JP3927349B2

JP3927349B2 - Air conditioner

Info

Publication number: JP3927349B2
Application number: JP2000077785A
Authority: JP
Inventors: 啓夫中村; 砂穂舟越; 和広遠藤; 正之野中; 恒台坂; 素生森本; 厚大塚
Original assignee: Hitachi Ltd
Current assignee: Hitachi Ltd
Priority date: 2000-03-15
Filing date: 2000-03-15
Publication date: 2007-06-06
Anticipated expiration: 2020-03-15
Also published as: JP2001263858A

Description

【０００１】
【発明の属する技術分野】
本発明は、空気調和機に係り、特に冷凍サイクルの凝縮熱で室内空気を加熱する除湿運転が可能な空気調和機に好適なものである。
【０００２】
【従来の技術】
従来の空気調和機としては、特開昭５４−４７３５３号公報に示されているものがある（従来技術１）。
【０００３】
この従来技術1のものは、圧縮機、四方弁、室外側熱交換器、冷房用絞り機構、暖房用絞り機構、室内側熱交換器、及び除湿用絞り機構等を配管で接続して冷凍サイクルを形成している。その四方弁は、圧縮機から出た冷媒流を室外側熱交換器から室内側熱交換器に流す冷房サイクルと、圧縮機から出た冷媒流を室内側熱交換器から室外側熱交換器の順に流す暖房サイクルとに切換える機能を有している。また、その冷房絞り機構は第１電磁弁と並列に接続して冷房運転時に絞り作用を行なうように室外側熱交換器と室内側熱交換器との間に設け、かつ、その暖房絞り機構は逆止弁と併設に接続して暖房運転時に絞り作用を行なうように室外側熱交換器と室内側熱交換器との間に設けている。さらには、その室内側熱交換器は、第１室内側熱交換器と第２室内側熱交換器とに分割している。また、除湿用絞り機構は第２電磁弁と並列に接続して除湿運転時に絞り作用を行なうように第１室内側熱交換器と第２室内側熱交換器との間に設けている。
【０００４】
そして、この従来技術１のものは、四方弁等の切換により、冷房サイクルによる第２室内側熱交換器、除湿用絞り機構及び室内側熱交換器の順に冷媒を流す冷房気味の除湿運転と、暖房サイクルによる室内側熱交換器、除湿用絞り機構及び第２室内側熱交換器の順に冷媒を流す暖房気味の除湿運転とを行なうことができるものである。
【０００５】
また、従来の空気調和機としては、特開平７−１５８８８８号公報に示されているものがある（従来技術２）。
【０００６】
この従来技術２のものは、圧縮機、四方弁、室外熱交換器、冷暖房用キャピラリーチューブ、室内熱交換器、及び除湿用キャピラリーチューブ等を配管で接続して冷凍サイクルを形成している。その四方弁は、圧縮機から出た冷媒流を室外熱交換器から室内熱交換器に流す冷房サイクルと、圧縮機から出た冷媒流を室内側熱交換器から室外側熱交換器の順に流す暖房サイクルとに切換える機能を有している。また、その冷暖房用キャピラリーチューブは冷暖房運転時に絞り作用を行なうように室外側熱交換器と室内側熱交換器との間に設けている。さらには、その室内側熱交換器は、蒸発器と再熱器とに分割している。また、除湿用キャピラリーチューブは除湿運転時に絞り作用を行なうように蒸発器と再熱器との間に設けている。
【０００７】
そして、この従来技術２のものは、冷房サイクルによる再熱器、除湿用キャピラリーチューブ及び蒸発器の順に冷媒を流す除湿運転を行なうことができるものであり、蒸発器と再熱器との大きさを変えた例が示されている。
【０００８】
【発明が解決しようとする課題】
しかし、従来技術１のものは、冷房サイクルによる冷房気味の除湿運転と暖房サイクルによる暖房気味の除湿運転とを行なえるようにしたことが示されているが、室内側熱交換器を第１室内側熱交換器と第２室内熱交換器とに分割する大きさについては何ら開示されておらず（但し、図面には単に同等の大きさの第１室内側熱交換器と第２室内側熱交換器が示されている）、冷房サイクルによる除湿運転と暖房サイクルによる除湿運転の温度範囲をさらに広げて、夏場でも十分に低い吹出空気温度の除湿運転を行なえるようにすること、及び冬場でも十分に高い吹出温度の除湿運転を行なえるようにするために、室内側熱交換器を異なる大きさの第１室内側熱交換器と第２室内側熱交換器とに分割することについては開示されていない。
【０００９】
そして、従来技術２のものは、冷房サイクルによる冷房気味の除湿運転と暖房サイクルによる暖房気味の除湿運転との必要冷媒量が異なることによる性能低下の改善についても何ら開示されていない。また、冷房サイクルによる冷房気味の除湿運転と暖房サイクルによる暖房気味の除湿運転とが可能な空気調和機において、除湿絞り装置の冷媒流が正逆両方向になっても開閉可能でかつ絞り作用を有する除湿絞り装置を備えることについても何ら開示されていない。
【００１０】
また、従来技術２のものは、蒸発器と再熱器の大きさを変化させた例が示されているが、単に冷房サイクルによる除湿運転の場合について示されているに過ぎず、冷房サイクルによる除湿運転と暖房サイクルによる除湿運転とに関連して蒸発器と再熱器の大きさを変えることについては開示されていない。
【００１１】
本発明の目的は、冷房サイクルによる除湿運転及び暖房サイクルによる除湿運転の温度範囲をさらに広くすることができると共にそれぞれの除湿運転に適正な冷媒量にすることができ、これにより快適で高性能な除湿運転を行なうことができる空気調和機を提供することにある。
【００１２】
本発明の別の目的は、冷房サイクルによる除湿運転と暖房サイクルによる除湿運転のそれぞれに必要な冷媒量をより一層適量に調節することができ、これにより高性能な除湿運転ができる空気調和機を提供することにある。
【００１３】
本発明の別の目的は、冷媒流が正逆両方向になっても開閉可能でかつ絞り作用を有する除湿絞り装置を備え、これにより簡単な構成で、快適かつ高性能な除湿運転ができる空気調和機を提供することにある。
【００１４】
本発明の別の目的は、冷房サイクルによる除湿運転と暖房サイクルによる除湿運転において、さらに送風機や圧縮機の能力制御により広い外気温度範囲にわたって快適で高性能な除湿運転ができる空気調和機を提供することにある。
【００１５】
【課題を解決するための手段】
上記目的を達成するために、本発明は、圧縮機、運転切換弁、室外熱交換器、冷暖房絞り装置、室内熱交換器、及び除湿絞り装置を配管で接続して形成された冷凍サイクルと、前記室外熱交換器に通風する室外ファンと、前記室内熱交換器に通風する室内ファンとを備え、前記運転切換弁は、前記圧縮機から出た冷媒流を前記室外熱交換器から前記室内熱交換器に流す冷房サイクルと、前記圧縮機から出た冷媒流を前記室内熱交換器から室外熱交換器の順に流す暖房サイクルとに切換える機能を有するものであり、前記冷暖房絞り装置は冷房運転時及び暖房運転時に絞り作用を行なうように前記室外熱交換器と前記室内熱交換器との間に設けられたものであり、前記室内熱交換器は第１室内熱交換器と第２室内熱交換器とを有するものであり、前記除湿絞り装置は除湿運転時に絞り作用を行なうように前記第１室内熱交換器と第２室内熱交換器との間に設けられたものであり、除湿運転として、前記冷房サイクルによる前記室外熱交換器、前記第２室内熱交換器、前記除湿絞り装置及び前記第１室内熱交換器の順に冷媒を流す除湿運転と、前記暖房サイクルによる前記第１室内熱交換器、前記除湿絞り装置、前記第２室内熱交換器及び前記室外熱交換器の順に冷媒を流す除湿運転とを有する空気調和機において、前記暖房サイクルによる除湿運転時に凝縮器となる前記第１室内熱交換器を、前記暖房サイクルによる除湿運転時に蒸発器となる前記第２室内熱交換器よりも大きくしたことにある。
係る本発明において、より好ましくは、前記室外ファンを、前記冷房サイクルによる除湿運転時と前記暖房サイクルによる除湿運転時とで異なる設定条件により、それぞれの除湿運転に適した冷媒量となるように回転数制御することにある。
【００２５】
【発明の実施の形態】
以下、本発明の各実施例を図を用いて説明する。なお、第２実施例以降の実施例においては第１実施例と共通する構成の一部を省略すると共に、重複する説明を省略する。各実施例の図における同一符号は同一物又は相当物を示す。
【００２６】
まず、本発明の第1実施例を図１及び図２を用いて説明する。図１は本発明の第１実施例の空気調和機の冷房サイクルによる除湿運転時の構成図、図２は図１の暖房サイクルによる除湿運転時の構成図である。
【００２７】
冷凍サイクルは、回転数制御等による能力可変圧縮機１４、冷房サイクル及び暖房サイクルを切り換える運転切換弁である四方弁１５、室外熱交換器１６、絞り作用の無い全開状態が可能でかつ絞り量をモータ等により広い範囲で連続的に変えられる電動膨張弁タイプの冷暖房絞り装置１７、多段曲げ室内熱交換器２及び除湿絞り装置７を接続配管により環状に接続して構成している。
【００２８】
なお、冷房サイクルとは、圧縮機１４から出た冷媒流を室外熱交換器１６から室内熱交換器２に流すサイクルであり、冷房運転及び冷房気味を含む除湿運転等で適用される。また、暖房サイクルとは、圧縮機１４から出た冷媒流を室内熱交換器２から室外熱交換器１６に流すサイクルであり、暖房運転及び暖房気味を含む除湿運転等で適用される。
【００２９】
冷暖房絞り装置１７は室内熱交換器２と室外熱交換器１６との間に接続されている。さらには、室外熱交換器１６に通風する室外ファン１８及び室内熱交換器２に通風する室内ファン８を備えている。室外ファン１８は、プロペラファンで構成され、回転数を制御してその通風能力を可変とすることができるようになっている。また、室内ファン８は、貫流ファンで構成され、回転数を制御してその通風能力を可変とすることができるようになっている。
【００３０】
