obtained.
[0086]
In the above embodiment, an example in which the present invention is applied to an air conditioner has been described. However, the present invention can also be applied to a cross-flow fan using a cross flow fan, and by reducing the opening area of the suction port by dust or the like. It is possible to provide a once-through fan that suppresses the deterioration of the blowing characteristics and noise characteristics against the increase of the ventilation resistance, further prevents the backflow from the air outlet of the room to the cross flow fan, and has good audibility by suppressing the rotating sound.
[0087]
Embodiment 6 FIG.
24 to 27 are diagrams showing the sixth embodiment. FIG. 24 is an external view showing the configuration of the air conditioner. FIG. 25 is a diagram showing dust accumulated on the dust filter 9 or the ventilation resistance of the crossflow fan 4 during cooling. FIG. 26 is a partial enlarged view of the vicinity of the stabilizer 6 showing the operation of the protrusion 6b when the air flow increases, and FIG. 26 is a normal operation where heating resistance or the crossflow fan 4 in which dust is not accumulated on the dust filter 9 is not large. FIG. 27 is a partially enlarged view of the dew condensation sensor 15 disposed on the surface of the up-and-down airflow direction vane 8 of the air conditioner body 1.
[0088]
In addition, since structures other than the shape of the stabilizer 6 in this Embodiment are the same as that of Embodiment 1 mentioned above, the same code | symbol is attached | subjected and description is abbreviate | omitted.
[0089]
In FIG. 24, a dew condensation sensor 15 is disposed on the surface of the up and down wind direction vane 8 provided at the air outlet 14 of the air conditioner body 1. When the dew condensation sensor 15 detects dew condensation, a signal is output to the control unit 16.
[0090]
The dew condensation sensor 15 has a configuration in which, for example, several thin copper wires 15 a are stretched close to the longitudinal direction of the up-and-down airflow vanes 8. For example, as shown in FIG. 27, a straight copper wire 15a extending in the longitudinal direction from the vicinity of the end of the driving motor 18 side end of the up-and-down airflow vane 8 and the other end of the up-and-down airflow vane 8 It is comprised with the substantially U-shaped copper wire 15a extended in the direction. When water droplets adhere between the straight strip copper wire 15a and the substantially U-shaped copper wire 15a, a current is applied between them, and a signal is output to the control unit 16.
[0091]
As the dew condensation sensor 15 disposed on the up-and-down wind direction vane 8, a configuration in which several thin copper wires 15a are stretched close to the longitudinal direction of the up-and-down wind direction vane 8 is shown, but the present invention is not limited to this. It is not a thing.
[0092]
In FIGS. 25 and 26, the stabilizer 6 is located close to and opposed to the cross flow fan 4, and separates the suction side flow path 12 and the blowout side flow path 13 of the cross flow fan 4. The stabilizer 6 has a stabilizer tongue 6 a extending in the rotation direction A (clockwise) of the cross flow fan 4. On the tongue portion 6a of the stabilizer, the tongue portion tip portion 6c2 on the downstream side in the rotational direction A of the crossflow fan 4 is formed to extend to the left and right of the air conditioner body 1, and is substantially triangular convex to the crossflow fan 4 side. The protrusion 6b is provided.
[0093]
25 and 26, at the upstream end portion in the fan rotation direction A of the fan facing surface 6c of the tongue portion 6a of the stabilizer that extends in the rotation direction A of the cross flow fan 4 along the concave curved surface in the direction along the cross flow fan 4. The gap Gc, which is the closest distance between a certain tongue start portion 6c1 and the fan outer circumference circle D in contact with the outer peripheral end 4b of each blade 4a of the crossflow fan 4, is the direction of fan rotation of the fan facing surface 6c of the tongue 6a of the stabilizer. A The closest distance between the front end 6c2 of the tongue that is the downstream end and the fan outer circumference circle D is larger than the gap G1 that is the minimum gap between the fan outer circumference D and the fan facing surface 6c. The gap G of the fan facing surface 6c of the tongue portion 6a of the stabilizer is formed so as to become smaller in the rotation direction A.
