JP4341093B2

JP4341093B2 - Air conditioner

Info

Publication number: JP4341093B2
Application number: JP00660399A
Authority: JP
Inventors: 恒家田
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 1999-01-13
Filing date: 1999-01-13
Publication date: 2009-10-07
Anticipated expiration: 2019-01-13
Also published as: JP2000203249A

Description

【０００１】
【発明の属する技術分野】
本発明は、空調装置に係り、例えば、電気自動車に採用するのに適したヒートポンプ式冷凍サイクル装置を備えた空調装置に関するものである。
【０００２】
【従来の技術】
従来、電気自動車用空調装置としては、除霜及び冷暖房可能なヒートポンプ式冷凍サイクル装置を備えたものがある。
そして、この空調装置の除霜方式では、冷凍サイクル装置の暖房運転時における冷媒の流れを冷房運転時の流れに変更した上で冷凍サイクル装置の室外熱交換器の除霜を行う。
【０００３】
【発明が解決しようとする課題】
しかし、上記空調装置においては、上述のような除霜方式が当該電気自動車の暖房走行中に実行されても、冷凍サイクル装置が暖房運転状態から冷房運転状態に変わるため、車室内に冷風が吹き出して、車室内の温度が低下してしまう。従って、除霜が可能であっても、当該電気自動車の乗員に対し良好な暖房感覚を与えることができないという不具合が生ずる。
【０００４】
そこで、本発明は、以上のようなことに対処すべく、ヒートポンプ式冷凍サイクル装置を備えた空調装置において、当該冷凍サイクル装置を暖房運転状態に維持したまま、適正な暖房感覚を損なうことなく、室外熱交換器の除霜を行うことを目的とする。
【０００５】
【課題を解決するための手段】
上記課題の達成にあたり、請求項１、２に記載の発明に係る空調装置は、空調ユニット（Ｕ）と、ヒートポンプ式冷凍サイクル装置（Ｒ）とを備える。
空調ユニットは、
空調ダクト（１０）と、
この空調ダクト内に設けられて当該空調ダクトの吸込口（１１、１２）から空気を吸込み空気流として空調ダクトの吹出口から吹き出す送風機（２０）と、
送風機の下流側にて空調ダクト内に設けられて空気流を流入冷媒に応じて冷却する室内側蒸発器（３０）と、
室内側蒸発器の下流側にて空調ダクト内に設けられて空気流を流入冷媒に応じて加熱する室内側凝縮器（５０）と、
室内側蒸発器の下流側にて空調ダクト内における室内側凝縮器の側方に形成される凝縮器バイパス路（１３）及び室内側凝縮器の一方を開き他方を閉じるように作動するエアミックスドア（４０）とを備える。
【０００６】
冷凍サイクル装置は、室内側凝縮器及び室内側蒸発器に加え、
吸入冷媒を駆動に応じて圧縮する圧縮機（６０）と、
室外側に設けられて外気と流入冷媒に応じて熱交換を行う室外側熱交換器（１１０）とを備えて、
暖房運転時には、圧縮機の圧縮冷媒を室内側凝縮器及び室外側熱交換器に各流入冷媒として順次循環させる暖房冷媒回路（Ｈ）を構成し、冷房運転時には、圧縮機の圧縮冷媒を室内側凝縮器、室外側熱交換器及び室内側蒸発器に各流入冷媒として順次循環させる冷房冷媒回路（Ｃ）を構成する。
【０００７】
また、空調装置は、
圧縮機を駆動するように制御する圧縮機制御手段（６０ａ、２２２、２３１、２３２、２３３）と、
エアミックスドアの開度が、暖房運転時には室内側凝縮器を全開にするとともに凝縮器バイパス路を全閉にする最大開度となり、冷房運転時には室内側凝縮器を全閉にするとともに凝縮器バイパス路を全開にする最小開度となるように、エアミックスドアを制御するエアミックスドア制御手段（１８０、２０８、２３３、２４１）と、
暖房運転時において室外側熱交換器の着霜の有無を判定する着霜判定手段（２３０）とを備える。
【０００８】
そして、圧縮機制御手段は、着霜判定手段による着霜ありとの判定時に圧縮機をその回転数を上昇させるように制御し、
エアミックスドア制御手段は、着霜判定手段の着霜ありとの判定時にエアミックスドアをその全開から閉じる方向に制御し、
冷凍サイクル装置は、着霜判定手段による着霜ありとの判定に伴い圧縮機によりその回転数の上昇に応じて圧縮される冷媒を室外側熱交換器に供給するホットガスバイパス手段（Ｇ、２４１）を有する。
【０００９】
上述のように、暖房運転時において着霜判定手段が室外側熱交換器の着霜有りと判定すると、圧縮機制御手段が圧縮機をその回転数を上昇させるように制御し、ホットガスバイパス手段が圧縮機によりその回転数の上昇に応じて圧縮される冷媒を室外側熱交換器に供給する。
これにより、室外側熱交換器の着霜がホットガスバイパス手段からの圧縮冷媒により融解される。その結果、暖房運転状態のままにて室外側熱交換器の除霜が良好になされる。
【００１０】
また、上述のように、着霜判定手段による着霜ありとの判定に伴いエアミックスドア制御手段はエアミックスドアをその全開から閉じる方向に制御するから、空気流のうち凝縮器バイパス路への流入分が増大して室内側凝縮器により加熱される分が減少する。その結果、圧縮機によりその回転数の上昇に応じて圧縮される冷媒により室内側凝縮器の加熱エネルギーが増大しても、適正な暖房感を維持しつつ上記除霜の効果を確保できる。
【００１１】
また、請求項１に記載の発明では、車室内への空気流の目標吹出温度（ＴＡＯ）を算出する手段（２０３）と、室内側蒸発器の空気流流出側温度（ＴＥ）を検出する温度センサ（１４０ｃ）と、圧縮機の吐出圧（ＳＰ）を検出する圧力センサ（１４０）とを備え、エアミックスドア制御手段は、着霜判定手段の着霜ありとの判定時にエアミックスドアの開度を、算出された車室内への空気流の目標吹出温度、検出された室内側蒸発器の空気流流出側温度および検出された圧縮機の吐出圧に基づいて決定し、エアミックスドア制御手段は、エアミックスドアの開度を圧縮機の回転数の上昇分だけ減少させるように補正する補正手段（２３３）を備えて、この補正手段による補正開度になるようエアミックスドアを制御する。また、請求項２に記載の発明では、車室内への空気流の目標吹出温度（ＴＡＯ）を算出する手段（２０３）と、室内側蒸発器の空気流流出側温度（ＴＥ）を検出する温度センサ（１４０ｃ）と、圧縮機の吐出圧（ＳＰ）を検出する圧力センサ（１４０）とを備え、エアミックスドア制御手段は、着霜判定手段の着霜ありとの判定時にエアミックスドアの開度を、算出された車室内への空気流の目標吹出温度、検出された室内側蒸発器の空気流流出側温度および検出された圧縮機の吐出圧に基づいて決定される冷媒の飽和温度（ＴＣ）に基づいて決定し、エアミックスドア制御手段は、エアミックスドアの開度を圧縮機の回転数の上昇分だけ減少させるように補正する補正手段（２３３）を備えて、この補正手段による補正開度になるようエアミックスドアを制御する。
【００１２】
これにより、適正な暖房感を維持しつつ除霜を行うという効果がより一層的確になされ得る。なお、上記各手段の括弧内の符号は、後述する実施形態記載の具体的手段との対応関係を示すものである。
【００１３】
【発明の実施の形態】
以下、本発明の一実施形態を図面に基づいて説明する。
図１及び図２は、それぞれ、本発明に係る電気自動車用空調装置の一実施形態の全体構成を示しており、この空調装置は、室内側空調ユニットＵと、冷凍サイクル装置Ｒとにより構成されている。なお、図１にて図示太線により示す冷媒回路（以下、暖房冷媒回路Ｈという）は、空調装置の暖房運転状態に対応し、図２にて図示太線により示す冷媒回路（以下、冷房冷媒回路Ｃという）は、空調装置の冷房運転状態に対応する。
【００１４】
空調ユニットＵは、当該電気自動車の車室内に設けられているもので、この空調ユニットＵは、図１にて示すごとく、空調ダクト１０内に送風機２０、室内側熱交換器である冷房用蒸発器３０、エアミックスドア４０、室内側熱交換器としての暖房用凝縮器５０を順次配置して構成されている。