室内機１には、室内熱交換器２、室内ファン８及び冷暖房絞り装置１７を有している。室内熱交換器２は、多段（３段）に曲げた構造であり、二段に曲げた第１室内熱交換器３とこれより伝熱面積の小さい第２室内熱交換器４とから成っている。第１室内熱交換器３は前面側に配置され、第２室内熱交換器４は背面側に配置される。この第１室内熱交換器３と第２室内熱交換器４は、熱的に分離された略山形の構造になっており、室内機ケーシング９内に配置されている。なお、第１室内熱交換器３は第２室内熱交換器４の２倍からそれ以上の伝熱面積となるように構成されている。そして、第１室内熱交換器３と第２室内熱交換器４の直下にはそれぞれ別個の露受皿５、６が設けられている。これにより、第１室内熱交換器３で発生した除湿水は露受皿５で受けられて外部へ導かれ、第２室内熱交換器４で発生した除湿水は露受皿６で受けられて外部へ導かれる。
【００３１】
第１室内熱交換器３と第２室内熱交換器４との間には、冷房及び暖房運転時には流通抵抗の非常に小さい全開状態となり、除湿運転時に絞り作用を行う除湿絞り装置７が接続されている。
【００３２】
室内ファン８は、第１室内熱交換器３の後方でかつ第２室内熱交換器４の下方に位置して室内機１のケーシング９内に配置され、矢印で示す吸込気流１１、１２のように室内空気を第１室内熱交換器３及び第２室内熱交換器４を通して吸込み、矢印で示す吹出気流１３のように室内へ吹出すように運転される。第１室内熱交換器３及び第２室内熱交換器４で熱交換された室内空気は、室内ファン８により混合されて室内へ吹出される。
【００３３】
除湿運転は、四方弁１５、除湿絞り装置７及び冷暖房絞り装置１７の動作により冷房サイクルによる除湿運転と暖房サイクルによる除湿運転が可能である。
【００３４】
まず、冷房サイクルによる除湿運転を図１を参照して説明する。この冷房サイクルによる除湿運転は、四方弁１５が冷房サイクルを構成するように動作させ、冷暖房絞り装置１７を全開にすると共に、除湿絞り装置７を絞ることにより、冷媒を、実線矢印で示すように、圧縮機１４、四方弁１５、室外熱交換器１６、電動膨張弁１７、第２室内熱交換器４、除湿絞り装置７、第１室内熱交換器３、四方弁１５、圧縮機１４の順に循環させ、室外熱交換器１６が上流側の凝縮器、第２室内熱交換器４が下流側の凝縮器、第１室内熱交換器３が蒸発器となるように運転する。
【００３５】
そして、室内ファン８により室内空気を吸込気流１１、１２のように吸い込んで室内熱交換器２を通過させ、吹出気流１３のように吹出すことにより、室内空気は、蒸発器として作用する第１室内熱交換器３で冷却・除湿されると同時に、下流側の凝縮器すなわち加熱器となる室内背面熱交換４で加熱され、これらが混合されて室内に吹出気流１３のように吹き出される。このようにして、室内空気は除湿される。そして、第１室内熱交換器３で生じた除湿水は、下方に流れ、凝縮器となる第２室内熱交換器４にかかって再蒸発すること無く露受皿５に集められ、さらに室外に排水される。
【００３６】
この冷房サイクルによる除湿運転において、室外ファン１８の送風量を増すと、室外熱交換器１６での放熱量が増え第２室内熱交換器４からの放熱量が減って吹出空気流１３の温度が下がる。また、圧縮機１４の能力を増したり室外ファン１８の送風量を増すと、蒸発温度が下がって第１室内熱交換器３での除湿能力が増大し、吹出空気流１３の湿度を下げることができる。さらに、室内ファン８の送風量を変化させることによっても吹出空気流１３の温度や湿度が変化するが、基本的には室外ファン１８と圧縮機１４の制御をベースにして、吹出空気流１３の温度や湿度を細かく制御することができる。この場合、室内熱交換器２において、蒸発器となる第１室内熱交換器３の伝熱面積を凝縮器となる第２室内熱交換器４に比べて大きくしてあるため、第１室内熱交換器３での冷却能力を第２室内熱交換器４の加熱能力より十分大きくすることができる。なお、第１室内熱交換器３の伝熱面積を第２室内熱交換器４の伝熱面積の２倍からそれ以上に大きく構成してあるため、第１室内熱交換器３での冷却能力を第２室内熱交換器４での加熱能力より著しく大きくすることができる。
【００３７】
このように、冷房サイクルによる除湿運転は、春先や晩秋の肌寒い時には吹出空気流の温度を室温より高くする暖房ぎみ除湿運転、春や秋の外気温が比較的快適な時に吹出空気流の温度を室温と同等にする等温除湿運転が行えることはもちろん、梅雨時から初夏にかけてはもちろんのこと、夏場において、空気の冷却能力が多く要求される時に吹出空気温度を下げた快適な除湿運転を行うことができる。特に、第１室内熱交換器３の伝熱面積を第２室内熱交換器４の伝熱面積より大きくしたことにより、除湿運転における吹出空気温度を下げる範囲が広がり、湿度を大きく低下させて快適な冷房気味の除湿運転を冷房運転の代わりとして使うことができる。
【００３８】
なお、冷房運転時は、四方弁１５が冷房サイクルを構成するように動作させ、除湿絞り装置７を全開させると共に冷暖房絞り装置１７を適切な絞り量に調節することにより、冷媒流を、圧縮機１４、四方弁１５、室外熱交換器１６、冷暖房絞り装置１７、第２室内熱交換器４、除湿絞り装置７、第１室内熱交換器３、四方弁１５及び圧縮機１４の順に循環させ、室外熱交換器１６を凝縮器として作用させて室外空気に放熱し、第２室内熱交換器４及び第１室内熱交換器３を蒸発器として作用させて室内空気を冷却し、所定の冷房を行う。
【００３９】
次に、暖房サイクルによる除湿運転を図２を参照して説明する。この暖房サイクルによる除湿運転は、四方弁１５が暖房サイクルを構成するように動作させ、冷暖房絞り装置１７を適当に開くと共に、除湿絞り装置７を絞ることにより、冷媒を、破線矢印で示すように、圧縮機１４、四方弁１５、第１室内熱交換器３、除湿絞り装置７、第２室内熱交換器４、電動膨張弁１７、室外熱交換器１６、四方弁１５、圧縮機１４の順に循環させ、第１室内熱交換器３が凝縮器、第２室内熱交換器４が上流側の蒸発器、室外熱交換器１６が下流側の蒸発器となるように運転する。
【００４０】
そして、室内ファン８により室内空気を吸込気流１１、１２のように吸い込んで室内熱交換器２を通過させて吹出気流１３のように吹出すことにより、室内空気は凝縮器となる寸法が大きい方の第１室内熱交換器３で加熱されると同時に蒸発器となる寸法が小さいほうの第２室内熱交換器４で冷却・除湿され、これらが混合されて室内に吹き出される。このようにして、室内空気は除湿される。そして、第２室内熱交換器４で生じた除湿水は、下方に流れ、凝縮器となる第１室内熱交換器３にかかって再蒸発すること無く露受皿６に集められ、さらに室外に排水される。
【００４１】
この暖房サイクルによる除湿運転において、凝縮器となる第１室内熱交換器３では、上流側蒸発器となる第２室内熱交換器４での吸熱量だけでなく、これよりはるかに大きい下流側蒸発器となる室外熱交換器１６での外気からの吸熱量が加わって放熱に利用することができるため、室内吸込空気の加熱量を前述の冷房サイクルによる除湿運転よりはるかに多くでき、また、第１室内熱交換器３の寸法を第２室内熱交換器４より大きくしてあるため、凝縮圧力が異常に高くなること無く、吹出空気流１３の温度を室温より十分に高くできる。なお、第１室内熱交換器３の伝熱面積を第２室内熱交換器４の伝熱面積の２倍からそれ以上に大きく構成してあるため、第１室内熱交換器３での加熱能力を第２室内熱交換器４での冷却能力より著しく大きくすることができる。
【００４２】
この暖房サイクルによる除湿運転において、室外ファン１８の送風量や圧縮機１４の能力を増すと、室外熱交換器１６での吸熱量が増えて第１室内熱交換器３からの放熱量が増えるため、吹出空気流１３の温度をいっそう高くできる。圧縮機１４の能力を増すと、蒸発温度が低下して第２室内熱交換器４での除湿能力が増大し、吹出空気流１３の湿度を大幅に下げることができる。さらに、室内ファン８の送風量によっても吹出空気流１３の温度や湿度が変化するが、基本的には上記室外ファンと圧縮機の制御をベースにして、吹出気流１３の温度や湿度を細かく制御することができる。
【００４３】
このようにして、暖房サイクルによる除湿運転は、吹出気流１３の温度が室温より十分に高くすることができ、春先や晩秋の肌寒い時に暖房気味の除湿運転を行えることはもちろん、冬場においても、吹出空気温度を十分高くした暖房気味の除湿運転を行なうことができ、これにより気温はそれ程低くないが湿度の高い時の暖房兼除湿の目的で使ったり、温度が低く湿度が高い時に窓等への結露を防止するために除湿の目的で使う（これは裏日本のように冬の湿度が高い地域には特に有効である）ことができる。
【００４４】
なお、暖房運転時は、四方弁１５が暖房サイクルを構成するように動作させ、除湿絞り装置７を全開させると共に、冷暖房絞り装置１７を適切な絞り量に調節することにより、冷媒流を、圧縮機１４、四方弁１５、第１室内熱交換器３、除湿絞り装置７、第２室内熱交換器４、冷暖房絞り装置１７、室外熱交換器１６、四方弁１５及び圧縮機１４の順に循環させ、第１室内熱交換器３及び第２室内熱交換器４を凝縮器として作用させて室内空気を加熱し、室外熱交換器１６を蒸発器として作用させて室外空気から吸熱して所定の暖房を行う。
【００４５】
次に、本発明の第２実施例を図３を用いて説明する。図３は本発明の第２実施例の室内機の構成図である。
【００４６】
この第２実施例は、第１実施例における二段に曲げた第１室内熱交換器３を直線状の一段の第１室内熱交換器にしたものである。これにより、第１実施例と同様の動作、機能及び効果を得ることができると共に、第1室内熱交換器３の構造を単純にでき、コスト低減に結び付けることができる。
【００４７】
次に、本発明の第３実施例を図４を用いて説明する。図４は本発明の第３実施例の室内機の構成図である。
【００４８】