[0094]
The substantially triangular protrusion 6b is composed of two sides, a fan upstream side 6e and a fan downstream side 6f. The apex angle of the projection apex 6b1 of the substantially triangular shape formed by these two sides on the cross flow fan 4 side is defined as θ. In the protrusion 6b, the stabilizer end point 6e1 of the fan upstream side 6e is connected to the stabilizer 6, and the protrusion apex 6b1 is a bending point.
[0095]
The substantially triangular projection 6b has a stabilizer side end point 6e1 as a starting point and a projection vertex 6b1 as a bending point so that the apex angle θ changes depending on the operating condition of the air conditioner, and the fan downstream side 6f and the fan upstream side 6e. Is movable.
[0096]
In addition, when the heat exchanger 3 is cooled by the refrigerant and performs an operation in which condensed water adheres (cooling or dehumidifying operation), the copper wire 15a of the condensation sensor 15 that senses the condensation attached to the wall surface of the blowout side flow path 13 When the dew condensation water is energized to detect dew condensation and a signal is output to the control unit 16, dust is further accumulated on the dust removal filter 9 and the ventilation resistance of the cross flow fan 4 is increased. When the pressure value of the differential pressure sensor 17 (FIG. 26) becomes a predetermined value and a signal is output to the control unit 16, the apex angle θ of the protrusion 6b is small as shown in FIG. 25 from the state of FIG. The protruding height Hs from the fan facing surface 6c of the stabilizer tongue 6a of the protruding portion 6b to the protruding portion apex 6b1 is 25 with respect to the minimum gap dimension G1 between the fan outer circumference D and the facing surface 6c of the stabilizer tongue 6a. The fan downstream side 6f and the fan upstream side 6e, which are the two sides of the protrusion 6b, are rotated by the cross flow fan 4 so that the apex angle θ of the substantially triangular protrusion is 50 to 75 °. Moving in the direction opposite to direction A, θ decreases.
[0097]
As a result, the minimum gap G2 (= G1-Hs) between the cross-flow fan outer circumference circle D and the protrusion vertex 6b1 becomes smaller than that during normal operation, and the fan upstream side 6e is inclined toward the cross-flow fan 4 and protrudes. Since the apex 6b1 moves to the outlet side passage 13, the circulation vortex a flowing from the outlet side passage 13 passing through the gap G between the stabilizer 6 and the cross flow fan 4 to the suction side passage 12 is blown out. As it moves to the 13th side, it becomes smaller, the dynamic pressure on the blowing side of the fan increases, and the blowing flow becomes stable.
[0098]
Since the protrusion 6b of the stabilizer 6 moves in this way, the apex angle θ can be further reduced while maintaining the ratio Hs / G1 at 25% to 35%, so that the ventilation resistance is reduced as shown in FIGS. Even if it increases, the noise can be reduced compared to the conventional case, and even if the ventilation resistance increases as compared with the case where the projection 6b is fixed as shown in FIGS. The cleaning time can be further extended, and since the operation of the crossflow fan 4 does not become unstable, it can flow backward from the air outlet 14 and dew on the fan, preventing this dew water from splashing into the room, so it is even higher quality A simple air conditioner.
[0099]
Further, during the cooling / dehumidifying operation, the indoor air having a high humidity and the blowout flow from the air outlet 14 of the air conditioner having a low temperature are merged, and the dew condensation sensor 15 is disposed on the surface of the up-and-down wind vane 8 where condensation is likely to occur. Therefore, it is possible to immediately detect dew condensation and output a signal to the control unit 16, and it is possible to prevent the dew condensation water from scattering into the room by shifting from the state of FIG. 26 to the dew condensation prevention control as shown in FIG. Therefore, a higher quality air conditioner can be obtained.
[0100]
Embodiment 7 FIG.