送風機２０は、空調ダクト１０内にその外気吸込口１１或いは内気吸込口１２から外気或いは内気を空気流として吸込み冷房用蒸発器３０に向けて送風する。ここで、外気吸込口１１及び内気吸込口１２は、空調ダクト１０の内外気切替えドア（図示しない）により選択的に切替え開閉される。
【００１５】
蒸発器３０は、冷房運転時に、送風機２０からの空気流を冷却してエアミックスドア４０側に向けて流動させる。エアミックスドア４０は、図１にて図示位置にて、凝縮器５０を全開にするとともに空調ダクト１０内にて凝縮器５０の側方に形成される凝縮器バイパス路１３を全閉にする。このときのエアミックスドア４０の開度を最大開度とする。一方、エアミックスドア４０は、図２にて図示位置にて、凝縮器５０を全閉にするとともに凝縮器バイパス路１３を全開にする。このときのエアミックスドア４０の開度を最小開度とする。
【００１６】
凝縮器５０は、暖房運転時に、蒸発器３０を通して送風機２０から送風される空気流を加熱する。
このように加熱した空気流或いは凝縮器バイパス路１３を通る冷却空気流は、吹出空気流として空調ダクト１０の各吹出口のいずれかから吹き出す。
冷凍サイクル装置Ｒは、その構成素子として、上記室内側蒸発器３０及び室内側凝縮器５０を備えている。室内側蒸発器３０は、その内部を流れる冷媒の吸熱作用によって、送風機２０からの空気流を冷却する室内側熱交換器たる冷却器として機能する。また、室内側凝縮器５０は、その内部を流れる冷媒の放熱作用によって、流入空気流を加熱する室内側熱交換器たる加熱器として機能する。
【００１７】
ところで、冷凍サイクル装置Ｒは、蒸発器３０及び凝縮器５０とにより車室内の冷暖房を行うヒートポンプ式冷凍サイクル装置として構成されており、この冷凍サイクル装置Ｒは、暖房冷媒回路Ｈ（図１参照）或いは冷房冷媒回路Ｃ（図２参照）を構成すべく、上記蒸発器３０、凝縮器５０に加え、以下の各構成素子を備えている。
【００１８】
即ち、電動圧縮機６０は、アキュムレータ７０からの気相冷媒を配管Ｐ１から吸入して高温高圧冷媒として両配管Ｐ２、Ｐ３を通して流量調整弁８０に供給するとともに両配管Ｐ２、Ｐ４を通して凝縮器５０に供給する。
流量調整弁８０は、冷凍サイクル装置Ｒが暖房運転状態のとき全閉となり冷房運転状態のとき全開になるように制御される。このため、流量調整弁８０は、その全開により、配管Ｐ３内の高温高圧冷媒を配管Ｐ５内に供給し、この供給を、全閉により遮断する。なお、流量調整弁８０は、両配管Ｐ３、Ｐ５と共にホットガスバイパス回路Ｇを構成する。
【００１９】
また、上述した凝縮器５０は、配管Ｐ４からの高温高圧冷媒の放熱作用に基づき上述のごとく蒸発器３０からの冷却空気流を加熱した後、蒸発冷媒を配管Ｐ６を通して暖房側電気式膨張弁９０に供給するとともに、当該蒸発冷媒を両配管Ｐ６、Ｐ７を通してＶＣ電磁弁１００に供給する。
ここで、暖房側電気式膨張弁９０は、冷凍サイクル装置Ｒの冷房運転時に閉じ暖房運転時に開くように制御される。また、ＶＣ電磁弁１００は、冷凍サイクル装置Ｒの冷房運転時に開き暖房運転時に閉じるように制御される。
【００２０】
このため、暖房側電気式膨張弁９０は、その開時に、配管Ｐ６からの蒸発冷媒を配管Ｐ９及び配管Ｐ５の下流部を通して室外側熱交換器１１０に供給し、この供給を、閉時に遮断する。ＶＣ電磁弁１００は、その開時に、両配管Ｐ６、Ｐ７からの蒸発冷媒を両配管Ｐ８、Ｐ９及び配管Ｐ５の下流部を通して室外側熱交換器１１０に供給し、この供給を、閉時に遮断する。
【００２１】
室外側熱交換器１１０は、両電動ファン１１１による送風のもと、内部を通る冷媒を外気と熱交換させる。例えば、室外側熱交換器１１０は、冷房運転時には、凝縮器として機能し、流入冷媒を両電動ファン１１１の送風による外気でもって冷却し、また、暖房運転時には、蒸発器として機能し、流入冷媒を両電動ファン１１１の送風による外気でもって吸熱させて蒸発させる。そして、室外側熱交換器１１０は、配管Ｐ１０及び配管Ｐ１１を通してＥＶＣ冷房側電気式膨張弁１２０及びＶＨ電磁弁１３０に冷媒を供給する。
【００２２】
ここで、ＥＶＣ冷房側電磁弁１２０は、冷凍サイクル装置Ｒの冷房運転時に開き暖房運転時に閉じるように制御される。また、ＶＨ電磁弁１３０は、冷凍サイクル装置Ｒの冷房運転時に閉じ暖房運転時に開くように制御される。
このため、ＥＶＣ冷房側電磁弁１２０は、その開時に、配管Ｐ１０からの冷媒を配管Ｐ１２を通して蒸発器３０に供給し、この供給を、閉時に遮断する。ＶＨ電磁弁１３０は、その開時に、配管Ｐ１１からの冷媒を両配管Ｐ１３、Ｐ１５を通してアキュムレータ７０に供給し、この供給を、閉時に遮断する。
【００２３】
従って、蒸発器３０は、その流入冷媒を、ＶＨ電磁弁１３０の閉時に、両配管Ｐ１４、Ｐ１５を通してアキュムレータ７０に供給する。アキュムレータ７０は、配管Ｐ１５からの冷媒のうち液相冷媒を蓄積し、気相冷媒を配管Ｐ１を通して電動圧縮機６０に供給する。
なお、凝縮器１１０及び両電動ファン１１１は当該電気自動車の車室外に設置されている。
【００２４】
次に、空調装置の電気回路構成につき図３乃至図５を参照して説明する。
圧力センサ１４０は、図１にて示すごとく、配管Ｐ２の中間部位に設けられて、当該配管Ｐ２内の冷媒の圧力ＳＰを検出する。外気温センサ１４０ａは、当該電気自動車の車室外に設けられて、外気温ＴＡＭを検出する。内気温センサ１４０ｂは、当該電気自動車の車室内に設けられて、内気温ＴＲを検出する。
【００２５】
エバ後センサ１４０ｃは、蒸発器３０の冷却流流出側に設けられて、当該蒸発器３０の空気流流出側温度をエバ後温度ＴＥとして検出する。日射センサ１４０ｄは日射量ＴＳを検出する。温度センサ１４０ｅは、室外側熱交換器１１０の冷媒流出口に設けられて、配管Ｐ１０への流入冷媒の温度ＴＨＯを検出する。
操作パネル１５０は、当該電気自動車の車室内に設けられており、この操作パネル１５０は、その操作により、車室内の設定温度ＴＳＥＴ等を空調装置の制御に必要な信号として出力する。
【００２６】
マイクロコンピュータ１６０は、図４及び図５のフローチャートに従い、コンピュータプログラムを実行し、この実行中において、上述した複数のセンサ１４０乃至１４０ｅの各検出出力及び操作パネル１５０の出力信号に基づき、インバータ６０ａ、流量調整弁８０、ＥＶＨ膨張弁９０、ＶＣ電磁弁１００、ＥＶＣ膨張弁１２０、ＶＨ電磁弁１３０、送風機２０のモータ、両電動ファン１１１のモータ、内外気切替えサーボモータ１７０、エアミックスドアサーボモータ１８０及び吹出口切替えサーボモータ１９０を駆動制御する処理を行う。なお、上記コンピュータプログラムは、マイクロコンピュータ１６０のＲＯＭに予め記憶されている。
【００２７】
インバータ６０ａは、マイクロコンピュータ１６０による制御のもと、電動圧縮機６０の交流モータ６１を駆動制御する。
内外気切替えサーボモータ１７０は、マイクロコンピュータ１６０による制御のもと、上記内外気切替えドアを切替え制御する。エアミックスドアサーボモータ１８０は、マイクロコンピュータ１６０による制御のもと、エアミックスドア４０を開閉制御する。吹出口サーボモータ１９０は、マイクロコンピュータ１５０による制御のもと、上記各吹出口を切替え開閉する吹出口切替えドアを切替え制御する。
【００２８】
このように構成した本実施形態において、マイクロコンピュータ１６０が図４及び図５のフローチャートに従いコンピュータプログラムの実行を開始すると、ステップ２００において、マイクロコンピュータ１６０の内部が初期化される。ついで、操作パネル１５０から車室内の設定温度ＴＳＥＴがステップ２０１にて読み込まれる。その後、ステップ２０２において、各センサ１４０乃至１４０ｅからの出力が読み込まれる。
【００２９】
ついで、ステップ２０３において、車室内への空気流の目標吹出温度ＴＡＯが設定温度ＴＳＥＴ、内気温センサ１４０ｂからの内気温ＴＲ、外気温センサ１４０ａからの外気温ＴＡＭ及び日射センサ１４０ｄからの日射量ＴＳに応じて次の数１の式に基づき算出される。