この第３実施例は、室内熱交換器２を寸法の小さい第２室内熱交換器４と寸法の大きい第１室内熱交換器３に熱的に分離して上下方向に配置し、さらに露受皿６を第２室内熱交換器４の下端に独立して設けたものであり、第１および第２実施例における室内機の前面から背面にかけて設けた室内熱交換器２を上下方向に伸ばして設けたものである。従って、第３実施例は、第１及び第２実施例と同様の動作、機能及び効果を得ることができ、暖房サイクルによる除湿運転においても、蒸発器となる第２室内熱交換器４で生じた除湿水は、露受皿６に集められて室外に排水されるため、凝縮器となる第１室内熱交換器３にかかって再蒸発することが無い。この第３実施例では室内熱交換器２の前後方向の寸法を小さくすることができるので、室内機を薄形にすることができる。
【００４９】
次に、本発明の第４実施例を図５を用いて説明する。図５は本発明の第４実施例の室内熱交換器と室外熱交換器の配管径を比較して説明する図である。図５（ａ）はクロスフィンタイプの室内熱交換器２の一部分を示す図、図５（ｂ）はクロスフィンタイプの室外熱交換器１６の一部分を示す図である。
【００５０】
上述した冷房サイクルによる除湿運転と暖房サイクルによる除湿運転ではそれぞれに最適な冷媒封入量が異なる。一般に、冷媒は高圧で液冷媒となるサブクール領域のある凝縮器に多く存在する。従って、冷房サイクルによる除湿運転では、室外熱交換器１６と第２室内熱交換器４が凝縮器となり、しかも室外熱交換器１６は室内熱交換器２に比べて寸法が大きいことから、必要冷媒量が多くなる。これに対し、暖房サイクルによる除湿運転では、凝縮器となるのは第１室内熱交換器３だけで小さいことから、必要冷媒量が少なくなる。上述した実施例では、凝縮器となる第１室内熱交換器３を蒸発器となる第２室内熱交換器４より大きくしているので、冷房サイクルによる除湿運転と暖房サイクルによる除湿運転の必要冷媒量の相違を調整でき、高性能の除湿運転をすることができるが、場合によっては暖房サイクルによる除湿運転で冷媒量が余ってしまう場合が想定される。
【００５１】
そこで、第４実施例では、この必要冷媒量のアンバランスを調整するために、室外熱交換器１６の伝熱管３３の内径ｄ₂を室内熱交換器２の伝熱管３１の内径ｄ₁より小さくしてある（ｄ₂＜ｄ₁）。この結果、冷房サイクルによる除湿運転時では、室外熱交換器１６が凝縮器となるが、伝熱管３３の内径ｄ₂が小さいため、室外熱交換器１６の中に存在する冷媒量が減り、必要冷媒量が暖房サイクルによる除湿運転の必要冷媒量に近づけることができ、両除湿運転ともによりいっそう適正な冷媒量の状態で運転できる。なお、この冷媒量調整のための第４実施例は、第１実施例から第３実施例に適用できる。
【００５２】
次に、本発明の第５実施例を図６を用いて説明する。図６は本発明の第５実施例の空気調和機の構成図である。
【００５３】
この第５実施例は必要冷媒量を調整するための他の実施例を示す。この第５実施例は、第１実施例において、第１室内熱交換器３と四方弁１５との間の接続管３５にこれをバイパスするバイパス管３６を設け、さらにこのバイパス管３６上に第１室内熱交換器３側の接続点Ａから四方弁側の接続点Ｂに向って二方弁３７と冷媒タンク３８を直列に接続して設けたものである。
【００５４】
この構成において、冷房サイクルによる除湿運転では、二方弁３７を開くことにより、蒸発器となる第１室内熱交換器３を出た低温・低圧のガス冷媒流は、接続管３５をＡ点からＢ点に流れると同時にバイパス管３６をＡ点から二方弁３７、冷媒タンク３８を通ってＢ点に流れる。この場合、冷媒タンク３８には常にガス冷媒流が流れると同時に周囲温度が飽和温度より高いため、内部には液冷媒が溜まらない。また、暖房サイクルによる除湿運転では、二方弁３７を閉じることにより、四方弁１５を出た高温・高圧のガス冷媒は接続管３５をＢ点からＡ点に流れるが、バイパス管３６を通る冷媒流は二方弁３７によって止められる。この結果、冷媒タンク３８内の冷媒は、飽和温度に比べて周囲温度が低いため、凝縮して液冷媒となって溜まる。従って、第５実施例では、冷媒量が過多となる暖房サイクルによる除湿運転時にのみ冷媒タンク内に液冷媒がたまることになり、冷房サイクルによる除湿運転および暖房サイクルによる除湿運転の場合ともよりいっそう適正な冷媒量の状態で運転することができる。
【００５５】
なお、第５実施例において、冷房運転及び暖房運転の時には二方弁３７を開くと、冷媒タンク３８にはガス冷媒が流れ液冷媒が溜まることが無いため、冷媒タンク３８が無いのと同じ適正冷媒量の状態で運転できる。
【００５６】
また、第５実施例は、第１及び第２実施例にも適用できて同様の効果を得ることができるが、特に室内熱交換器の寸法をあまり大きくできず第１室内熱交換器を十分大きくできない第３実施例に適用する場合に特に有効である。
【００５７】
次に、本発明の第６実施例を説明する。第６実施例は、前述した第１から第５実施例の空気調和機の構成において、室外ファン１８を冷房サイクルによる除湿運転時と暖房サイクルによる除湿運転時とで異なる設定条件により回転数制御するようにしたものであり、これによりそれぞれの除湿運転により適した冷媒量で運転を行なうことができ、快適性を向上することができるものである。また、圧縮機１４を冷房サイクルによる除湿運転時と暖房サイクルによる除湿運転時とで異なる設定条件により運転能力を制御するようにしたものであり、これによりそれぞれの除湿運転により適した冷媒量で運転を行なうことができ、快適性を向上することができるようにしたものである。さらには、圧縮機１４、室外ファン１８及び室内ファン８を冷房サイクルによる除湿運転時と暖房サイクルによる除湿運転時とで異なる複数の組み合せで能力制御するようにしたものであり、これによりそれぞれの除湿運転によりいっそう適した冷媒量で運転を行なうことができ、快適性を向上することができる。
【００５８】
室外ファン１８及び圧縮機１４を制御する場合について具体的に説明する。暖房サイクルによる除湿運転において、室外ファン１８を回転して送風運転させると、蒸発器となる室外熱交換器１６の伝熱管内で液・ガス二相冷媒中の液冷媒が外側空気から吸熱して蒸発し、ガス冷媒となる。そして、ガスは体積が大きいことから伝熱管内はほとんどガス冷媒で占められ、伝熱管内に保有される冷媒量が少なくなる。ここで、室外ファン１８を止めるか送風量を十分少なくしておけば、室外熱交換器１６内の液冷媒の蒸発は非常に少なくなり、室外熱交換器１６に比較的多くの液冷媒を溜めておくことができ、室外熱交換器１６を液冷媒溜めとして利用することができる。この場合、圧縮機の能力をそれ程大きくしなければ（暖房サイクルによる除湿運転時に圧縮機を低能力状態で運転することにより）、室外熱交換器内に溜まった液冷媒が圧縮機１４に戻る液戻りはほとんど問題にならない程度になる。以上より、暖房サイクルによる除湿運転時には、室外ファン１８を運転しないか送風量を十分少なくし、圧縮機１４の能力を低くすることにより、冷房サイクルによる除湿運転との必要冷媒量のアンバランスを調整することができる。
【００５９】
なお、以上に述べた冷房サイクルによる除湿運転と暖房サイクルによる除湿運転との必要冷媒冷媒量の調整方法は、各調整方法を単独で用いても良く、あるいは必要に応じて複数の方法を組み合わせて実施することもできる。
【００６０】
次に、本発明の第１実施例における除湿絞り弁装置の一例を図７及び図８を用いて説明する。図７は図１の空気調和機の除湿絞り装置の一例の除湿運転時の断面図、図８は図７の除湿絞り装置の冷暖房運転時の断面図である。
【００６１】
第１実施例の除湿絞り装置７において、冷媒流は、図１の冷房サイクルによる除湿運転では室外熱交換器１６から室内熱交換器２の方向に流れ、図２の暖房サイクルによる除湿運転では室内熱交換器２から室外熱交換器１６の方向に流れ、互いに逆方向に流れる。このような除湿絞り装置７に、電磁石を用いて弁体を弁座に対して上下に移動し弁ポートの開閉を行う二方弁タイプを用いた場合には、暖房サイクルによる除湿運転の時に、弁体が冷媒流によって押し上げられ、弁が開状態になり絞り装置として働かなくなってしまう。
【００６２】
そこで、図７及び図８に示す除湿絞り装置７は、弁の開閉動作をステッピングモータで行うようにしたものである。弁部Ａは、弁座４１により弁ポート４２を形成した弁本体４０と、弁ポート４２内を図中上下方向に移動可能な弁体４３とから構成されている。弁本体４０には第１接続管４４と第２接続管４５が取り付けられている。ステッピングモータ部Ｂは、弁本体４０に取り付けられる密閉ケース４６と、この密閉ケース４６の外側に配置されるステータコイル４５と、この密閉ケース４６の内側に設けられる永久磁石４９と、スリーブ５０及びケース軸受４７に支持された中心軸５１より成るロータ４８とから構成されている。なお、永久磁石４９はステータコイル４５により回転される。また、弁体４３と中心軸５１は雄ネジ部５２ａを設けた弁連結部５２によって連結され、さらに弁本体４０内には雌ネジ部５３ａを設けたブッシュ５３が固定されており、この雌ネジ部５３ａと前記雄ネジ部５２ａが互いに噛み合うように配置されている。そしてこの噛み合いにより、ロータ４８を回転させると、弁体４３が図中上下方向に移動して、弁ポート４２の開閉が行われる。
【００６３】
以上の構成により、除湿運転時には、図７のように、ロータ４８を回転させ、弁体４３を弁ポート４２が閉じるように下方に移動させ、冷媒を弁体４３と弁ポート４２との間にできた絞り隙間５４に流して絞り作用を行う。ここで例えば冷房サイクルによる除湿運転時に、冷媒を第１接続管４４から第２接続管４５の方向に流すと、暖房サイクルによる除湿運転では、冷媒が第２接続管４５から第１接続管４４の方に流れ、第２接続管４５から入った冷媒流は弁体４３を上に押し上げて弁ポート４２を開く方向に作用する。しかし弁体４３は、弁連結部の雄ネジ部５２ａとブッシュの雌ネジ部５３ａとの噛み合いにより上下動が拘束されているため、弁は開くことなく、絞り作用を行うことができる。場合によっては、ステッピングモータは、ステータコイル４５に通電することによりロータ４８が回転しないように拘束できることから、さらに確実に弁体４３が上下方向に動かないように固定できる。
【００６４】