28 and 29 are diagrams showing the seventh embodiment, and FIG. 28 shows the operation of the air guide plate 19 when dust is accumulated on the dust filter 9 or when the ventilation resistance of the cross flow fan 4 during cooling is increased. 29 is a partially enlarged view of the vicinity of the stabilizer 6, and FIG. 29 is a partially enlarged vertical sectional view of the vicinity of the stabilizer 6 during heating and during normal operation in which the dust flow filter 4 in which dust is not deposited on the dust removal filter 9 does not have large ventilation resistance. .
[0101]
In addition, since structures other than the shape of the stabilizer 6 in this Embodiment are the same as that of Embodiment 1 mentioned above, the same code | symbol is attached | subjected and description is abbreviate | omitted.
[0102]
28 and 29, the stabilizer 6 is located close to and opposed to the cross flow fan 4, and separates the suction side flow path 12 and the blowout side flow path 13 of the cross flow fan 4. The stabilizer 6 has a stabilizer tongue 6 a extending in the rotation direction A (clockwise) of the cross flow fan 4. On the tongue portion 6 a of the stabilizer, a wind guide plate 19 is provided at the tongue portion tip portion 6 c 2 on the downstream side in the rotational direction A of the cross flow fan 4 so as to extend to the left and right of the air conditioner body 1. A connecting portion with the tongue tip 6c2 is a bending point 19a of the air guide plate 19, and the air guide plate 19 is movable around the bending point 19a.
[0103]
28 and 29, at the upstream end portion in the fan rotation direction A of the fan facing surface 6c of the tongue portion 6a of the stabilizer extending in the rotation direction A of the cross flow fan 4 along the concave curved surface in the direction along the cross flow fan 4. The gap Gc, which is the closest distance between a certain tongue start portion 6c1 and the fan outer circumference circle D in contact with the outer peripheral end 4b of each blade 4a of the crossflow fan 4, is the direction of fan rotation of the fan facing surface 6c of the tongue 6a of the stabilizer. A The closest distance between the front end 6c2 of the tongue that is the downstream end and the fan outer circumference circle D is larger than the gap G1 that is the minimum gap between the fan outer circumference D and the fan facing surface 6c. The gap G of the fan facing surface 6c of the tongue portion 6a of the stabilizer is formed so as to become smaller in the rotation direction A.
[0104]
Further, as shown in FIG. 28, when the heat exchanger 3 is cooled by the refrigerant and performs the operation in which the dew condensation water adheres (cooling, dehumidification operation), the dew condensation sensor 15 for detecting dew condensation attached to the wall surface of the outlet side flow path 13 When the copper wire 15a is energized by dew condensation water and dew condensation is detected and a signal is output to the control unit 16, dust is accumulated on the dust removal filter 9 and the ventilation resistance of the cross flow fan 4 is increased. When the pressure value of the differential pressure sensor 17 attached to is a predetermined value and a signal is output to the control unit 16, as shown in FIG. 28 from the state of FIG. 29, the air guide plate 19 has the bending point 19a as an axis. The free end 19b of the air guide plate 19 is inclined so as to move toward the inside of the fan.
[0105]
At this time, the protrusion height Hs from the fan facing surface 6c of the stabilizer tongue 6a of the air guide plate 19 to the free air guide plate free end 19b is the minimum gap dimension G1 between the fan outer circumference D and the facing surface 6c of the stabilizer tongue 6a. In contrast, it is inclined to be 25% to 35%.
[0106]
As a result, the minimum gap G2 (= G1-Hs) between the cross-flow fan outer circumference circle D and the protrusion vertex 6b1 is smaller than that during normal operation, and the air guide plate 19 is inclined toward the cross-flow fan 4, thereby stabilizing the stabilizer. 6 and the circulation vortex a flowing from the outlet side flow path 13 to the suction side flow path 12 passing through the gap G between the cross flow fan 4 and the suction side flow path 13 become smaller and move on the outlet side of the fan. The pressure increases and the blowout flow is stabilized.