【００３０】
【数１】
ＴＡＯ＝Ｋｓｅｔ・ＴＳＥＴ−Ｋｒ・ＴＲ−Ｋａｍ・ＴＡＭ−Ｋｓ・ＴＳ−Ｋ
ここで、本実施形態では、例えば、Ｋｓｅｔ＝５．８であり、Ｋｒ＝３．４であり、Ｋａｍ＝１．０であり、Ｋｓ＝１．０及びＫ＝１１である。この数１の式は、マイクロコンピュータ１６０のＲＯＭに予め記憶されている。
【００３１】
その後、ステップ２０４において、送風機２０のモータを駆動する電圧（いわゆるブロワ電圧）が決定され、ステップ２０５において、吹出口モードが決定され、かつ、ステップ２０６において、吸込口モードが決定される。
ついで、ステップ２０７において、吸込温度ＴＩＮが外気温ＴＡＭ及び内気温ＴＲに応じて次の数２の式に基づき算出される。
【００３２】
【数２】
ＴＩＮ＝α・ＴＡＭ＋（１−α）ＴＲ
ここで、αは０〜１の範囲にて内外気割合ＰＡＩに比例して変化する（図６参照）。
以上の処理がなされた後、ステップ２１０において、空調装置を冷房運転にするか否かが（ＴＡＯ−ＴＩＮ）≦３の成立の有無に基づきなされる。
【００３３】
（ＴＡＯ−ＴＩＮ）≦３が成立すれば、ステップ２１０における判定がＹＥＳとなり、ステップ２１１において、冷凍サイクル装置Ｒが空調ユニットＵとともに冷房運転運転におかれる（図２参照）。
即ち、空調ユニットＵにおいては、エアミックスドア４０の開度（以下、開度ＳＷという）が開度ＳＷ＝０と決定され、この開度ＳＷ＝０に基づきエアミックスドア４０はエアミックスドアサーボモータ１８０により駆動されて凝縮器５０を全閉にしバイパス路１３を全開にした状態となる。なお、開度ＳＷ＝０はエアミックスドア４０の最小開度に対応する最大冷房（ＭＡＸＣＯＯＬ）を表す。
【００３４】
このため、送風機２０がそのモータにて上記ブロワ電圧に基づき駆動されて、上記決定吸込口モードにより空調ダクト１０内に外気或いは内気を吸込み空気流として送風すると、この空気流は、蒸発器３０及びバイパス路１３を通して空調ダクト１０の吹出口側に向けて流動する。
このとき、当該空気流は蒸発器３０により冷却されて冷房用空気流（目標吹出温度ＴＡＯを有する）として、上記決定吹出口モードにて空調ダクト１０の吹出口から吹き出す。
【００３５】
また、冷凍サイクル装置Ｒでは、流量調整弁８０が全開状態となり、ＶＣ電磁弁１００及びＥＶＨ膨張弁１２０が開状態におかれ、一方、ＥＶＨ膨張弁９０及びＥＶＣ膨張弁１３０が閉状態におかれる。
このため、電動圧縮機６０がその交流モータ６１にてインバータ６０ａにより駆動されてアキュムレータ７０から配管Ｐ１を通して気相冷媒を吸引して圧縮し高温高圧冷媒として配管Ｐ２内に吐出すると、この吐出冷媒は、配管Ｐ４、凝縮器５０、両配管Ｐ６、Ｐ７、ＶＣ電磁弁１００及び両配管Ｐ８、Ｐ９を通して室外側熱交換器１１０に流入し、一方、配管Ｐ３、流量調整弁８０、配管Ｐ５及び配管Ｐ９の下流部を通して室外側熱交換器１１０に流入する。
【００３６】
従って、電動圧縮機６０からの高温高圧冷媒及び凝縮器５０からの冷媒が室外側熱交換器１１０により両電動ファン１１１による空冷作用のもとに空冷されて配管Ｐ１０を通りＥＶＨ膨張弁１２０から蒸発器３０に供給される。これにより、上述のような蒸発器３０による空気流の冷却がなされる。また、蒸発器３０の内部の冷媒は、両配管Ｐ１４、Ｐ１５、アキュムレータ７０及び配管Ｐ１を通り気相冷媒となって電動圧縮機６０に供給される。
【００３７】
これにより、車室内には冷風の吹き出し空気流が吹き出される。
また、ステップ２１０における判定がＮＯとなると、ステップ２２０において、空調装置を送風運転及び暖房運転運転のいずれにおくか否かが（ＴＡＯ−ＴＩＮ）＞３の成立の有無に基づき判定される。
ここで、（ＴＡＯ−ＴＩＮ）＞３が不成立ならば、ステップ２２０における判定がＮＯとなり、ステップ２２１において、空調ユニットＵの送風機２０による送風運転がなされる。
【００３８】
一方、ステップ２２０における判定がＹＥＳになると、ステップ２２２にて、冷凍サイクル装置Ｒが空調ユニットＵとともにが暖房運転運転におかれる。
即ち、空調ユニットＵにおいては、エアミックスドア４０の開度はＳＷ＝１００と決定され、この開度ＳＷ＝１００に基づきエアミックスドアサーボモータ１８０により駆動されて凝縮器５０を完全に開いた状態となる。なお、ＳＷ＝１００は、エアミックスドア４０の最大開度に対応する最大暖房（ＭＡＸＨＯＴ）を表す。
【００３９】
このため、送風機２０がそのモータにて上記ブロワ電圧に基づき駆動されて、上記決定吸込口モードにより空調ダクト１０内に外気或いは内気を吸込み空気流として送風すると、この空気流は、蒸発器３０及び凝縮器５０を通して空調ダクト１０の吹出口側に向けて流動する。このとき、当該空気流は蒸発器３０により冷却されることなく凝縮器５０により加熱されて暖房用空気流（目標吹出温度ＴＡＯを有する）として、上記決定吹出口モードにて空調ダクト１０の吹出口から吹き出す。
【００４０】
また、冷凍サイクル装置Ｒでは、流量調整弁８０、ＶＣ電磁弁１００及びＥＶＨ膨張弁１２０が閉状態におかれ、一方、ＥＶＨ膨張弁９０及びＥＶＣ膨張弁１３０が開状態におかれる。
このため、電動圧縮機６０がその交流モータ６１にてインバータ６０ａにより駆動制御されてアキュムレータ７０から配管Ｐ１を通して気相冷媒を吸引して圧縮し高温高圧冷媒として配管Ｐ２内に吐出すると、この吐出冷媒は、配管Ｐ４を通して凝縮器５０にのみ供給される。これにより、上述のような凝縮器５０による空気流の加熱がなされる。また、凝縮器５０は、その内部の冷媒を両配管Ｐ６、Ｐ７、ＥＶＨ膨張弁９０及び配管Ｐ９を通して凝縮器１１０に供給する。
【００４１】
従って、凝縮器５０からの冷媒が凝縮器１１０により両電動ファン１１１の送風による外気と熱交換して両配管Ｐ１０、Ｐ１１、ＥＶＣ膨張弁１３０、両配管Ｐ１３、Ｐ１５、アキュムレータ７０及び配管Ｐ１を通り気相冷媒となって電動圧縮機６０に供給される。
これにより、車室内には温風の吹出空気流が吹き出される。
【００４２】
このような状態において、コンピュータプログラムがステップ２３０に進むと、室外側熱交換器１１０の着霜の有無が次のようにして判定される。
即ち、上記着霜の有無は、室外側熱交換器１１０の温度、即ち温度センサ１４０ｆの検出温度ＴＨＯ（℃）がＴＨＯ≦０及びＴＡＭ−ＴＨＯ≧１５の双方を１０分以上継続して満たすか否かにより、判定される。
【００４３】
ここで、ＴＨＯ≦０及びＴＡＭ−ＴＨＯ≧１５の双方が１０分以上継続して満たされれば、ステップ２３０における判定がＹＥＳとなる。このことは、室外側熱交換器１１０が暖房運転の継続により着霜していることを意味する。
そして、この判定のもと、ステップ２３１において、冷媒の目標飽和温度ＴＣＯが吸込温度ＴＩＮに応じて次の数３の式に基づき算出される。
【００４４】
【数３】
ＴＣＯ＝｛（ＴＡＯ−ＴＩＮ）／Φ｝＋ＴＩＮ
ここで、Φは凝縮器５０の温度効率を示すが、この温度効率は、図８のデータに基づき風量Ｖｔｏｔａｌに応じて決定される。
ついで、ステップ２３２において、電動圧縮機６０の冷媒の目標圧力ＳＰＯが図９のデータに基づき目標飽和温度ＴＣＯに応じて決定される。但し、目標圧力ＳＰＯは電動圧縮機６０の交流モータ６１の回転数Ｎｓの上昇（又は低下）に増大（又は減少）する。
【００４５】
しかして、ステップ２３０にて着霜ありと判定された場合には、目標圧力ＳＰＯ、即ち回転数Ｎｓは上昇するように決定される。
そして、ステップ２３２ａにおいて、エアミックスドア４０の開度ＳＷが次の数４の式に基づき算出される。
【００４６】
【数４】
ＳＷ＝〔｛ＴＡＯ−（ＴＥ−Ｃ）｝／｛ＴＣ−（ＴＥ−Ｃ）｝〕×１００（％）ここで、ＴＣは冷媒の飽和温度であって、この飽和温度ＴＣは、電動圧縮機６０の吐出圧（圧力センサ１４０の検出圧力ＳＰ）に応じて図７のデータに基づき決定される。
【００４７】