なお、以上の説明において、冷媒の流れを冷房サイクルによる除湿運転と暖房サイクルによる除湿運転で逆にして、冷房サイクルによる除湿運転の時に冷媒流が弁体４３の下方からぶつかるように流れても同様の同様の機能・効果が得られ、確実に絞り作用を行うことができる。
【００６５】
また、冷房及び暖房運転の場合には、図８のように、ロータ４８を回転により弁体４３を上方に移動させ、弁ポート４２を開く。これにより冷媒流は弁部Ａをほとんど流通抵抗のない状態で流れ、性能の低下を防げる。
【００６６】
なお、図７及び図８においては弁の開閉動作にステッピングモータを用いたが、これに限らず、回転の位置を制御できるモータであれば他の方式のモータを用いて同様の動作及び同様の効果を得ることができる。
【００６７】
次に、本発明の第１実施例における除湿絞り弁装置の異なる例を図９を用いて説明する。図９は図１の空気調和機の除湿絞り装置の異なる例の構成図である。
【００６８】
この除湿絞り装置７は、冷媒流の正逆方向に対して流路の開閉が行える二方弁６０とキャピラリーチューブ６１を並列に接続した構成にしたものであり、また６２は第１接続管、６３は第２接続管である。この構成において、冷房サイクルによる除湿運転と暖房サイクルによる除湿運転の時には、二方弁６０を閉じ、キャピラリーチューブ６１を絞り装置として使用することにより、二方弁６０を通ろうとする冷媒流が遮断され、両除湿運転ともキャピラリチューブ６１により安定した絞り作用が行われる。また冷房及び暖房運転の場合には、二方弁６０が開き、冷媒流がこの二方弁６０をほとんど抵抗なく流れるようにする。この結果、第１接続管６２と第２接続管６３がほとんど流通抵抗の無い状態で連通され、除湿絞り装置による損失がほとんど無い状態で冷房及び暖房運転を行える。
【００６９】
本発明は、上述した各実施例に限定されるものではなく、室内側熱交換器２の各部分を必要に応じてそれぞれ多段に曲げたり、円弧状にすることもできる。特に小形の空気調和機であるルームエアコン等では、室内熱交換器を収納するスペースが十分に取れないことが多く、この場合には室内熱交換器の曲げ回数を多くしたり、曲線上にすることにより、狭いスペースに十分な伝熱面積を持つ室内熱交換器を収納でき、冷房、暖房さらには除湿運転での性能を向上することができる。
【００７０】
また、上述した実施例では、冷房運転や暖房運転の時に使う絞り装置７としては電動膨張弁タイプのもので説明したが、これに限らず、絞り装置７としては、キャピラリーチューブあるいは通常の膨張弁と二方弁とを並列に設けた構成のものにしてもよく、二方弁の開閉により、上述した実施例と同様の作用を行うことができる。
【００７１】
さらに、上述した各実施例においては、室内ファン８の送風能力を変えることによりいろいろな使用状態に適した除湿運転を行うことができる。たとえば通常の除湿運転では人の好みに応じて室内風量を変え、洗濯物を乾燥するときには室内風量を増して運転し、寝るときには室内風量を落として運転するようにする。
【００７２】
また、上述した各実施例においては、使用冷媒としてＨＣＦＣ２２やＨＦＣ系やＨＣ系の単一冷媒及び混合冷媒等種々の冷媒に適用でき、上述した同様の効果を得ることができる。
【００７３】
【発明の効果】
本発明によれば、冷房サイクルによる除湿運転及び暖房サイクルによる除湿運転の温度範囲をさらに広くすることができると共にそれぞれの除湿運転に適正な冷媒量にすることができ、これにより快適で高性能な除湿運転を行なうことができる空気調和機を得ることができる。
【００７４】
また、本発明によれば、冷房サイクルによる除湿運転と暖房サイクルによる除湿運転のそれぞれに必要な冷媒量をより一層適量に調節することができ、これにより高性能な除湿運転ができる空気調和機を得ることができる。
【００７５】
また、本発明によれば、冷媒流が正逆両方向になっても開閉可能でかつ絞り作用を有する除湿絞り装置を備え、これにより簡単な構成で、快適かつ高性能な除湿運転ができる空気調和機を得ることができる。
【００７６】
また、本発明によれば、冷房サイクルによる除湿運転と暖房サイクルによる除湿運転において、さらに送風機や圧縮機の能力制御により広い外気温度範囲にわたって快適で高性能な除湿運転ができる空気調和機を得ることができる。
【図面の簡単な説明】
【図１】本発明の第１実施例の空気調和機の冷房サイクルによる除湿運転時の構成図である。
【図２】図１の暖房サイクルによる除湿運転時の構成図である。
【図３】本発明の第２実施例の室内機の構成図である。
【図４】本発明の第３実施例の室内機の構成図である。
【図５】本発明の第４実施例の室内熱交換器と室外熱交換器の配管径を比較して説明する図である。
【図６】本発明の第５実施例の空気調和機の構成図である。
【図７】図１の空気調和機の除湿絞り装置の一例の除湿運転時の断面図である。
【図８】図７の除湿絞り装置の冷暖房運転時の断面図である。
【図９】図１の空気調和機の除湿絞り装置の異なる例の構成図である。
【符号の説明】
１…室内機、２…室内熱交換器、３…第１室内熱交換器、４…第２室内熱交換器、５、６…露受皿、７…除湿絞り装置、８室内ファン、９…室内機ケーシング、１１、１２…吸込空気流、１３…吹出空気流、１４…圧縮機、１５…四方弁、１６…室外熱交換器、１８…室外ファン、３０、３２…放熱フィン、３３…伝熱管、３５…接続管、３６…バイパス管、３７…二方弁、３８…冷媒タンク、４０…弁本体３０、４１…弁座、４２…弁ポート、４３…弁体、６２…第１接続管、４５、６３…第２接続管、４６…密閉ケース、４７…ケース軸受、４８…ロータ、４９…永久磁石、５０…スリーブ、５１…中心軸、５２…弁連結部、５３…ブッシュ、５２ａ…雄ネジ部、５３ａ…雌ネジ部、５４…絞り隙間、６０…二方弁、６１…キャピラリーチューブ。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an air conditioner, and is particularly suitable for an air conditioner capable of performing a dehumidifying operation in which room air is heated by condensation heat of a refrigeration cycle.
[0002]
[Prior art]
As a conventional air conditioner, there is one disclosed in Japanese Patent Laid-Open No. 54-47353 (prior art 1).
[0003]
This prior art 1 has a refrigeration cycle in which a compressor, a four-way valve, an outdoor heat exchanger, a cooling throttle mechanism, a heating throttle mechanism, an indoor heat exchanger, a dehumidifying throttle mechanism, etc. are connected by piping. Is forming. The four-way valve includes a cooling cycle in which the refrigerant flow from the compressor flows from the outdoor heat exchanger to the indoor heat exchanger, and the refrigerant flow from the compressor flows from the indoor heat exchanger to the outdoor heat exchanger. It has a function of switching to a heating cycle that flows in order. The cooling throttle mechanism is connected between the outdoor heat exchanger and the indoor heat exchanger so as to perform a throttle action during cooling operation by being connected in parallel with the first solenoid valve, and the heating throttle mechanism is It is provided between the outdoor heat exchanger and the indoor heat exchanger so as to be connected to the check valve and perform a throttling action during heating operation. Furthermore, the indoor heat exchanger is divided into a first indoor heat exchanger and a second indoor heat exchanger. Further, the dehumidifying throttle mechanism is provided between the first indoor heat exchanger and the second indoor heat exchanger so as to be connected in parallel with the second electromagnetic valve so as to perform a throttling action during the dehumidifying operation.