[0107]
In this way, the air guide plate 19 of the stabilizer 6 moves while maintaining the ratio Hs / G1 in the range of 25% to 35%, so that the noise is lower than the conventional one even if the ventilation resistance increases as shown in FIG. Thus, even if the ventilation resistance is increased as shown in FIG. 7, the operating time can be further extended even when the ventilation resistance is increased, the cleaning time of the dust filter 9 can be further extended, and the cross flow fan 4. Since this operation does not become unstable, it is possible to prevent the dewed water from splashing into the room by flowing backward from the air outlet 14 and dewing with a fan, so that a higher quality air conditioner can be obtained.
[0108]
Further, during the cooling / dehumidifying operation, the dew condensation sensor 15 is disposed on the surface of the up-and-down air vane 8 where the indoor air having a high humidity and the blowout flow from the air outlet 14 of the air conditioner having a low temperature are merged to easily condense. 29. Condensation can be immediately detected, a signal can be output to the control unit 16, and control can be performed from the state shown in FIG. 29 to prevent condensation as shown in FIG. 28, so that the dew condensation water can be prevented from scattering into the room. Is obtained.
[0109]
【The invention's effect】
In the air conditioner according to the present invention, the tongue portion of the stabilizer is formed so that the clearance from the outer circle of the cross flow fan gradually decreases in the direction of rotation of the cross flow fan, and the tongue portion of the protruding portion faces the cross flow fan. The protrusion height Hs from the surface is 25 to 35% of the minimum gap dimension G1 between the outer circumference of the cross flow fan and the cross flow fan facing surface of the tongue, and the apex angle of the protrusion is 50 ° to 75 °. As a result, the noise level does not deteriorate rapidly even if dust is accumulated on the dust filter, and the operating time of the air conditioner can be extended compared to the conventional method. It is possible to extend the time, and since it is difficult to back flow from the outlet, a high-quality air conditioner that does not have to worry about splashing of dew condensation water to the cross flow fan can be obtained.
[Brief description of the drawings]
FIG. 1 is a diagram showing a first embodiment, and is an external view showing a configuration of an air conditioner.
FIG. 2 shows the first embodiment and is a longitudinal sectional view of the air conditioner.
FIG. 3 shows the first embodiment, and is an enlarged view of a main part in which the vicinity of a tongue portion of a stabilizer of an air conditioner is enlarged.
FIG. 4 is a diagram showing the first embodiment and is an enlarged view of a main part in which the vicinity of a tongue portion of a stabilizer of an air conditioner is enlarged.
FIG. 5 shows the first embodiment, and shows a protrusion 6b with respect to a minimum gap dimension G1 between the fan outer circumference D and the fan facing surface 6c of the stabilizer tongue 6a when the dust removal filter has and does not have dust. It is the figure which showed the change of the noise value at the time of the same air volume when ratio Hs / G1 of protrusion height Hs of this changes.
6 is a diagram illustrating the first embodiment, and is a diagram illustrating a change in noise value at the same air volume when the apex angle θ of the protrusion 6b is changed when the dust filter has dust and when there is no dust. FIG.
FIG. 7 shows the first embodiment, and shows the operation possible time until the air in the room 10 flows backward to the outlet 14 when the ratio Hs / G1 changes when the dust filter has dust. It is a figure.
FIG. 8 shows the first embodiment, and can be operated until the air in the room 10 flows backward to the air outlet 14 when the apex angle θ of the protrusion 6b changes when the dust filter has dust or not. It is the figure which showed time.
FIG. 9 shows the first embodiment and is a longitudinal sectional view of the air conditioner when a fine air purifying filter 11 is mounted.
FIG. 10 shows the first embodiment, and is an external view of the air conditioner when the opening area is reduced by reducing the grid of the front suction grill that is located in front of the air conditioner and can be opened and closed.
