JP2004203085A

JP2004203085A - Air conditioner

Info

Publication number: JP2004203085A
Application number: JP2002371649A
Authority: JP
Inventors: Hisashi Ieda; 恒家田; Mitsuyo Omura; 充世大村
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2002-12-24
Filing date: 2002-12-24
Publication date: 2004-07-22

Abstract

<P>PROBLEM TO BE SOLVED: To prevent air conditioning feeling from being considerably deteriorated when switching an operation mode. <P>SOLUTION: When an absolute value of a rising ratio of a target after evaporation temperature TEO becomes larger than a prescribed value, an absolute value of a rate of change of a target increased numberΔf of revolution is reduced to lower the number of revolution of a compressor 7. As a result, problems wherein air conditioning feeling is deteriorated due to blowing of cold air having high humidity into a cabin in a transition period when transferring a mode from a heating mode or an air mix mode to a cooling mode and vibration or noise is generated when restarting the compressor 7 after finishing the transition period can be prevented from occurring since the compressor 7 can be prevented from being stopped due to substantial zero of circulating coolant flow rate. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、室内に吹き出す空気を加熱する熱源として、電気ヒータ等の廃熱以外のエネルギを用いた空調装置に関するもので、燃料電池を用いた電気自動車、又は内燃機関（エンジン）と電動モータとを組み合わせて走行する、いわゆるハイブリッド自動車等の電気自動車用の空調装置に適用して有効である。
【０００２】
【従来の技術】
内燃機関（エンジン）を有する車両用空調装置は、周知のごとく、エンジンの廃熱を熱源として室内に吹き出す空気を加熱する加熱器、蒸気圧縮式冷凍機により生成された冷熱により室内に吹き出す空気を加熱する冷却器、及び加熱器を通過して室内側に流れる温風の風量と加熱器を迂回して室内側に流れる冷風の風量との風量割合を調節するエアミックスドア等から構成され、室内に吹き出す空気の温度は、冷風と温風との混合割合、つまり加熱器を流れる風量と加熱器を迂回する風量との風量割合を調節することにより行っている。
【０００３】
【発明が解決しようとする課題】
ところで、電気自動車用の空調装置では、車両で発生する廃熱を加熱器の熱源として利用することが困難であるため、電気ヒータや燃焼式ヒータ等の熱源専用の機器を設ける必要がある。
【０００４】
このため、上記した従来の技術のごとく、加熱器を通過して室内側に流れる温風の風量と加熱器を迂回して室内側に流れる冷風の風量との風量割合を調節して室内に吹き出す空気の温度を調節すると、空調装置の消費エネルギ、つまり電気ヒータ及び蒸気圧縮式冷凍機の消費電力が増大してしまう。
【０００５】
そこで、発明者は、冷却器で発生する冷却能力を調節することにより室内に吹き出す空気の温度を調節する冷房モード、冷却器にて室内に吹き出す空気を露点温度以下まで低下させた後、加熱器にて露点温度以下まで低下した空気を所定温度まで加熱する除湿モード（除湿暖房モード）、及びエアミックスドアにて室内に吹き出す空気の温度を調節するエアミックスモードの少なくとも３つの運転モードを有する空調装置を試作検討したところ、以下に述べる問題が発生した。