[0004]
And the thing of this prior art 1 is the dehumidification operation of the cooling flavor which flows a refrigerant | coolant in order of the 2nd indoor side heat exchanger by a cooling cycle, the throttle mechanism for dehumidification, and the indoor side heat exchanger by switching of a four-way valve etc., It is possible to perform a heating-like dehumidifying operation in which the refrigerant flows in the order of the indoor heat exchanger, the dehumidifying throttle mechanism, and the second indoor heat exchanger in the heating cycle.
[0005]
Further, as a conventional air conditioner, there is one disclosed in JP-A-7-158888 (Prior Art 2).
[0006]
In the prior art 2, a refrigeration cycle is formed by connecting a compressor, a four-way valve, an outdoor heat exchanger, an air conditioning capillary tube, an indoor heat exchanger, a dehumidifying capillary tube, and the like with piping. The four-way valve allows the refrigerant flow from the compressor to flow from the outdoor heat exchanger to the indoor heat exchanger and the refrigerant flow from the compressor to flow from the indoor heat exchanger to the outdoor heat exchanger in this order. It has a function to switch to the heating cycle. The air conditioning capillary tube is provided between the outdoor heat exchanger and the indoor heat exchanger so as to perform a throttling operation during the air conditioning operation. Furthermore, the indoor heat exchanger is divided into an evaporator and a reheater. Further, the dehumidifying capillary tube is provided between the evaporator and the reheater so as to perform a throttling action during the dehumidifying operation.
[0007]
And this thing of this prior art 2 can perform the dehumidification operation | movement which flows a refrigerant | coolant in order of the reheater by a cooling cycle, the capillary tube for dehumidification, and an evaporator, and is the magnitude | size of an evaporator and a reheater. An example of changing is shown.
[0008]
[Problems to be solved by the invention]
However, although it has been shown that the prior art 1 can perform a dehumidifying operation with a cooling cycle by a cooling cycle and a dehumidifying operation with a heating cycle by a heating cycle, the indoor heat exchanger is installed in the first chamber. The size divided into the inner heat exchanger and the second indoor heat exchanger is not disclosed at all (however, the first indoor heat exchanger and the second indoor heat having the same size are simply not shown in the drawings). The exchanger is shown), further expanding the temperature range of the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle so that the dehumidifying operation can be performed at a sufficiently low blowing air temperature even in summer, and also in winter It is disclosed that the indoor heat exchanger is divided into a first indoor heat exchanger and a second indoor heat exchanger having different sizes so that a dehumidifying operation with a sufficiently high blowing temperature can be performed. It has not been.
[0009]
And the thing of the prior art 2 is not disclosed at all about the improvement of the performance fall by the amount of refrigerant | coolants required for the dehumidifying operation of the air_conditioning | cooling taste by the air_conditioning | cooling cycle and the dehumidifying operation of the air_feeling | heated taste by the heating cycle differing. Further, in an air conditioner that can perform a dehumidifying operation with a cooling cycle by a cooling cycle and a dehumidifying operation with a heating cycle by a heating cycle, it can be opened and closed even when the refrigerant flow of the dehumidifying throttle device is in both forward and reverse directions and has a throttling effect There is no disclosure of providing a dehumidifying squeezing device.
[0010]
Moreover, although the example of changing the magnitude | size of an evaporator and a reheater is shown, the thing of the prior art 2 is only shown about the case of the dehumidification operation by a cooling cycle, and is based on a cooling cycle. There is no disclosure of changing the size of the evaporator and reheater in connection with the dehumidifying operation and the dehumidifying operation by the heating cycle.
[0011]
The object of the present invention is to further widen the temperature range of the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle, and to make the amount of refrigerant appropriate for each dehumidifying operation, thereby making the comfortable and high performance. It is providing the air conditioner which can perform a dehumidification driving | operation.
[0012]
Another object of the present invention is to provide an air conditioner that can adjust the amount of refrigerant necessary for each of the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle to a more appropriate amount, thereby enabling high-performance dehumidifying operation. It is to provide.
[0013]
Another object of the present invention is to provide a dehumidifying squeezing device that can be opened and closed even when the refrigerant flow is in both forward and reverse directions and has a throttling action, thereby enabling air conditioning that can perform a comfortable and high-performance dehumidifying operation with a simple configuration. Is to provide a machine.
[0014]
Another object of the present invention is to provide an air conditioner that can perform a comfortable and high-performance dehumidifying operation over a wide outside air temperature range by controlling the performance of the blower and the compressor in the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle. There is.
[0015]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides a refrigeration cycle formed by connecting a compressor, an operation switching valve, an outdoor heat exchanger, an air conditioner / throttle device, an indoor heat exchanger, and a dehumidifying throttle device with piping, An outdoor fan that ventilates the outdoor heat exchanger; and an indoor fan that ventilates the indoor heat exchanger, and the operation switching valve causes the refrigerant flow from the compressor to flow from the outdoor heat exchanger to the indoor heat. A cooling cycle that flows through the exchanger and a heating cycle that flows the refrigerant flow from the compressor in order from the indoor heat exchanger to the outdoor heat exchanger, and the cooling and heating throttle device is in a cooling operation And the outdoor heat exchanger and the indoor heat exchanger so as to perform a throttling action during heating operation, the indoor heat exchanger being a first indoor heat exchanger and a second indoor heat exchanger. With a bowl The dehumidifying throttle device is provided between the first indoor heat exchanger and the second indoor heat exchanger so as to perform a throttling operation during the dehumidifying operation, and the outdoor heat generated by the cooling cycle is used as the dehumidifying operation. A dehumidifying operation in which refrigerant flows in the order of the exchanger, the second indoor heat exchanger, the dehumidifying throttle device, and the first indoor heat exchanger, the first indoor heat exchanger by the heating cycle, the dehumidifying throttle device, In the air conditioner having a dehumidifying operation in which the refrigerant flows in the order of the second indoor heat exchanger and the outdoor heat exchanger, It becomes a condenser during dehumidifying operation by the heating cycle The first indoor heat exchanger , Becomes an evaporator during dehumidifying operation by the heating cycle It is made larger than the second indoor heat exchanger.
In the present invention, more preferably ,in front The outdoor fan has a refrigerant amount suitable for each dehumidifying operation under different setting conditions during the dehumidifying operation by the cooling cycle and during the dehumidifying operation by the heating cycle. Rotational speed There is to control.
[0025]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings. In the second and subsequent embodiments, a part of the configuration common to the first embodiment is omitted, and a duplicate description is omitted. The same reference numerals in the drawings of the respective embodiments indicate the same or equivalent.
[0026]
First, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a configuration diagram during a dehumidifying operation by a cooling cycle of the air conditioner according to the first embodiment of the present invention, and FIG. 2 is a configuration diagram during a dehumidifying operation by a heating cycle of FIG.
[0027]
The refrigeration cycle is a variable-capacity compressor 14 by rotational speed control, etc., a four-way valve 15 that is an operation switching valve for switching between a cooling cycle and a heating cycle, an outdoor heat exchanger 16, a fully open state without a throttling action, and a throttle amount. An electric expansion valve type air-conditioning expansion / contraction expansion device 17 that can be continuously changed over a wide range by a motor, the multi-stage bending indoor heat exchanger 2 and the dehumidification expansion device 7 are configured to be connected annularly by a connection pipe.
[0028]
The cooling cycle is a cycle in which the refrigerant flow from the compressor 14 flows from the outdoor heat exchanger 16 to the indoor heat exchanger 2, and is applied in a cooling operation and a dehumidifying operation including a cooling taste. The heating cycle is a cycle in which the refrigerant flow from the compressor 14 flows from the indoor heat exchanger 2 to the outdoor heat exchanger 16, and is applied in a dehumidifying operation including a heating operation and a heating taste.
[0029]
The air-conditioning expansion / contraction device 17 is connected between the indoor heat exchanger 2 and the outdoor heat exchanger 16. Furthermore, an outdoor fan 18 that ventilates the outdoor heat exchanger 16 and an indoor fan 8 that ventilates the indoor heat exchanger 2 are provided. The outdoor fan 18 is composed of a propeller fan, and can control its rotational speed to make its ventilation capacity variable. Moreover, the indoor fan 8 is comprised by a cross-flow fan, and can control the rotation speed and make the ventilation capability variable.
[0030]
The indoor unit 1 includes an indoor heat exchanger 2, an indoor fan 8, and a cooling / heating throttle device 17. The indoor heat exchanger 2 has a structure bent in multiple stages (three stages), and includes a first indoor heat exchanger 3 bent in two stages and a second indoor heat exchanger 4 having a smaller heat transfer area. Yes. The first indoor heat exchanger 3 is disposed on the front side, and the second indoor heat exchanger 4 is disposed on the back side. The first indoor heat exchanger 3 and the second indoor heat exchanger 4 have a substantially mountain-shaped structure that is thermally separated, and are disposed in the indoor unit casing 9. The In addition, the 1st indoor heat exchanger 3 is comprised so that it may become 2 or more heat transfer areas than the 2nd indoor heat exchanger 4. FIG. Separate dew trays 5 and 6 are provided directly below the first indoor heat exchanger 3 and the second indoor heat exchanger 4, respectively. As a result, the dehumidified water generated in the first indoor heat exchanger 3 is received by the dew receiving tray 5 and guided to the outside, and the dehumidified water generated in the second indoor heat exchanger 4 is received by the dew receiving tray 6 to the outside. Led.
[0031]
Connected between the first indoor heat exchanger 3 and the second indoor heat exchanger 4 is a dehumidifying squeezing device 7 that is in a fully open state with very low flow resistance during cooling and heating operations and that performs a squeezing action during the dehumidifying operation. ing.
[0032]
The indoor fan 8 is located behind the first indoor heat exchanger 3 and below the second indoor heat exchanger 4 and is disposed in the casing 9 of the indoor unit 1, like the suction airflows 11 and 12 indicated by arrows. The indoor air is sucked through the first indoor heat exchanger 3 and the second indoor heat exchanger 4 and is blown into the room as a blown air flow 13 indicated by an arrow. The indoor air heat-exchanged by the first indoor heat exchanger 3 and the second indoor heat exchanger 4 is mixed by the indoor fan 8 and blown into the room.