FIG. 11 is a longitudinal sectional view showing the configuration of the air conditioner according to the second embodiment.
12 is a diagram showing the second embodiment, and is an arrow E view of FIG. 11. FIG.
13 shows the second embodiment, and is an enlarged view of each stabilizer cross section of FIG. 12. FIG.
FIG. 14 is a diagram showing the second embodiment, and is a frequency characteristic diagram in a conventional and an air conditioner according to the present invention.
FIG. 15 is a diagram showing the second embodiment, and is a change diagram of a rotation sound peak value when the direction of the protrusion 6b is changed more finely than one frame.
FIG. 16 shows the third embodiment and is a longitudinal sectional view showing the structure of the air conditioner.
FIG. 17 is a diagram showing the third embodiment and is an F diagram of FIG. 16;
18 is a diagram showing the third embodiment, and is an enlarged view of each stabilizer cross section of FIG. 17. FIG.
FIG. 19 is a diagram illustrating the third embodiment, and is a frequency characteristic diagram when the fan facing surface 6c of the tongue portion 6a of the stabilizer has an uneven shape.
FIG. 20 is a diagram illustrating the third embodiment, and is a frequency characteristic diagram when the widths S1 and S2 in the fan length direction of the convex portions 6a1 and the concave portions 6a2 of the tongue portion of the stabilizer are unequal.
FIG. 21 shows the fourth embodiment and is a longitudinal sectional view showing the configuration of the air conditioner.
FIG. 22 is a diagram illustrating the fifth embodiment and is an external view illustrating a configuration of an air conditioner.
FIG. 23 shows the fifth embodiment, and is a longitudinal sectional view of FIG.
FIG. 24 is a diagram showing the sixth embodiment and is an external view showing the configuration of the air conditioner.
FIG. 25 is a diagram illustrating the sixth embodiment. FIG. 25 shows the operation of the protrusion 6b when dust accumulates on the dust removal filter 9 or when the ventilation resistance of the crossflow fan 4 increases during cooling. It is a partial enlarged view.
FIG. 26 is a diagram showing the sixth embodiment, and is a partially enlarged longitudinal sectional view in the vicinity of the stabilizer 6 during heating and during normal operation where the ventilation resistance of the crossflow fan 4 in which dust is not accumulated on the dust removal filter 9 is not large. is there.
27 shows the sixth embodiment and is a partially enlarged view of the dew condensation sensor 15 disposed on the surface of the up-and-down airflow direction vanes 8 of the air conditioner body 1. FIG.
FIG. 28 is a diagram illustrating the seventh embodiment, in the vicinity of the stabilizer 6 illustrating the operation of the air guide plate 19 when dust is accumulated on the dust removal filter 9 or when the ventilation resistance of the crossflow fan 4 during cooling is increased. FIG.
FIG. 29 is a diagram showing the seventh embodiment, and is a partially enlarged longitudinal sectional view in the vicinity of the stabilizer 6 during heating and during normal operation where the ventilation resistance of the crossflow fan 4 in which dust is not deposited on the dust removal filter 9 is not large. is there.
FIG. 30 is a longitudinal sectional view of a conventional air conditioner.
31 is a cross-sectional view of relevant parts in FIG. 30. FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Air conditioner main body, 2a Front suction grille, 2b Upper suction grille, 3 Heat exchanger, 4 Cross flow fan, 4a blade, 4b Outer edge of blade, 4c Re-inflow point, 4d Circular support plate, 4e frame, 5 Casing , 6 Stabilizer, 6a Tongue, 6a1 Convex, 6a2 Concave, 6b Protrusion, 6b1 Protrusion apex, 6c1 Tongue start, 6c2 Tongue tip, 6c3 Tongue start, 6e Fan upstream side, 6e1 Stabilizer Side end point, 6f Fan downstream side, 7 Left and right wind direction vanes, 8 Up and down wind direction vanes, 9 Dust removal filter, 10 rooms, 10a wall, 11 Air purification filter, 12 Suction side flow path, 13 Outlet side flow path, 14 Outlet, DESCRIPTION OF SYMBOLS 15 Condensation sensor, 15a Copper wire, 16 Control part, 17 Differential pressure sensor, 18 Driving motor, 19 Air guide plate, 19a Bending point, 19b Free end.