【０００６】
すなわち、除湿運転時等に行われるエアミックスモード又は除湿暖房モードでは、冷却器で冷却された冷風が加熱器にて再加熱されているため、冷却器を通過した直後の空気温度は、実際に室内に吹き出す空気の温度より低くなる。
【０００７】
一方、冷房モードでは、温風量を０として冷却器で発生する冷却能力を調節することにより室内に吹き出す空気の温度を調節するので、冷却器を通過した直後の空気温度と実際に室内に吹き出す空気の温度とは略等しい。
【０００８】
そして、冷却器で発生する冷凍能力は、冷却器を通過した空気の温度が目標温度（目標エバ後温度ＴＥＯ）となるように圧縮機の回転数を制御する等して、循環冷媒流量を制御することにより調節されるので、冷房モード時における目標エバ後温度ＴＥＯよりエアミックスモード又は除湿暖房モード時における目標エバ後温度ＴＥＯの方が低い場合がある。
【０００９】
このため、エアミックスモード又は除湿暖房モードから冷房モードに切り替わると、目標エバ後温度ＴＥＯが急上昇してしまい、運転モードが切り替わった時から所定時間（過渡期間）は冷房能力が過剰となってしまうので、図１２（ｂ）に示すように、圧縮機を停止させる等して循環冷媒流量が略０となってしまう状態が発生する。
【００１０】
したがって、循環冷媒流量が略０となってしまう過渡期間においては、湿度が高い冷風が車室内に吹き出されて空調感が悪化してしまうといった問題、及び過渡期間が終了して圧縮機を再起動した時に振動や騒音が発生してしまうといった問題等が発生する。
【００１１】
本発明は、上記点に鑑み、第１には、従来と異なる新規な空調装置を提供し、第２には、運転モードが切り替わったとき空調感が大きく悪化してしまうことを防止することを目的とする。
【００１２】
【課題を解決するための手段】
本発明は、上記目的を達成するために、請求項１に記載の発明では、室内に吹き出す空気と減圧された冷媒とを熱交換させて室内に吹き出す空気を冷却する冷却器（６）と、冷却器（６）にて室内に吹き出す空気から吸熱して蒸発した冷媒を圧縮して放熱器（８）に供給する圧縮機（７）と、室内に吹き出す空気を加熱する加熱器（１２）と、冷却器（６）を通過した空気の温度が目標温度（ＴＥＯ）となるように循環冷媒流量を制御する流量制御手段とを備え、流量制御手段は、目標温度（ＴＥＯ）の上昇率の絶対値が所定値より大きいときには、目標温度（ＴＥＯ）の変化率の絶対値が所定値以下のときに比べて、循環冷媒流量の変化率の絶対値を小さくすることを特徴とする。
【００１３】
これにより、循環冷媒流量が略０となってしまうことを防止できるので、過渡期間において、湿度が高い冷風が車室内に吹き出されて空調感が悪化してしまう、及び過渡期間が終了して圧縮機を再起動した時に振動や騒音が発生してしまうといった問題が発生してしまうことを防止できる。
【００１４】
請求項２に記載の発明では、室内に吹き出す空気と減圧された冷媒とを熱交換させて室内に吹き出す空気を冷却する冷却器（６）と、冷却器（６）にて室内に吹き出す空気から吸熱して蒸発した冷媒を圧縮して放熱器（８）に供給する圧縮機（７）と、室内に吹き出す空気を加熱する加熱器（１２）と、冷却器（６）を通過した空気の目標温度（ＴＥＯ）を決定する目標温度決定手段と、冷却器（６）を通過した空気の温度が目標温度（ＴＥＯ）となるように循環冷媒流量を制御する流量制御手段と、目標温度決定手段が決定した目標温度（ＴＥＯ）の上昇率の絶対値が所定値より大きいときには、目標温度決定手段が決定した目標温度（ＴＥＯ）の変化率の絶対値が所定値以下のときに比べて、目標温度（ＴＥＯ）の上昇率の絶対値を小さくする目標温度補正手段とを備えることを特徴とする。
【００１５】
これにより、循環冷媒流量が略０となってしまうことを防止できるので、過渡期間において、湿度が高い冷風が車室内に吹き出されて空調感が悪化してしまう、及び過渡期間が終了して圧縮機を再起動した時に振動や騒音が発生してしまうといった問題が発生してしまうことを防止できる。
【００１６】
請求項３に記載の発明では、室内に吹き出す空気と減圧された冷媒とを熱交換させて室内に吹き出す空気を冷却する冷却器（６）と、冷却器（６）にて室内に吹き出す空気から吸熱して蒸発した冷媒を圧縮して放熱器（８）に供給する圧縮機（７）と、室内に吹き出す空気を加熱する加熱器（１２）と、冷却器（６）を通過した空気の温度が目標温度（ＴＥＯ）となるように循環冷媒流量を制御する流量制御手段と、冷却器（６）で発生する冷却能力を調節することにより室内に吹き出す空気の温度を調節する冷房モードと、冷却器（６）にて室内に吹き出す空気を露点温度以下まで低下させた後、加熱器（１２）にて露点温度以下まで低下した空気を所定温度まで加熱する除湿モードとを切り替える運転モード切替手段とを備え、流量制御手段は、除湿モードから冷房モードに切り替わった時から所定時間は、除湿モード又は冷房モード時における循環冷媒流量の変化率の絶対値に比べて、循環冷媒流量の変化率の絶対値を小さくすることを特徴とする。