ついで、ステップ２３３において、電動圧縮機６０の回転数Ｎｓを上昇させるように処理し、かつ、エアミックスドア４０の開度ＳＷを回転数Ｎｓの上昇分に相当する値だけ減少させるように補正処理する。
その後、ステップ２３４において、マイクロコンピュータ６０に内蔵のタイマーをリセットスタートする。これに伴い、当該タイマーは計時を開始する。
このような処理後、ステップ２４０において、除霜要求の有無が次のようにして判定される。
【００４８】
即ち、室外側熱交換器１１０の温度である温度センサ１４０ｆの検出温度ＴＨＯが、ＴＨＯ≦０及びＴＡＭ−ＴＨＯ≧１８の双方を満たす場合には、ステップ２４０における判定がＹＥＳとなる。このことは、室外側熱交換器１１０の除霜要求があることを意味する。また、ステップ２４０における判定がＮＯとなる場合には、ステップ２５０における上記タイマーの計時時間が所定時間経過するまで、両ステップ２４０、２５０の処理が繰り返される。この間にステップ２５０における判定がＹＥＳとなるときは、除霜要求がないとの判定のもとにコンピュータプログラムはステップ２０１に戻る。
また、ステップ２４０における判定がＹＥＳになると、ステップ２４１にて、次のごとく除霜運転がなされる。
【００４９】
即ち、ステップ２３３での処理に基づき電動圧縮機６０の交流モータ６１の回転数Ｎｓが上記目標圧力ＳＰＯに応じて上昇される。このため、電動圧縮機６０の冷媒の吐出圧力及び温度がさらに上昇するとともに流量調整弁８０が全開状態にされる。
これに伴い、電動圧縮機６０への吐出冷媒の供給が流量調整弁８０を含むホットガスバイパス路Ｇをも通してなされる。これにより、室外側熱交換器１１０の着霜が効率よく融解されて的確に除霜される。
【００５０】
また、上述のごとく、電動圧縮機６０の冷媒の吐出圧力及び温度がさらに上昇すると、凝縮器５０の送風機２０からの空気流に対する加熱エネルギーが増大する。一方、上述のごとく、エアミックスドア４０の開度ＳＷが回転数Ｎｓの上昇分に相当する値だけ減少補正されるから、送風機２０からの空気流のうちエアミックスドア４０の開度ＳＷの減少分だけ凝縮器５０に流入することなく凝縮器バイパス路１３を通ることとなる。
【００５１】
これに伴い、結果として、吹出口からの吹出空気流の温度が上昇することなく除霜運転前の状態にほぼ維持されるので、暖房運転運転時に除霜処理を行っても、乗員の暖房感を良好に維持しつつ、室外側熱交換器１１０の着霜を的確に除去できる。
また、本発明は、自動車用空調装置に限定されることなく、一般的には車両や建築物等の空調装置に広く適用可能である。
【図面の簡単な説明】
【図１】本発明に係る電気自動車用空調装置の実施形態における空調ユニット及び冷房サイクル装置の暖房運転時における概略全体構成図である。
【図２】上記実施形態における空調ユニット及び冷房サイクル装置の冷房運転時における概略全体構成図である。
【図３】空調ユニット及び冷房サイクル装置のための電気回路構成図である。
【図４】図３のマイクロコンピュータの作用を示すフローチャートの前段部である。
【図５】当該フローチャートの後段部である。
【図６】数２の式におけるαと内外気割合との関係を示すグラフである。
【図７】数３の式における飽和温度ＴＣを決定するための図表である。
【図８】数４の式におけるΦと風量Ｖｔｏｔａｌとの関係を示すグラフである。
【図９】目標飽和温度ＴＣＯと目標圧力ＳＰＯとの関係を示す図表である。
【符号の説明】
Ｃ…冷房冷媒回路、Ｇ…ホットガスバイパス回路、Ｈ…暖房冷媒回路、
Ｒ…ヒートポンプ式冷凍サイクル装置、Ｕ…空調ユニット、
１０…空調ダクト、１１…内気吸込口、１２…外気吸込口、
１３…凝縮器バイパス路、２０…送風機、３０…室内側蒸発器、
４０…エアミックスドア、５０…室内側凝縮器、６０…電動圧縮機、
６０ａ…インバータ、１１０…室外側熱交換器、
１６０…マイクロコンピュータ、１８０…エアミックスドアサーボモータ。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an air conditioner, for example, an air conditioner including a heat pump refrigeration cycle apparatus suitable for use in an electric vehicle.
[0002]
[Prior art]
Conventionally, as an air conditioner for an electric vehicle, there is one provided with a heat pump type refrigeration cycle apparatus capable of defrosting and air conditioning.
And in this defrosting method of an air conditioner, after changing the flow of the refrigerant | coolant at the time of heating operation of a refrigeration cycle apparatus to the flow at the time of cooling operation, the defrost of the outdoor heat exchanger of a refrigeration cycle apparatus is performed.
[0003]
[Problems to be solved by the invention]
However, in the above air conditioner, even if the defrosting method as described above is executed while the electric vehicle is heating, the refrigeration cycle apparatus changes from the heating operation state to the cooling operation state, so that cold air blows out into the vehicle interior. As a result, the temperature in the passenger compartment decreases. Therefore, even if the defrosting is possible, there arises a problem that a good sense of heating cannot be given to the passenger of the electric vehicle.
[0004]
Therefore, in order to deal with the above, the present invention, in an air conditioner equipped with a heat pump refrigeration cycle apparatus, while maintaining the refrigeration cycle apparatus in a heating operation state, without impairing the proper heating sense, The purpose is to defrost the outdoor heat exchanger.
[0005]
[Means for Solving the Problems]
In achieving the above object, an air conditioner according to claims 1 and 2 includes an air conditioning unit (U) and a heat pump refrigeration cycle apparatus (R).