[0033]
In the dehumidifying operation, the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle can be performed by the operations of the four-way valve 15, the dehumidifying throttle device 7 and the cooling / heating throttle device 17.
[0034]
First, the dehumidifying operation by the cooling cycle will be described with reference to FIG. In the dehumidifying operation by this cooling cycle, the four-way valve 15 is operated so as to constitute a cooling cycle, the air conditioning and expansion device 17 is fully opened, and the dehumidification and expansion device 7 is throttled, so that the refrigerant is indicated by a solid arrow. , Compressor 14, four-way valve 15, outdoor heat exchanger 16, electric expansion valve 17, second indoor heat exchanger 4, dehumidifying throttle device 7, first indoor heat exchanger 3, four-way valve 15, compressor 14 in this order. The outdoor heat exchanger 16 is operated as an upstream condenser, the second indoor heat exchanger 4 as a downstream condenser, and the first indoor heat exchanger 3 as an evaporator.
[0035]
Then, the indoor air is sucked in like the suction airflows 11 and 12 by the indoor fan 8 and passed through the indoor heat exchanger 2 and blown out like the blowing airflow 13 so that the indoor air acts as an evaporator. At the same time as being cooled and dehumidified by the indoor heat exchanger 3, it is heated by the indoor back surface heat exchange 4, which becomes a condenser or heater on the downstream side, and these are mixed and blown out into the room like a blown air flow 13. In this way, the room air is dehumidified. The dehumidified water generated in the first indoor heat exchanger 3 flows downward, collects in the dew tray 5 without being re-evaporated on the second indoor heat exchanger 4 serving as a condenser, and further drains to the outside. Is done.
[0036]
In the dehumidifying operation by this cooling cycle, when the air blowing amount of the outdoor fan 18 is increased, the heat radiation amount in the outdoor heat exchanger 16 is increased, the heat radiation amount from the second indoor heat exchanger 4 is decreased, and the temperature of the blown air flow 13 is increased. Go down. Further, when the capacity of the compressor 14 is increased or the amount of air blown from the outdoor fan 18 is increased, the evaporation temperature is lowered, the dehumidifying capacity in the first indoor heat exchanger 3 is increased, and the humidity of the blown air flow 13 is lowered. it can. Furthermore, the temperature and humidity of the blown air flow 13 also change by changing the amount of air blown by the indoor fan 8, but basically, the control of the outdoor fan 18 and the compressor 14 makes the blown air flow 13 Temperature and humidity can be finely controlled. In this case, in the indoor heat exchanger 2, the heat transfer area of the first indoor heat exchanger 3 serving as an evaporator is larger than that of the second indoor heat exchanger 4 serving as a condenser. The cooling capacity in the exchanger 3 can be made sufficiently larger than the heating capacity of the second indoor heat exchanger 4. In addition, since the heat transfer area of the first indoor heat exchanger 3 is configured to be larger than twice the heat transfer area of the second indoor heat exchanger 4, the cooling capacity in the first indoor heat exchanger 3 is increased. Can be made significantly larger than the heating capacity of the second indoor heat exchanger 4.
[0037]
In this way, the dehumidifying operation by the cooling cycle is the heating dehumidifying operation in which the temperature of the blown air flow is higher than room temperature in the early spring and late autumn chills, and the temperature of the blown air flow is relatively comfortable in the spring and autumn outside temperatures. In addition to being able to perform isothermal dehumidification operation equivalent to room temperature, not only from the rainy season to early summer, but also in summer, perform comfortable dehumidification operation by lowering the blown air temperature when air cooling capacity is required Can do. In particular, since the heat transfer area of the first indoor heat exchanger 3 is larger than the heat transfer area of the second indoor heat exchanger 4, the range of lowering the blown air temperature in the dehumidifying operation is widened, and the humidity is greatly reduced to be comfortable. A cool dehumidifying operation can be used as an alternative to the cooling operation.
[0038]
During the cooling operation, the four-way valve 15 is operated so as to constitute a cooling cycle, the dehumidifying throttle device 7 is fully opened and the cooling / heating throttle device 17 is adjusted to an appropriate throttle amount, whereby the refrigerant flow is changed to the compressor. 14, the four-way valve 15, the outdoor heat exchanger 16, the cooling / heating throttle device 17, the second indoor heat exchanger 4, the dehumidifying throttle device 7, the first indoor heat exchanger 3, the four-way valve 15 and the compressor 14 are circulated in this order. The outdoor heat exchanger 16 acts as a condenser to dissipate heat to the outdoor air, the second indoor heat exchanger 4 and the first indoor heat exchanger 3 act as an evaporator to cool the indoor air, and a predetermined cooling is performed. Do.
[0039]
Next, the dehumidifying operation by the heating cycle will be described with reference to FIG. In this dehumidifying operation by the heating cycle, the four-way valve 15 is operated so as to constitute a heating cycle, and the cooling / heating throttle device 17 is appropriately opened and the dehumidifying throttle device 7 is throttled, so that the refrigerant is indicated by the broken-line arrows. , Compressor 14, four-way valve 15, first indoor heat exchanger 3, dehumidifying throttle device 7, second indoor heat exchanger 4, electric expansion valve 17, outdoor heat exchanger 16, four-way valve 15, and compressor 14 in this order. The first indoor heat exchanger 3 is a condenser, the second indoor heat exchanger 4 is an upstream evaporator, and the outdoor heat exchanger 16 is a downstream evaporator.
[0040]
Then, the indoor air is sucked like the suction airflows 11 and 12 by the indoor fan 8, passed through the indoor heat exchanger 2, and blown like the blown airflow 13, so that the room air has a larger dimension to become a condenser. The first indoor heat exchanger 3 is heated and at the same time, the second indoor heat exchanger 4 having a smaller dimension serving as an evaporator is cooled and dehumidified, and these are mixed and blown into the room. In this way, the room air is dehumidified. The dehumidified water generated in the second indoor heat exchanger 4 flows downward, is collected in the dew tray 6 without being re-evaporated on the first indoor heat exchanger 3 serving as a condenser, and further drained to the outside. Is done.
[0041]
In the dehumidifying operation by the heating cycle, the first indoor heat exchanger 3 that is a condenser not only absorbs heat in the second indoor heat exchanger 4 that is an upstream evaporator, but also has a much larger downstream evaporation. Since the amount of heat absorbed from the outside air in the outdoor heat exchanger 16 serving as a heat exchanger can be used for heat dissipation, the amount of heating of the indoor suction air can be much larger than the dehumidifying operation by the above-described cooling cycle, Since the size of the 1 indoor heat exchanger 3 is larger than that of the second indoor heat exchanger 4, the temperature of the blown air flow 13 can be sufficiently higher than room temperature without the condensation pressure becoming abnormally high. Since the heat transfer area of the first indoor heat exchanger 3 is larger than twice the heat transfer area of the second indoor heat exchanger 4, the heating capacity in the first indoor heat exchanger 3 is increased. Can be made significantly larger than the cooling capacity of the second indoor heat exchanger 4.
[0042]
In the dehumidifying operation by the heating cycle, if the air blowing amount of the outdoor fan 18 and the capacity of the compressor 14 are increased, the heat absorption amount in the outdoor heat exchanger 16 is increased and the heat radiation amount from the first indoor heat exchanger 3 is increased. The temperature of the blown air stream 13 can be further increased. When the capacity of the compressor 14 is increased, the evaporation temperature is lowered, the dehumidifying capacity in the second indoor heat exchanger 4 is increased, and the humidity of the blown air flow 13 can be greatly reduced. Further, the temperature and humidity of the blown air flow 13 change depending on the amount of air blown by the indoor fan 8, but basically the temperature and humidity of the blown air flow 13 are finely controlled based on the control of the outdoor fan and the compressor. can do.
[0043]
In this way, the dehumidifying operation by the heating cycle can make the temperature of the blown airflow 13 sufficiently higher than the room temperature, and can perform the dehumidifying operation with a heating effect when it is chilly in early spring or late autumn. It is possible to perform a dehumidifying operation with the air temperature sufficiently high, so that the temperature is not so low, but it is used for heating and dehumidification when the humidity is high, or when the temperature is low and the humidity is high It can be used for dehumidification to prevent condensation (this is especially effective in areas with high winter humidity such as back Japan).
[0044]
During heating operation, the four-way valve 15 is operated to form a heating cycle, the dehumidifying throttle device 7 is fully opened, and the cooling / heating throttle device 17 is adjusted to an appropriate throttle amount to compress the refrigerant flow. Machine 14, four-way valve 15, first indoor heat exchanger 3, dehumidifying throttle device 7, second indoor heat exchanger 4, cooling / heating throttle device 17, outdoor heat exchanger 16, four-way valve 15 and compressor 14 are circulated in this order. The first indoor heat exchanger 3 and the second indoor heat exchanger 4 act as condensers to heat the indoor air, and the outdoor heat exchanger 16 acts as an evaporator to absorb heat from the outdoor air and perform predetermined heating. I do.
[0045]
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 3 is a block diagram of the indoor unit of the second embodiment of the present invention.
[0046]
In the second embodiment, the first indoor heat exchanger 3 bent in two stages in the first embodiment is changed to a linear first stage first indoor heat exchanger. As a result, the same operation, function, and effect as in the first embodiment can be obtained, and the structure of the first indoor heat exchanger 3 can be simplified, leading to cost reduction.
[0047]
Next, a third embodiment of the present invention will be described with reference to FIG. FIG. 4 is a block diagram of an indoor unit according to the third embodiment of the present invention.