Claims

In an air conditioner having a cross flow fan and a stabilizer for separating the suction side flow path and the blow side flow path of the cross flow fan,
The stabilizer is formed so as to extend in the rotation direction of the cross flow fan, and the cross flow fan facing surface is formed so that the gap with the outer circle of the cross flow fan gradually decreases toward the rotation direction of the cross flow fan. Tongue and
It is formed to protrude toward the inside of the cross flow fan at the front end of the tongue where the clearance between the outer circumference of the cross flow fan and the tongue is minimum, and is orthogonal to the fan axial direction serving as the minimum clearance with the cross flow fan. A projection having a substantially triangular cross-sectional shape,
The protruding height Hs of the tongue from the crossflow fan facing surface of the tongue is 25 to 35 with respect to the minimum gap dimension G1 between the outer circumference of the crossflow fan and the crossflow fan facing surface of the tongue. %age,
An air conditioner characterized in that the projection has an apex angle of 50 ° to 75 °.

2. The air conditioner according to claim 1, wherein the protrusion is formed to face in a different direction in a longitudinal direction of the cross flow fan.

The cross flow fan is formed by connecting and fixing a plurality of pieces, each having a plurality of blades extending in the direction of fan rotation from the support plate, and the projections are provided at every third of each piece. The air conditioner according to claim 2, wherein the air conditioner is formed to face in a different direction in the longitudinal direction.

2. The air conditioner according to claim 1, wherein the surface of the stabilizer facing the cross flow fan is formed to have a concavo-convex shape in a length direction of the cross flow fan.

5. The air conditioner according to claim 4, wherein the cross flow fan facing surface of the stabilizer is formed to have an uneven shape alternately in the length direction of the cross flow fan.

The air conditioner according to claim 4 or 5, wherein widths of the uneven shapes are made unequal.

A dust removal filter is arranged on the downstream side of the suction grille, a heat exchanger is arranged on the upstream side of the cross flow fan, and an air purification filter capable of removing fine air suspended matter is arranged between the dust removal filter and the heat exchanger. The air conditioner according to claim 1, wherein

The air conditioner according to claim 1, further comprising a front suction grill on a front surface and an upper suction grill on an upper portion, wherein a ventilation resistance of the front suction grill is larger than a ventilation resistance of the upper suction grill.

In an air conditioner having a cross flow fan and a stabilizer for separating the suction side flow path and the blow side flow path of the cross flow fan,
The stabilizer is formed so as to extend in the rotation direction of the cross flow fan, and the cross flow fan facing surface is formed so that the gap with the outer circle of the cross flow fan gradually decreases toward the rotation direction of the cross flow fan. Tongue and
The apex angle of the apex of a substantially triangular shape that protrudes toward the inside of the crossflow fan at the tip of the tongue where the clearance between the outer circumference of the crossflow fan and the tongue is minimized, and is the minimum clearance with the crossflow fan A protrusion that changes so that θ decreases as the ventilation resistance of the crossflow fan increases, and the gap between the apex and the crossflow fan decreases,
An air conditioner characterized by comprising:

In an air conditioner having a cross flow fan and a stabilizer for separating the suction side flow path and the blow side flow path of the cross flow fan,
The stabilizer is formed so as to extend in the rotation direction of the cross flow fan, and the cross flow fan facing surface is formed so that the gap with the outer circle of the cross flow fan gradually decreases toward the rotation direction of the cross flow fan. Tongue and
Provided at the tip of the tongue where the clearance between the outer circumference of the cross flow fan and the tongue is minimized, and when the ventilation resistance of the cross flow fan increases, it tilts toward the inside of the fan starting from the axis on the tip of the tongue And a wind guide plate movable so as to guide the circulating vortex of the cross flow fan toward the inside of the fan, the gap with the cross flow fan is reduced,
An air conditioner characterized by comprising:

A heat exchanger provided on the upstream side of the cross-flow fan, in which the air sucked into the air conditioner and the refrigerant exchange heat;
The outlet channel wall of the outlet side channel separated by the stabilizer;
A dew condensation sensor attached to the outlet channel wall surface to sense dew;
A dust filter provided on the upstream side of the heat exchanger to remove dust in the indoor air;
A differential pressure sensor attached before and after the dust filter;
A control unit for controlling the protrusion,
And when the heat exchanger is cooled by a refrigerant and operates to adhere dew condensation water, or the dew condensation sensor that detects dew condensation attached to the wall surface of the blowout channel senses dew condensation and sends a signal to the control unit. Or when dust is accumulated on the dust removal filter and the ventilation resistance of the cross flow fan is increased, and the pressure value of the differential pressure sensor attached before and after the dust removal filter becomes a predetermined value and signals to the control unit 11. The air conditioner according to claim 9, wherein the projection or the air guide plate at the tip of the tongue moves when the air is output.

The protrusion or the air guide plate has a protrusion height Hs of the tongue from the surface facing the cross flow fan of 25 with respect to a minimum gap dimension G1 between the outer circumference of the cross flow fan and the surface facing the tongue. It moves so that it may become% -35%, The air conditioner in any one of Claims 9-11 characterized by the above-mentioned.