Air conditioning unit
An air conditioning duct (10);
A blower (20) provided in the air-conditioning duct and blowing out air from the air-conditioning duct outlet through the air inlets (11, 12) of the air-conditioning duct;
An indoor evaporator (30) provided in the air conditioning duct on the downstream side of the blower to cool the air flow according to the incoming refrigerant;
An indoor condenser (50) provided in the air conditioning duct on the downstream side of the indoor evaporator and heating the air flow according to the incoming refrigerant;
An air mix door which operates to open one of the condenser bypass passage (13) and the indoor condenser on the downstream side of the indoor evaporator in the air conditioning duct and to close the other. (40).
[0006]
In addition to the indoor condenser and the indoor evaporator, the refrigeration cycle apparatus
A compressor (60) for compressing the suction refrigerant according to driving;
An outdoor heat exchanger (110) that is provided on the outdoor side and performs heat exchange according to the outside air and the inflowing refrigerant,
A heating refrigerant circuit (H) is configured to sequentially circulate the compressed refrigerant of the compressor to the indoor condenser and the outdoor heat exchanger as each inflow refrigerant during the heating operation, and the compressed refrigerant of the compressor is disposed indoors during the cooling operation. A cooling refrigerant circuit (C) is configured to sequentially circulate through the condenser, the outdoor heat exchanger, and the indoor evaporator as each inflow refrigerant.
[0007]
The air conditioner
Compressor control means (60a, 222, 231, 232, 233) for controlling the compressor to drive;
The opening of the air mix door is the maximum opening that fully opens the indoor condenser and fully closes the condenser bypass path during heating operation, and fully closes the indoor condenser and condenser bypass during cooling operation. Air mix door control means (180, 208, 233, 241) for controlling the air mix door so as to have a minimum opening degree to fully open the road;
Frosting determination means (230) for determining the presence or absence of frost formation on the outdoor heat exchanger during heating operation.
[0008]
Then, the compressor control means controls the compressor to increase its rotational speed when it is determined that frost is formed by the frost determination means,
The air mix door control means controls the air mix door in the direction of closing from its full open when it is determined that the frost determination means has frost formation,
The refrigeration cycle apparatus has hot gas bypass means (G, 241) for supplying refrigerant to the outdoor heat exchanger that is compressed by the compressor in accordance with the increase in the number of revolutions when the frost determination means determines that frost is present. ).
[0009]
As described above, when the frosting determination means determines that the outdoor heat exchanger has frosted during the heating operation, the compressor control means controls the compressor to increase its rotational speed, and the hot gas bypass means Supplies the refrigerant which is compressed by the compressor according to the increase in the rotational speed thereof to the outdoor heat exchanger.
Thereby, the frost formation of the outdoor heat exchanger is melted by the compressed refrigerant from the hot gas bypass means. As a result, the defrosting of the outdoor heat exchanger is satisfactorily performed in the heating operation state.
[0010]
In addition, as described above, the air mix door control means controls the air mix door in the direction of closing the air mix door from its full opening in accordance with the determination that frost formation is present by the frost determination means, so that the air flow to the condenser bypass path is controlled. The amount of inflow increases and the amount heated by the indoor condenser decreases. As a result, even if the heating energy of the indoor condenser is increased by the refrigerant compressed in accordance with the increase in the number of rotations by the compressor, the effect of defrosting can be ensured while maintaining an appropriate heating feeling.
[0011]
In the invention according to claim 1,Means (203) for calculating a target blowing temperature (TAO) of the air flow into the passenger compartment, a temperature sensor (140c) for detecting an air flow outflow side temperature (TE) of the indoor evaporator, and a discharge pressure of the compressor And a pressure sensor (140) for detecting (SP), and the air mix door control means determines the opening of the air mix door based on the calculated opening of the air mix door when the frost determination means determines that frost is present. Determined based on the target flow temperature of the flow, the detected air flow outlet temperature of the indoor evaporator and the detected compressor discharge pressure,The air mix door control means includes correction means (233) for correcting the opening degree of the air mix door so as to reduce the opening amount of the compressor by an increase in the number of rotations of the compressor. Control the door.In the second aspect of the invention, the means (203) for calculating the target outlet temperature (TAO) of the air flow into the passenger compartment and the temperature for detecting the air flow outlet side temperature (TE) of the indoor evaporator. A sensor (140c) and a pressure sensor (140) for detecting the discharge pressure (SP) of the compressor, and the air mix door control means opens the air mix door when the frost determination means determines that frost is formed. The refrigerant saturation temperature (determined based on the calculated target outlet temperature of the air flow into the passenger compartment, the detected air flow outlet temperature of the indoor evaporator and the detected discharge pressure of the compressor) TC), and the air mix door control means includes correction means (233) for correcting the air mix door so that the opening degree of the air mix door is decreased by the increase in the rotational speed of the compressor. Air to correct the opening To control the Kkusudoa.
[0012]
ThisSuitableThe effect of performing defrosting while maintaining a positive feeling of heating can be achieved more accurately. In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment description later mentioned.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
1 and 2 each show the overall configuration of an embodiment of an air conditioner for an electric vehicle according to the present invention. This air conditioner is composed of an indoor air conditioning unit U and a refrigeration cycle apparatus R. ing. A refrigerant circuit (hereinafter referred to as a heating refrigerant circuit H) indicated by a bold line in FIG. 1 corresponds to a heating operation state of the air conditioner, and a refrigerant circuit (hereinafter referred to as a cooling refrigerant circuit C) indicated by a bold line in FIG. Corresponds to the cooling operation state of the air conditioner.
[0014]
The air conditioning unit U is provided in the passenger compartment of the electric vehicle. As shown in FIG. 1, the air conditioning unit U has a blower 20 in the air conditioning duct 10 and an evaporation for cooling that is an indoor heat exchanger. The heat exchanger 30, the air mix door 40, and the heating condenser 50 as an indoor heat exchanger are sequentially arranged.
The blower 20 sucks the outside air or the inside air as an air flow from the outside air inlet 11 or the inside air inlet 12 into the air conditioning duct 10 and blows it toward the cooling evaporator 30. Here, the outside air suction port 11 and the inside air suction port 12 are selectively switched and opened and closed by an inside / outside air switching door (not shown) of the air conditioning duct 10.
[0015]
The evaporator 30 cools the air flow from the blower 20 and flows toward the air mix door 40 during the cooling operation. The air mix door 40 fully opens the condenser 50 at the position shown in FIG. 1 and fully closes the condenser bypass 13 formed on the side of the condenser 50 in the air conditioning duct 10. The opening of the air mix door 40 at this time is defined as the maximum opening. On the other hand, the air mix door 40 fully closes the condenser 50 and fully opens the condenser bypass 13 at the position shown in FIG. The opening degree of the air mix door 40 at this time is set as the minimum opening degree.
[0016]
The condenser 50 heats the airflow blown from the blower 20 through the evaporator 30 during the heating operation.
The air flow thus heated or the cooling air flow passing through the condenser bypass 13 is blown out from any one of the air outlets of the air conditioning duct 10 as a blown air flow.
The refrigeration cycle apparatus R includes the indoor evaporator 30 and the indoor condenser 50 as its constituent elements. The indoor-side evaporator 30 functions as a cooler that is an indoor-side heat exchanger that cools the air flow from the blower 20 by the endothermic action of the refrigerant that flows inside. Moreover, the indoor side condenser 50 functions as a heater which is an indoor side heat exchanger that heats the inflow air flow by the heat radiation action of the refrigerant flowing inside.
[0017]
By the way, the refrigeration cycle apparatus R is configured as a heat pump refrigeration cycle apparatus that cools and heats the passenger compartment with the evaporator 30 and the condenser 50, and the refrigeration cycle apparatus R includes a heating refrigerant circuit H (see FIG. 1). Or in order to comprise the cooling refrigerant circuit C (refer FIG. 2), in addition to the said evaporator 30 and the condenser 50, the following each component is provided.
[0018]
That is, the electric compressor 60 sucks the gas-phase refrigerant from the accumulator 70 from the pipe P1 and supplies it as a high-temperature and high-pressure refrigerant to the flow rate adjusting valve 80 through both pipes P2 and P3 and to the condenser 50 through both pipes P2 and P4. Supply.