[0048]
In this third embodiment, the indoor heat exchanger 2 is thermally separated into a second indoor heat exchanger 4 having a small size and a first indoor heat exchanger 3 having a large size and arranged in the vertical direction, and the dew tray is further provided. 6 is provided independently at the lower end of the second indoor heat exchanger 4, and the indoor heat exchanger 2 provided from the front side to the back side of the indoor unit in the first and second embodiments is vertically extended and provided. It is a thing. Therefore, the third embodiment can obtain the same operation, function and effect as those of the first and second embodiments, and occurs in the second indoor heat exchanger 4 serving as an evaporator even in the dehumidifying operation by the heating cycle. Since the dehumidified water is collected in the dew tray 6 and drained to the outside, it does not re-evaporate on the first indoor heat exchanger 3 serving as a condenser. In this 3rd Example, since the dimension of the front-back direction of the indoor heat exchanger 2 can be made small, an indoor unit can be made thin.
[0049]
Next, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 5 is a diagram illustrating the comparison of the pipe diameters of the indoor heat exchanger and the outdoor heat exchanger according to the fourth embodiment of the present invention. FIG. 5A is a diagram showing a part of the cross fin type indoor heat exchanger 2, and FIG. 5B is a diagram showing a part of the cross fin type outdoor heat exchanger 16.
[0050]
In the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle described above, the optimum refrigerant filling amount is different. In general, a large amount of refrigerant exists in a condenser having a subcool region that is a liquid refrigerant at high pressure. Therefore, in the dehumidifying operation by the cooling cycle, the outdoor heat exchanger 16 and the second indoor heat exchanger 4 serve as a condenser, and the outdoor heat exchanger 16 is larger in size than the indoor heat exchanger 2, so that the necessary refrigerant The amount increases. On the other hand, in the dehumidifying operation by the heating cycle, since only the first indoor heat exchanger 3 is small as a condenser, the amount of necessary refrigerant is reduced. In the above-described embodiment, the first indoor heat exchanger 3 serving as a condenser is made larger than the second indoor heat exchanger 4 serving as an evaporator, so that the refrigerant necessary for the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle is used. Although the difference in the amount can be adjusted and a high-performance dehumidifying operation can be performed, in some cases, it is assumed that the amount of refrigerant is excessive in the dehumidifying operation by the heating cycle.
[0051]
Therefore, in the fourth embodiment, in order to adjust the imbalance of the necessary refrigerant amount, the inner diameter d of the heat transfer tube 33 of the outdoor heat exchanger 16 is adjusted. ₂ The inner diameter d of the heat transfer tube 31 of the indoor heat exchanger 2 ₁ Smaller (d ₂ <D ₁ ). As a result, during the dehumidifying operation by the cooling cycle, the outdoor heat exchanger 16 becomes a condenser, but the inner diameter d of the heat transfer tube 33 is reduced. ₂ Therefore, the amount of refrigerant existing in the outdoor heat exchanger 16 is reduced, and the necessary refrigerant amount can be made closer to the necessary refrigerant amount for the dehumidifying operation by the heating cycle, and the state of the more appropriate refrigerant amount in both dehumidifying operations. You can drive in. Note that the fourth embodiment for adjusting the refrigerant amount can be applied to the first to third embodiments.
[0052]
Next, a fifth embodiment of the present invention will be described with reference to FIG. FIG. 6 is a block diagram of an air conditioner according to a fifth embodiment of the present invention.
[0053]
The fifth embodiment shows another embodiment for adjusting the necessary refrigerant amount. In the fifth embodiment, in the first embodiment, a bypass pipe 36 is provided in the connection pipe 35 between the first indoor heat exchanger 3 and the four-way valve 15, and the bypass pipe 36 is provided on the bypass pipe 36. A two-way valve 37 and a refrigerant tank 38 are connected in series from a connection point A on the one-room heat exchanger 3 side to a connection point B on the four-way valve side.
[0054]
In this configuration, in the dehumidifying operation by the cooling cycle, by opening the two-way valve 37, the low-temperature / low-pressure gas refrigerant flow exiting the first indoor heat exchanger 3 serving as an evaporator causes the connecting pipe 35 to be connected from the point A. At the same time as flowing to the point B, the bypass pipe 36 flows from the point A through the two-way valve 37 and the refrigerant tank 38 to the point B. In this case, since the gas refrigerant flow always flows in the refrigerant tank 38 and the ambient temperature is higher than the saturation temperature, liquid refrigerant does not accumulate inside. Further, in the dehumidifying operation by the heating cycle, by closing the two-way valve 37, the high-temperature and high-pressure gas refrigerant that has exited the four-way valve 15 flows from the point B to the point A through the connecting pipe 35, but passes through the bypass pipe 36. The flow is stopped by a two-way valve 37. As a result, the refrigerant in the refrigerant tank 38 has a lower ambient temperature than the saturation temperature, and therefore condenses and accumulates as a liquid refrigerant. Therefore, in the fifth embodiment, liquid refrigerant accumulates in the refrigerant tank only during the dehumidifying operation by the heating cycle in which the refrigerant amount is excessive, and is more appropriate in both the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle. It is possible to operate in a state of a small amount of refrigerant.
[0055]
In the fifth embodiment, when the two-way valve 37 is opened during the cooling operation and the heating operation, the gas refrigerant flows in the refrigerant tank 38 and the liquid refrigerant does not accumulate. It can be operated with the refrigerant amount.
[0056]
Further, the fifth embodiment can be applied to the first and second embodiments and can obtain the same effect, but the size of the indoor heat exchanger cannot be increased so much that the first indoor heat exchanger is sufficient. This is particularly effective when applied to the third embodiment which cannot be increased.
[0057]
Next, a sixth embodiment of the present invention will be described. In the sixth embodiment, in the configuration of the air conditioner of the first to fifth embodiments described above, the outdoor fan 18 is controlled in rotation speed under different setting conditions during the dehumidifying operation by the cooling cycle and during the dehumidifying operation by the heating cycle. Thus, the operation can be performed with the refrigerant amount more suitable for each dehumidifying operation, and the comfort can be improved. Further, the compressor 14 is configured to control the operation capacity under different setting conditions during the dehumidifying operation by the cooling cycle and during the dehumidifying operation by the heating cycle, and thus, the compressor 14 is operated with a refrigerant amount suitable for each dehumidifying operation. It is possible to improve the comfort. Further, the capacity of the compressor 14, the outdoor fan 18, and the indoor fan 8 is controlled by a plurality of combinations different in the dehumidifying operation by the cooling cycle and in the dehumidifying operation by the heating cycle. The operation can be performed with the refrigerant amount more suitable for the operation, and the comfort can be improved.
[0058]
The case where the outdoor fan 18 and the compressor 14 are controlled will be specifically described. In the dehumidifying operation by the heating cycle, when the outdoor fan 18 is rotated and blown, the liquid refrigerant in the liquid / gas two-phase refrigerant absorbs heat from the outside air in the heat transfer tube of the outdoor heat exchanger 16 serving as an evaporator. It evaporates and becomes a gas refrigerant. Since the volume of the gas is large, the heat transfer tube is almost occupied by the gas refrigerant, and the amount of refrigerant held in the heat transfer tube is reduced. Here, if the outdoor fan 18 is stopped or the amount of air blown is sufficiently small, the evaporation of the liquid refrigerant in the outdoor heat exchanger 16 becomes very small, and a relatively large amount of liquid refrigerant is stored in the outdoor heat exchanger 16. The outdoor heat exchanger 16 can be used as a liquid refrigerant reservoir. In this case, if the capacity of the compressor is not increased so much (by operating the compressor in a low capacity state during the dehumidifying operation by the heating cycle), the liquid refrigerant accumulated in the outdoor heat exchanger returns to the compressor 14. Return is almost insignificant. As described above, during the dehumidifying operation by the heating cycle, the outdoor fan 18 is not operated or the air flow rate is sufficiently reduced, and the capacity of the compressor 14 is lowered to adjust the unbalance of the necessary refrigerant amount with the dehumidifying operation by the cooling cycle. can do.
[0059]
In addition, as for the adjustment method of the amount of refrigerant refrigerant required for the dehumidification operation by the cooling cycle and the dehumidification operation by the heating cycle described above, each adjustment method may be used alone, or a plurality of methods may be combined as necessary. It can also be implemented.
[0060]
Next, an example of the dehumidifying throttle device in the first embodiment of the present invention will be described with reference to FIGS. FIG. 7 is a cross-sectional view of the example of the dehumidifying throttle device of the air conditioner of FIG. 1 during a dehumidifying operation, and FIG. 8 is a cross-sectional view of the dehumidifying throttle device of FIG.
[0061]
In the dehumidifying throttle device 7 of the first embodiment, the refrigerant flow flows from the outdoor heat exchanger 16 to the indoor heat exchanger 2 in the dehumidifying operation by the cooling cycle of FIG. 1, and indoors in the dehumidifying operation by the heating cycle of FIG. It flows in the direction from the heat exchanger 2 to the outdoor heat exchanger 16, and flows in the opposite directions. When using a two-way valve type that moves the valve body up and down with respect to the valve seat using an electromagnet and opens and closes the valve port in such a dehumidifying throttle device 7, during the dehumidifying operation by the heating cycle, The valve body is pushed up by the refrigerant flow, and the valve is opened and does not work as a throttle device.
[0062]
Therefore, the dehumidifying and throttling device 7 shown in FIGS. 7 and 8 is configured such that the opening / closing operation of the valve is performed by a stepping motor. The valve portion A includes a valve main body 40 in which a valve port 42 is formed by a valve seat 41, and a valve body 43 that can move in the valve port 42 in the vertical direction in the drawing. A first connecting pipe 44 and a second connecting pipe 45 are attached to the valve body 40. The stepping motor part B includes a sealed case 46 attached to the valve body 40, a stator coil 45 disposed outside the sealed case 46, a permanent magnet 49 provided inside the sealed case 46, a sleeve 50 and a case. The rotor 48 includes a central shaft 51 supported by a bearing 47. The permanent magnet 49 is rotated by the stator coil 45. The valve body 43 and the central shaft 51 are connected by a valve connecting portion 52 provided with a male screw portion 52a, and a bush 53 provided with a female screw portion 53a is fixed in the valve main body 40. The portion 53a and the male screw portion 52a are arranged so as to mesh with each other. When the rotor 48 is rotated by this meshing, the valve body 43 moves in the vertical direction in the figure, and the valve port 42 is opened and closed.