The protrusion is movable so that the apex angle θ of the apex of a substantially triangle that is the minimum clearance with the cross flow fan is 50 to 75 °. The air conditioner described in 1.

An air outlet vane is provided at the air outlet, and a dew condensation sensor that senses that the air outlet and the air flow passage of the cross flow fan have condensed during cooling and dehumidifying operation is provided on the surface of the air vane. The air conditioner according to any one of claims 9 to 13, wherein the air conditioner is provided.

In a cross flow fan having a cross flow fan and a stabilizer for separating the suction side flow path and the blow side flow path of the cross flow fan,
The stabilizer is formed so as to extend in the rotation direction of the cross flow fan, and the cross flow fan facing surface is formed so that the gap with the outer circle of the cross flow fan gradually decreases toward the rotation direction of the cross flow fan. Tongue and
It is formed to protrude toward the inside of the cross flow fan at the front end of the tongue where the clearance between the outer circumference of the cross flow fan and the tongue is minimum, and is orthogonal to the fan axial direction serving as the minimum clearance with the cross flow fan. A projection having a substantially triangular cross-sectional shape,
The protruding height Hs of the tongue from the crossflow fan facing surface of the tongue is 25 to 35 with respect to the minimum gap dimension G1 between the outer circumference of the crossflow fan and the crossflow fan facing surface of the tongue. %age,
A once-through fan, wherein the protrusion has an apex angle of 50 ° to 75 °.

The cross-flow blower according to claim 15, wherein the protrusion is formed to face in a different direction in a longitudinal direction of the cross flow fan.

The cross flow fan is formed by connecting and fixing a plurality of pieces, each having a plurality of blades extending in the direction of fan rotation from the support plate, and the projections are provided at every third of each piece. The cross-flow blower according to claim 16, wherein the cross-flow blower is formed to face in a different direction in the longitudinal direction.

The cross-flow blower according to claim 15, wherein the cross flow fan facing surface of the stabilizer is formed to have an uneven shape in a length direction of the cross flow fan.

The cross-flow blower according to claim 18, wherein the cross flow fan facing surface of the stabilizer is formed to have an uneven shape alternately in the length direction of the cross flow fan.

The cross-flow blower according to claim 18 or 19, wherein widths of the uneven shapes are unequal.

In the stabilizer of the cross flow fan that separates the suction side flow path and the outlet side flow path of the cross flow fan,
A tongue portion formed so as to extend in the rotation direction of the cross flow fan, and so that the gap between the cross flow fan facing surface and the outer circle of the cross flow fan gradually decreases toward the rotation direction of the cross flow fan. When,
It is formed to protrude toward the inside of the cross flow fan at the front end of the tongue where the clearance between the outer circumference of the cross flow fan and the tongue is minimum, and is orthogonal to the fan axial direction serving as the minimum clearance with the cross flow fan. A projection having a substantially triangular cross-sectional shape,
The protruding height Hs of the tongue from the crossflow fan facing surface of the tongue is 25 to 35 with respect to the minimum gap dimension G1 between the outer circumference of the crossflow fan and the crossflow fan facing surface of the tongue. %age,
A stabilizer for a cross flow fan, wherein the protrusion has an apex angle of 50 ° to 75 °.

The stabilizer for a cross flow fan according to claim 21, wherein the protrusion is formed to face in a different direction in a longitudinal direction of the cross flow fan.

The cross flow fan is formed by connecting and fixing a plurality of pieces, each having a plurality of blades extending in the direction of fan rotation from the support plate, and the projections are provided at every third of each piece. The stabilizer for a crossflow fan according to claim 22, wherein the stabilizer is formed so as to face in a different direction in the longitudinal direction.

The stabilizer of the crossflow fan according to claim 21, wherein the crossflow fan facing surface of the stabilizer is formed to have an uneven shape in a length direction of the crossflow fan.

25. The stabilizer for a cross flow fan according to claim 24, wherein the cross flow fan facing surface of the stabilizer is formed to have an uneven shape alternately in the length direction of the cross flow fan.

26. The stabilizer for a crossflow fan according to claim 24 or 25, wherein widths of the concave and convex shapes are made unequal.