The flow rate adjustment valve 80 is controlled to be fully closed when the refrigeration cycle apparatus R is in the heating operation state and fully open when the cooling operation state is in the cooling operation state. For this reason, the flow regulating valve 80 supplies the high-temperature and high-pressure refrigerant in the pipe P3 into the pipe P5 when fully opened, and shuts off this supply when fully closed. The flow rate adjusting valve 80 constitutes a hot gas bypass circuit G together with both the pipes P3 and P5.
[0019]
Further, the condenser 50 described above heats the cooling air flow from the evaporator 30 as described above based on the heat radiation action of the high-temperature and high-pressure refrigerant from the pipe P4, and then the evaporative refrigerant passes through the pipe P6 and the heating side electric expansion valve 90 is heated. The evaporative refrigerant is supplied to the VC solenoid valve 100 through both pipes P6 and P7.
Here, the heating-side electric expansion valve 90 is controlled to be closed during the cooling operation of the refrigeration cycle apparatus R and opened during the heating operation. Further, the VC solenoid valve 100 is controlled to open during the cooling operation of the refrigeration cycle apparatus R and close during the heating operation.
[0020]
For this reason, the heating-side electric expansion valve 90 supplies the evaporative refrigerant from the pipe P6 to the outdoor heat exchanger 110 through the downstream portions of the pipe P9 and the pipe P5 when the heating side electric expansion valve 90 is opened, and shuts off this supply when the valve is closed. . The VC solenoid valve 100 supplies the evaporative refrigerant from both the pipes P6 and P7 to the outdoor heat exchanger 110 through the downstream parts of both the pipes P8 and P9 and the pipe P5 when the VC solenoid valve 100 is opened, and shuts off this supply when closed. .
[0021]
The outdoor heat exchanger 110 exchanges heat between the refrigerant passing through the inside and the outside air under the blowing of the electric fans 111. For example, the outdoor heat exchanger 110 functions as a condenser during the cooling operation, cools the inflowing refrigerant with outside air by the air blown by the both electric fans 111, and functions as an evaporator during the heating operation, Is absorbed by the outside air by the electric fans 111 and evaporated. The outdoor heat exchanger 110 then supplies the refrigerant to the EVC cooling side electric expansion valve 120 and the VH solenoid valve 130 through the pipe P10 and the pipe P11.
[0022]
Here, the EVC cooling side electromagnetic valve 120 is controlled to open during the cooling operation of the refrigeration cycle apparatus R and close during the heating operation. The VH solenoid valve 130 is controlled to be closed during the cooling operation of the refrigeration cycle apparatus R and opened during the heating operation.
For this reason, the EVC cooling side electromagnetic valve 120 supplies the refrigerant from the pipe P10 to the evaporator 30 through the pipe P12 when the EVC cooling side electromagnetic valve 120 is opened, and shuts off this supply when closed. When the VH solenoid valve 130 is opened, the refrigerant from the pipe P11 is supplied to the accumulator 70 through both pipes P13 and P15, and this supply is shut off when the valve is closed.
[0023]
Therefore, the evaporator 30 supplies the inflowing refrigerant to the accumulator 70 through both pipes P14 and P15 when the VH solenoid valve 130 is closed. The accumulator 70 accumulates the liquid phase refrigerant among the refrigerant from the pipe P15 and supplies the gas-phase refrigerant to the electric compressor 60 through the pipe P1.
The condenser 110 and both electric fans 111 are installed outside the passenger compartment of the electric vehicle.
[0024]
Next, the electric circuit configuration of the air conditioner will be described with reference to FIGS.
As shown in FIG. 1, the pressure sensor 140 is provided at an intermediate portion of the pipe P2, and detects the pressure SP of the refrigerant in the pipe P2. The outside air temperature sensor 140a is provided outside the passenger compartment of the electric vehicle and detects the outside air temperature TAM. The inside air temperature sensor 140b is provided in the passenger compartment of the electric vehicle and detects the inside air temperature TR.
[0025]
The post-evaporation sensor 140c is provided on the cooling flow outflow side of the evaporator 30 and detects the air flow outflow side temperature of the evaporator 30 as the post-evaporation temperature TE. The solar radiation sensor 140d detects the solar radiation amount TS. The temperature sensor 140e is provided at the refrigerant outlet of the outdoor heat exchanger 110 and detects the temperature THO of the refrigerant flowing into the pipe P10.
The operation panel 150 is provided in the passenger compartment of the electric vehicle, and the operation panel 150 outputs the set temperature TSET and the like in the passenger compartment as signals necessary for controlling the air conditioner.
[0026]
The microcomputer 160 executes a computer program according to the flowcharts of FIGS. 4 and 5, and during this execution, based on the detection outputs of the plurality of sensors 140 to 140 e and the output signals of the operation panel 150, the inverter 60 a, Flow adjustment valve 80, EVH expansion valve 90, VC solenoid valve 100, EVC expansion valve 120, VH solenoid valve 130, motor of blower 20, motor of both electric fans 111, inside / outside air switching servo motor 170, air mix door servo motor 180 And the process which carries out drive control of the blower outlet switching servomotor 190 is performed. The computer program is stored in advance in the ROM of the microcomputer 160.
[0027]
The inverter 60 a drives and controls the AC motor 61 of the electric compressor 60 under the control of the microcomputer 160.
The inside / outside air switching servo motor 170 switches and controls the inside / outside air switching door under the control of the microcomputer 160. The air mix door servo motor 180 controls opening and closing of the air mix door 40 under the control of the microcomputer 160. Under the control of the microcomputer 150, the air outlet servomotor 190 performs switching control of the air outlet switching door that switches the opening and closing of the air outlets.
[0028]
In the present embodiment configured as described above, when the microcomputer 160 starts executing the computer program according to the flowcharts of FIGS. 4 and 5, in step 200, the inside of the microcomputer 160 is initialized. Next, the set temperature TSET in the passenger compartment is read from the operation panel 150 in step 201. Thereafter, in step 202, outputs from the sensors 140 to 140e are read.
[0029]
Next, in step 203, the target blowout temperature TAO of the air flow into the vehicle interior is set temperature TSET, the internal air temperature TR from the internal air temperature sensor 140b, the external air temperature TAM from the external air temperature sensor 140a, and the solar radiation amount TS from the solar radiation sensor 140d. Is calculated based on the following equation (1).
[0030]
[Expression 1]
TAO = Kset, TSET-Kr, TR-Kam, TAM-Ks, TS-K
Here, in this embodiment, for example, Kset = 5.8, Kr = 3.4, Kam = 1.0, Ks = 1.0, and K = 11. The expression of Equation 1 is stored in advance in the ROM of the microcomputer 160.
[0031]
Thereafter, in step 204, the voltage for driving the motor of the blower 20 (so-called blower voltage) is determined, in step 205, the outlet mode is determined, and in step 206, the inlet mode is determined.
Next, at step 207, the suction temperature TIN is calculated based on the following equation 2 according to the outside air temperature TAM and the inside air temperature TR.
[0032]
[Expression 2]
TIN = α · TAM + (1-α) TR
Here, α varies in the range of 0 to 1 in proportion to the inside / outside air ratio PAI (see FIG. 6).
After the above processing is performed, in step 210, whether or not the air conditioner is to be in the cooling operation is determined based on whether or not (TAO−TIN) ≦ 3 is established.
[0033]
If (TAO-TIN) ≦ 3 is satisfied, the determination in step 210 is YES, and in step 211, the refrigeration cycle apparatus R is placed in the cooling operation together with the air conditioning unit U (see FIG. 2).
That is, in the air conditioning unit U, the opening degree of the air mix door 40 (hereinafter referred to as the opening degree SW) is determined as the opening degree SW = 0, and the air mixing door 40 is based on the opening degree SW = 0. Driven by the motor 180, the condenser 50 is fully closed and the bypass passage 13 is fully opened. Note that the opening degree SW = 0 represents the maximum cooling (MAXCOOL) corresponding to the minimum opening degree of the air mix door 40.
[0034]
For this reason, when the blower 20 is driven by the motor based on the blower voltage and the outside air or the inside air is blown into the air conditioning duct 10 as the air flow in the determined suction port mode, the air flow is It flows toward the air outlet side of the air conditioning duct 10 through the bypass 13.