[0063]
With the above configuration, during the dehumidifying operation, as shown in FIG. 7, the rotor 48 is rotated, the valve body 43 is moved downward so that the valve port 42 is closed, and the refrigerant is interposed between the valve body 43 and the valve port 42. The squeezing action is performed by flowing through the squeezed gap 54 formed. Here, for example, when the refrigerant flows in the direction from the first connection pipe 44 to the second connection pipe 45 during the dehumidifying operation by the cooling cycle, the refrigerant flows from the second connection pipe 45 to the first connection pipe 44 in the dehumidifying operation by the heating cycle. The refrigerant flow that flows inward and enters from the second connecting pipe 45 acts to push up the valve body 43 and open the valve port 42. However, since the vertical movement of the valve body 43 is restricted by the engagement between the male threaded portion 52a of the valve connecting portion and the female threaded portion 53a of the bush, the valve body 43 can perform a throttling action without opening the valve. In some cases, the stepping motor can be restrained so that the rotor 48 does not rotate by energizing the stator coil 45, so that the valve body 43 can be more securely fixed so as not to move in the vertical direction.
[0064]
In the above description, the flow of the refrigerant is reversed between the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle, and the same applies even if the refrigerant flows from below the valve body 43 during the dehumidifying operation by the cooling cycle. Thus, the same function and effect can be obtained, and the squeezing action can be surely performed.
[0065]
In the case of cooling and heating operation, as shown in FIG. 8, the valve body 43 is moved upward by rotating the rotor 48 to open the valve port 42. As a result, the refrigerant flow flows through the valve portion A with almost no flow resistance, and the performance can be prevented from deteriorating.
[0066]
7 and 8, the stepping motor is used for the opening / closing operation of the valve. However, the present invention is not limited to this, and other types of motors can be used for the same operation and the same as long as the motor can control the rotational position. An effect can be obtained.
[0067]
Next, a different example of the dehumidifying throttle device in the first embodiment of the present invention will be described with reference to FIG. FIG. 9 is a configuration diagram of a different example of the dehumidifying throttle device of the air conditioner of FIG.
[0068]
This dehumidifying throttle device 7 has a configuration in which a two-way valve 60 and a capillary tube 61 that can open and close a flow path in the forward and reverse directions of the refrigerant flow are connected in parallel, and 62 is a first connecting pipe, 63 is a 2nd connection pipe. In this configuration, at the time of the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle, the two-way valve 60 is closed and the capillary tube 61 is used as a throttling device, so that the refrigerant flow trying to pass through the two-way valve 60 is blocked. In both dehumidifying operations, a stable squeezing action is performed by the capillary tube 61. In the case of cooling and heating operation, the two-way valve 60 is opened so that the refrigerant flow flows through the two-way valve 60 almost without resistance. As a result, the first connecting pipe 62 and the second connecting pipe 63 communicate with each other with almost no flow resistance, and cooling and heating operations can be performed with almost no loss due to the dehumidifying throttle device.
[0069]
This invention is not limited to each Example mentioned above, Each part of the indoor side heat exchanger 2 can also be bent in multiple steps, or can also be made into circular arc shape as needed. In particular, room air conditioners, which are small air conditioners, often do not have enough space to store indoor heat exchangers. In this case, the number of bending of the indoor heat exchanger is increased or curved. Thus, an indoor heat exchanger having a sufficient heat transfer area in a narrow space can be accommodated, and the performance in cooling, heating, and dehumidifying operation can be improved.
[0070]
In the above-described embodiments, the expansion device 7 used in the cooling operation or the heating operation has been described as an electric expansion valve type. However, the expansion device 7 is not limited thereto, and the expansion device 7 may be a capillary tube or a normal expansion valve. And a two-way valve may be provided in parallel. By opening and closing the two-way valve, the same operation as in the above-described embodiment can be performed.
[0071]
Furthermore, in each Example mentioned above, the dehumidification operation suitable for various use conditions can be performed by changing the ventilation capability of the indoor fan 8. FIG. For example, in a normal dehumidifying operation, the indoor air volume is changed according to the preference of the person, the indoor air volume is increased when the laundry is dried, and the indoor air volume is decreased when sleeping.
[0072]
Moreover, in each Example mentioned above, it can apply to various refrigerant | coolants, such as HCFC22, a HFC type | system | group, a single refrigerant | coolant of HC type | system | group, and a mixed refrigerant | coolant as a use refrigerant | coolant, and the same effect mentioned above can be acquired.
[0073]
【The invention's effect】
According to the present invention, the temperature range of the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle can be further widened, and the amount of refrigerant can be set to an appropriate amount for each dehumidifying operation. An air conditioner capable of performing a dehumidifying operation can be obtained.
[0074]
In addition, according to the present invention, an air conditioner that can adjust the amount of refrigerant necessary for each of the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle to a more appropriate amount, thereby performing a high-performance dehumidifying operation. Obtainable.
[0075]
In addition, according to the present invention, the dehumidifying and throttling device that can be opened and closed even when the refrigerant flow is in both forward and reverse directions and has a throttling action is provided, and thereby air conditioning that allows a comfortable and high-performance dehumidifying operation with a simple configuration. You can get a chance.
[0076]
In addition, according to the present invention, in the dehumidifying operation by the cooling cycle and the dehumidifying operation by the heating cycle, an air conditioner capable of performing a comfortable and high-performance dehumidifying operation over a wide outside air temperature range by further controlling the performance of the blower and the compressor is obtained. Can do.
[Brief description of the drawings]
FIG. 1 is a configuration diagram during a dehumidifying operation by a cooling cycle of an air conditioner according to a first embodiment of the present invention.
FIG. 2 is a configuration diagram at the time of dehumidifying operation by the heating cycle of FIG. 1;
FIG. 3 is a configuration diagram of an indoor unit according to a second embodiment of the present invention.
FIG. 4 is a configuration diagram of an indoor unit according to a third embodiment of the present invention.
FIG. 5 is a diagram illustrating a comparison of pipe diameters of an indoor heat exchanger and an outdoor heat exchanger according to a fourth embodiment of the present invention.
FIG. 6 is a configuration diagram of an air conditioner according to a fifth embodiment of the present invention.
7 is a cross-sectional view of the example of the dehumidifying throttle device of the air conditioner of FIG. 1 during a dehumidifying operation.
8 is a cross-sectional view of the dehumidifying throttle device of FIG. 7 during air conditioning operation.
9 is a configuration diagram of a different example of the dehumidifying throttle device of the air conditioner of FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Indoor unit, 2 ... Indoor heat exchanger, 3 ... 1st indoor heat exchanger, 4 ... 2nd indoor heat exchanger, 5, 6 ... Dew tray, 7 ... Dehumidification throttle apparatus, 8 indoor fan, 9 ... Indoor Machine casing, 11, 12 ... Suction air flow, 13 ... Blowing air flow, 14 ... Compressor, 15 ... Four-way valve, 16 ... Outdoor heat exchanger, 18 ... Outdoor fan, 30, 32 ... Radiation fin, 33 ... Heat transfer tube 35 ... connecting pipe, 36 ... bypass pipe, 37 ... two-way valve, 38 ... refrigerant tank, 40 ... valve body 30, 41 ... valve seat, 42 ... valve port, 43 ... valve body, 62 ... first connecting pipe, 45, 63 ... second connection pipe, 46 ... sealed case, 47 ... case bearing, 48 ... rotor, 49 ... permanent magnet, 50 ... sleeve, 51 ... central shaft, 52 ... valve coupling part, 53 ... bush, 52a ... male Screw part, 53a ... Female thread part, 54 ... Restriction gap, 60 ... Two-way valve, 61 ... Capillary Cube.

Claims

A refrigeration cycle formed by connecting a compressor, an operation switching valve, an outdoor heat exchanger, a cooling / heating throttle device, an indoor heat exchanger, and a dehumidifying throttle device with piping;
An outdoor fan that ventilates the outdoor heat exchanger;
An indoor fan that ventilates the indoor heat exchanger;
The operation switching valve includes a cooling cycle for flowing a refrigerant flow from the compressor from the outdoor heat exchanger to the indoor heat exchanger, and an outdoor heat exchange for the refrigerant flow from the compressor from the indoor heat exchanger. It has the function to switch to the heating cycle that flows in the order of the vessel,
The air-conditioning expansion / contraction device is provided between the outdoor heat exchanger and the indoor heat exchanger so as to perform an expansion operation during cooling operation and heating operation,
The indoor heat exchanger has a first indoor heat exchanger and a second indoor heat exchanger,
The dehumidifying throttle device is provided between the first indoor heat exchanger and the second indoor heat exchanger so as to perform a throttling action during a dehumidifying operation,
As the dehumidifying operation, the dehumidifying operation in which the refrigerant flows in the order of the outdoor heat exchanger, the second indoor heat exchanger, the dehumidifying throttle device, and the first indoor heat exchanger in the cooling cycle, and the first in the heating cycle. In an air conditioner having an indoor heat exchanger, the dehumidifying throttle device, the second indoor heat exchanger, and a dehumidifying operation for flowing refrigerant in the order of the outdoor heat exchanger,
An air conditioner in which the first indoor heat exchanger serving as a condenser during the dehumidifying operation by the heating cycle is larger than the second indoor heat exchanger serving as an evaporator during the dehumidifying operation by the heating cycle .

The air conditioner according to claim 1, the pre-Symbol outdoor fan, the different setting conditions in the dehumidification operation according to the heating cycle and during dehumidifying operation by the cooling cycle, the refrigerant quantity suitable for each dehumidifying operation The air conditioner is characterized in that the rotational speed is controlled as described above.