At this time, the air flow is cooled by the evaporator 30 and is blown out from the air outlet of the air conditioning duct 10 as the cooling air flow (having the target outlet temperature TAO) in the above-described determined outlet mode.
[0035]
In the refrigeration cycle apparatus R, the flow rate adjustment valve 80 is fully opened, the VC solenoid valve 100 and the EVH expansion valve 120 are opened, while the EVH expansion valve 90 and the EVC expansion valve 130 are closed. .
For this reason, when the electric compressor 60 is driven by the inverter 60a by the AC motor 61 and sucks and compresses the gas-phase refrigerant from the accumulator 70 through the pipe P1 and discharges it into the pipe P2 as a high-temperature and high-pressure refrigerant, the discharged refrigerant is , Pipe P4, condenser 50, both pipes P6 and P7, VC solenoid valve 100 and both pipes P8 and P9, and flows into outdoor heat exchanger 110, while pipe P3, flow rate adjusting valve 80, pipe P5 and pipe P9. It flows into the outdoor heat exchanger 110 through the downstream part.
[0036]
Accordingly, the high-temperature and high-pressure refrigerant from the electric compressor 60 and the refrigerant from the condenser 50 are air-cooled by the outdoor heat exchanger 110 under the air-cooling action by the both electric fans 111 and evaporate from the EVH expansion valve 120 through the pipe P10. Supplied to the container 30. As a result, the air flow is cooled by the evaporator 30 as described above. Further, the refrigerant inside the evaporator 30 passes through both pipes P14 and P15, the accumulator 70 and the pipe P1, and is supplied to the electric compressor 60 as a gas phase refrigerant.
[0037]
As a result, a cold air blowing air flow is blown out into the passenger compartment.
Further, when the determination in step 210 is NO, in step 220, it is determined based on whether (TAO-TIN)> 3 is established, whether or not the air conditioner is placed in either the air blowing operation or the heating operation.
Here, if (TAO-TIN)> 3 is not established, the determination in step 220 is NO, and in step 221, the air blowing operation by the blower 20 of the air conditioning unit U is performed.
[0038]
On the other hand, if the determination in step 220 is YES, in step 222, the refrigeration cycle apparatus R and the air conditioning unit U are placed in the heating operation.
That is, in the air conditioning unit U, the opening degree of the air mix door 40 is determined as SW = 100, and the condenser 50 is completely opened by being driven by the air mix door servo motor 180 based on the opening degree SW = 100. It becomes. SW = 100 represents maximum heating (MAXHOT) corresponding to the maximum opening of the air mix door 40.
[0039]
For this reason, when the blower 20 is driven by the motor based on the blower voltage and the outside air or the inside air is blown into the air conditioning duct 10 as the air flow in the determined suction port mode, the air flow is It flows toward the air outlet side of the air conditioning duct 10 through the condenser 50. At this time, the air flow is heated by the condenser 50 without being cooled by the evaporator 30 and is heated as the air flow for heating (having the target blowing temperature TAO), and the air outlet of the air conditioning duct 10 in the determined outlet mode. Blow out from.
[0040]
In the refrigeration cycle apparatus R, the flow rate adjusting valve 80, the VC solenoid valve 100, and the EVH expansion valve 120 are closed, while the EVH expansion valve 90 and the EVC expansion valve 130 are opened.
For this reason, when the electric compressor 60 is driven and controlled by the inverter 60a by the AC motor 61 and sucks and compresses the gas-phase refrigerant from the accumulator 70 through the pipe P1, and discharges it into the pipe P2 as a high-temperature and high-pressure refrigerant. Is supplied only to the condenser 50 through the pipe P4. Thereby, the air flow is heated by the condenser 50 as described above. Further, the condenser 50 supplies the internal refrigerant to the condenser 110 through both pipes P6 and P7, the EVH expansion valve 90 and the pipe P9.
[0041]
Therefore, the refrigerant from the condenser 50 exchanges heat with the outside air generated by the two electric fans 111 by the condenser 110 and passes through the pipes P10, P11, the EVC expansion valve 130, the pipes P13, P15, the accumulator 70, and the pipe P1. It becomes a gas-phase refrigerant and is supplied to the electric compressor 60.
As a result, a hot air blowing air flow is blown into the passenger compartment.
[0042]
When the computer program proceeds to step 230 in such a state, the presence or absence of frost formation on the outdoor heat exchanger 110 is determined as follows.
That is, whether the frost is present or not satisfies whether the temperature of the outdoor heat exchanger 110, that is, the detected temperature THO (° C) of the temperature sensor 140f continuously satisfies both THO ≦ 0 and TAM-THO ≧ 15 for 10 minutes or more. It is determined depending on whether or not.
[0043]
Here, if both THO ≦ 0 and TAM-THO ≧ 15 are continuously satisfied for 10 minutes or more, the determination in step 230 is YES. This means that the outdoor heat exchanger 110 is frosted by continuing the heating operation.
Based on this determination, in step 231, the target saturation temperature TCO of the refrigerant is calculated based on the following equation 3 according to the suction temperature TIN.
[0044]
[Equation 3]
TCO = {(TAO-TIN) / Φ} + TIN
Here, Φ indicates the temperature efficiency of the condenser 50, and this temperature efficiency is determined according to the air volume Vtotal based on the data of FIG.
Next, at step 232, the target pressure SPO of the refrigerant of the electric compressor 60 is determined according to the target saturation temperature TCO based on the data of FIG. However, the target pressure SPO increases (or decreases) as the rotational speed Ns of the AC motor 61 of the electric compressor 60 increases (or decreases).
[0045]
Therefore, when it is determined in step 230 that frost formation has occurred, the target pressure SPO, that is, the rotational speed Ns is determined to increase.
In step 232a, the opening degree SW of the air mix door 40 is calculated based on the following equation (4).
[0046]
[Expression 4]
SW = [{TAO− (TE−C)} / {TC− (TE−C)}] × 100 (%) where TC is the saturation temperature of the refrigerant, and this saturation temperature TC is the electric compressor. It is determined based on the data of FIG. 7 according to the discharge pressure of 60 (the detected pressure SP of the pressure sensor 140).
[0047]
Next, in step 233, processing is performed so as to increase the rotational speed Ns of the electric compressor 60, and correction processing is performed so as to decrease the opening SW of the air mix door 40 by a value corresponding to the increase in the rotational speed Ns. To do.
Thereafter, in step 234, a timer built in the microcomputer 60 is reset and started. Along with this, the timer starts timing.
After such processing, in step 240, the presence / absence of a defrost request is determined as follows.
[0048]
That is, if the detected temperature THO of the temperature sensor 140f, which is the temperature of the outdoor heat exchanger 110, satisfies both THO ≦ 0 and TAM−THO ≧ 18, the determination in step 240 is YES. This means that there is a defrosting request for the outdoor heat exchanger 110. If the determination in step 240 is NO, the processes of both steps 240 and 250 are repeated until the time measured by the timer in step 250 elapses. If the determination in step 250 is YES during this time, the computer program returns to step 201 based on the determination that there is no defrost request.
If the determination in step 240 is YES, the defrosting operation is performed in step 241 as follows.
[0049]
That is, based on the processing in step 233, the rotational speed Ns of the AC motor 61 of the electric compressor 60 is increased according to the target pressure SPO. For this reason, the discharge pressure and temperature of the refrigerant of the electric compressor 60 further increase, and the flow rate adjustment valve 80 is fully opened.
Accordingly, the supply of the discharged refrigerant to the electric compressor 60 is also made through the hot gas bypass passage G including the flow rate adjusting valve 80. Thereby, the frost formation of the outdoor heat exchanger 110 is efficiently melted and defrosted accurately.
[0050]
Further, as described above, when the discharge pressure and temperature of the refrigerant of the electric compressor 60 further increase, the heating energy for the air flow from the blower 20 of the condenser 50 increases. On the other hand, as described above, the opening degree SW of the air mix door 40 is corrected to decrease by a value corresponding to the increase in the rotational speed Ns, so that the opening degree SW of the air mix door 40 is reduced in the air flow from the blower 20. It will pass through the condenser bypass 13 without flowing into the condenser 50 by the amount.
[0051]
As a result, since the temperature of the air flow from the outlet is not increased, the state before the defrosting operation is almost maintained, so that even if the defrosting process is performed during the heating operation, the passenger's feeling of heating The frost formation of the outdoor heat exchanger 110 can be accurately removed while maintaining the above.
In addition, the present invention is not limited to an automobile air conditioner, and is generally widely applicable to air conditioners such as vehicles and buildings.
[Brief description of the drawings]
BRIEF DESCRIPTION OF DRAWINGS FIG. 1 is a schematic overall configuration diagram of an air conditioning unit and a cooling cycle device in an embodiment of an air conditioner for an electric vehicle according to the present invention during heating operation.
FIG. 2 is a schematic overall configuration diagram of the air conditioning unit and the cooling cycle device in the embodiment at the time of cooling operation.
FIG. 3 is an electrical circuit configuration diagram for an air conditioning unit and a cooling cycle device.
4 is a front part of a flowchart showing the operation of the microcomputer of FIG. 3;
FIG. 5 is a latter part of the flowchart.
6 is a graph showing the relationship between α and the inside / outside air ratio in the equation (2).
FIG. 7 is a chart for determining a saturation temperature TC in the equation (3).
FIG. 8 is a graph showing the relationship between Φ and the air volume Vtotal in the equation (4).
FIG. 9 is a chart showing a relationship between a target saturation temperature TCO and a target pressure SPO.
[Explanation of symbols]
C ... Cooling refrigerant circuit, G ... Hot gas bypass circuit, H ... Heating refrigerant circuit,
R ... Heat pump refrigeration cycle device, U ... Air conditioning unit,
10 ... Air conditioning duct, 11 ... Inside air inlet, 12 ... Outside air inlet,
13 ... Condenser bypass, 20 ... Blower, 30 ... Indoor evaporator,
40 ... Air mix door, 50 ... Indoor condenser, 60 ... Electric compressor,
60a ... inverter, 110 ... outdoor heat exchanger,
160 ... microcomputer, 180 ... air mix door servo motor.

Claims

An air conditioning unit (U) and a heat pump refrigeration cycle apparatus (R);
The air conditioning unit is
An air conditioning duct (10);
A blower (20) provided in the air-conditioning duct and blowing out air from the air-conditioning duct as an air flow through the air-intake duct (11, 12);
An indoor evaporator (30) provided in the air conditioning duct on the downstream side of the blower to cool the air flow according to the incoming refrigerant;
An indoor condenser (50) provided in the air conditioning duct on the downstream side of the indoor evaporator and heating the air flow according to the inflowing refrigerant;
The condenser bypass passage (13) formed on the side of the indoor condenser in the air conditioning duct on the downstream side of the indoor evaporator and operates so as to open one of the indoor condenser and close the other. An air mix door (40)
In addition to the indoor condenser and the indoor evaporator, the refrigeration cycle apparatus,
A compressor (60) for compressing the suction refrigerant according to driving;
An outdoor heat exchanger (110) that is provided on the outdoor side and performs heat exchange according to the outside air and the inflowing refrigerant,
A heating refrigerant circuit (H) that sequentially circulates the compressed refrigerant of the compressor as the inflow refrigerant to the indoor condenser and the outdoor heat exchanger during the heating operation is configured, and during the cooling operation, the compressor of the compressor An air conditioner configured to constitute a cooling refrigerant circuit (C) that sequentially circulates compressed refrigerant as each inflow refrigerant to the indoor condenser, the outdoor heat exchanger, and the indoor evaporator,
Compressor control means (60a, 222, 231, 232, 233) for controlling the compressor to drive;
The opening degree of the air mix door is a maximum opening degree that fully opens the indoor-side condenser and fully closes the condenser bypass passage during heating operation, and fully closes the indoor-side condenser during cooling operation. And an air mix door control means (180, 208, 233, 241) for controlling the air mix door so as to have a minimum opening degree that fully opens the condenser bypass path;
Frost determination means (230) for determining the presence or absence of frost on the outdoor heat exchanger during heating operation,
The compressor control means controls the compressor to increase its rotational speed when it is determined that frost formation is present by the frost determination means,
The air mix door control means controls the air mix door in the direction of closing from its fully open when it is determined that the frost determination means has frost formation,
The refrigeration cycle apparatus includes a hot gas bypass unit that supplies the outdoor heat exchanger with a refrigerant that is compressed by the compressor in accordance with an increase in the number of revolutions when the frost determination unit determines that frost formation has occurred. (G, 241) is an air-conditioning system to have a,
Means (203) for calculating a target outlet temperature (TAO) of the air flow into the passenger compartment, a temperature sensor (140c) for detecting an air flow outflow side temperature (TE) of the indoor evaporator, A pressure sensor (140) for detecting the discharge pressure (SP),
The air mix door control means determines the opening degree of the air mix door at the time of the determination that the frost determination means has frost, the calculated target air temperature of the air flow into the vehicle interior, and the detected room Determined based on the air flow outlet temperature of the inner evaporator and the detected compressor discharge pressure,
The air mix door control means includes correction means (233) for correcting the air mix door so that the opening of the air mix door is decreased by an increase in the rotation speed of the compressor, and the correction opening by the correction means is obtained. The air conditioner is characterized by controlling the air mix door.

An air conditioning unit (U) and a heat pump refrigeration cycle apparatus (R);
The air conditioning unit is
An air conditioning duct (10);
A blower (20) provided in the air-conditioning duct and blowing out air from the air-conditioning duct as an air flow through the air-intake duct (11, 12);
An indoor evaporator (30) provided in the air conditioning duct on the downstream side of the blower to cool the air flow according to the incoming refrigerant;
An indoor condenser (50) provided in the air conditioning duct on the downstream side of the indoor evaporator and heating the air flow according to the inflowing refrigerant;
The condenser bypass passage (13) formed on the side of the indoor condenser in the air conditioning duct on the downstream side of the indoor evaporator and operates so as to open one of the indoor condenser and close the other. An air mix door (40)
In addition to the indoor condenser and the indoor evaporator, the refrigeration cycle apparatus,
A compressor (60) for compressing the suction refrigerant according to driving;
An outdoor heat exchanger (110) that is provided on the outdoor side and performs heat exchange according to the outside air and the inflowing refrigerant,
A heating refrigerant circuit (H) that sequentially circulates the compressed refrigerant of the compressor as the inflow refrigerant to the indoor condenser and the outdoor heat exchanger during the heating operation is configured, and during the cooling operation, the compressor of the compressor An air conditioner configured to constitute a cooling refrigerant circuit (C) that sequentially circulates compressed refrigerant as each inflow refrigerant to the indoor condenser, the outdoor heat exchanger, and the indoor evaporator,
Compressor control means (60a, 222, 231, 232, 233) for controlling the compressor to drive;
The opening degree of the air mix door is a maximum opening degree that fully opens the indoor-side condenser and fully closes the condenser bypass passage during heating operation, and fully closes the indoor-side condenser during cooling operation. And an air mix door control means (180, 208, 233, 241) for controlling the air mix door so as to have a minimum opening degree that fully opens the condenser bypass path;
Frost determination means (230) for determining the presence or absence of frost on the outdoor heat exchanger during heating operation,
The compressor control means controls the compressor to increase its rotational speed when it is determined that frost formation is present by the frost determination means,
The air mix door control means controls the air mix door in the direction of closing from its fully open when it is determined that the frost determination means has frost formation,
The refrigeration cycle apparatus includes a hot gas bypass unit that supplies the outdoor heat exchanger with a refrigerant that is compressed by the compressor in accordance with an increase in the number of revolutions when the frost determination unit determines that frost formation has occurred. (G, 241) is an air-conditioning system to have a,
Means (203) for calculating a target outlet temperature (TAO) of the air flow into the passenger compartment, a temperature sensor (140c) for detecting an air flow outflow side temperature (TE) of the indoor evaporator, A pressure sensor (140) for detecting the discharge pressure (SP),
The air mix door control means determines the opening degree of the air mix door at the time of the determination that the frost determination means has frost, the calculated target air temperature of the air flow into the vehicle interior, and the detected room An air flow outlet side temperature of the inner evaporator and a refrigerant saturation temperature (TC) determined based on the detected compressor discharge pressure;
The air mix door control means includes correction means (233) for correcting the air mix door so that the opening of the air mix door is decreased by an increase in the rotation speed of the compressor, and the correction opening by the correction means is obtained. The air conditioner is characterized by controlling the air mix door.