【００１７】
これにより、循環冷媒流量が略０となってしまうことを防止できるので、過渡期間において、湿度が高い冷風が車室内に吹き出されて空調感が悪化してしまう、及び過渡期間が終了して圧縮機を再起動した時に振動や騒音が発生してしまうといった問題が発生してしまうことを防止できる。
【００１８】
請求項４に記載の発明では、室内に吹き出す空気と減圧された冷媒とを熱交換させて室内に吹き出す空気を冷却する冷却器（６）と、冷却器（６）にて室内に吹き出す空気から吸熱して蒸発した冷媒を圧縮して放熱器（８）に供給する圧縮機（７）と、室内に吹き出す空気を加熱する加熱器（１２）と、冷却器（６）を通過した空気の目標温度（ＴＥＯ）を決定する目標温度決定手段と、冷却器（６）を通過した空気の温度が目標温度（ＴＥＯ）となるように循環冷媒流量を制御する流量制御手段と、除湿モードから冷房モードに切り替わった時から所定時間に、除湿モード又は冷房モード時において目標温度決定手段が決定した目標温度（ＴＥＯ）の変化率の絶対値に比べて、目標温度（ＴＥＯ）の変化率の絶対値を小さくする目標温度補正手段とを備えることを特徴とする。
【００１９】
これにより、循環冷媒流量が略０となってしまうことを防止できるので、過渡期間において、湿度が高い冷風が車室内に吹き出されて空調感が悪化してしまう、及び過渡期間が終了して圧縮機を再起動した時に振動や騒音が発生してしまうといった問題が発生してしまうことを防止できる。
【００２０】
請求項５に記載の発明では、室内に吹き出す空気と減圧された冷媒とを熱交換させて室内に吹き出す空気を冷却する冷却器（６）と、冷却器（６）にて室内に吹き出す空気から吸熱して蒸発した冷媒を圧縮して放熱器（８）に供給する圧縮機（７）と、室内に吹き出す空気を加熱する加熱器（１２）と、冷却器（６）を通過した空気の温度が目標温度（ＴＥＯ）となるように循環冷媒流量を制御する流量制御手段とを備え、流量制御手段は、目標温度（ＴＥＯ）の上昇率の絶対値が所定値より大きいときには、循環冷媒流量を所定流量以下まで低下させないことを特徴とする。
【００２１】
これにより、循環冷媒流量が略０となってしまうことを防止できるので、過渡期間において、湿度が高い冷風が車室内に吹き出されて空調感が悪化してしまう、及び過渡期間が終了して圧縮機を再起動した時に振動や騒音が発生してしまうといった問題が発生してしまうことを防止できる。
【００２２】
請求項６に記載の発明では、室内に吹き出す空気と減圧された冷媒とを熱交換させて室内に吹き出す空気を冷却する冷却器（６）と、冷却器（６）にて室内に吹き出す空気から吸熱して蒸発した冷媒を圧縮して放熱器（８）に供給する圧縮機（７）と、室内に吹き出す空気を加熱する加熱器（１２）と、冷却器（６）を通過した空気の温度が目標温度（ＴＥＯ）となるように循環冷媒流量を制御する流量制御手段と、冷却器（６）で発生する冷却能力を調節することにより室内に吹き出す空気の温度を調節する冷房モードと、冷却器（６）にて室内に吹き出す空気を露点温度以下まで低下させた後、加熱器（１２）にて露点温度以下まで低下した空気を所定温度まで加熱する除湿モードとを切り替える運転モード切替手段とを備え、流量制御手段は、除湿モードから冷房モードに切り替わった時から所定時間は、循環冷媒流量を所定流量以下まで低下させないことを特徴とする。
【００２３】
これにより、循環冷媒流量が略０となってしまうことを防止できるので、過渡期間において、湿度が高い冷風が車室内に吹き出されて空調感が悪化してしまう、及び過渡期間が終了して圧縮機を再起動した時に振動や騒音が発生してしまうといった問題が発生してしまうことを防止できる。
【００２４】
因みに、上記各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示す一例である。
【００２５】
【発明の実施の形態】
（第１実施形態）
本実施形態は、本発明に係る空調装置を電気自動車に適用したものであって、図１は本実施形態に係る空調装置の模式図である。
【００２６】
空調ケーシング１は室内に吹き出す空気の流路を構成するダクト手段であり、この空調ケーシング１の空気流れ上流側部位には、車室内空気を導入する内気導入口２及び車室外空気を導入する外気導入口３が形成されており、空調ケーシング１に導入する内気の量及び外気の量は内外気切替ドア４により調節される。
【００２７】
送風機５は室内に空気を送風する遠心式のファンであり、蒸発器６は送風機５から送風された空気と冷媒とを熱交換し、液相冷媒を蒸発させることにより空気を冷却する冷却器である。
【００２８】
ここで、蒸発器６は蒸気圧縮式冷凍機の低圧側熱交換器であり、蒸気圧縮式冷凍機は、周知のごとく、冷媒を吸入圧縮する圧縮機７、圧縮機７から吐出する冷媒を冷却する放熱器８、冷却された冷媒を減圧する減圧器９、及び蒸発器６から流出する冷媒を気相冷媒と液相冷媒とに分離して余剰冷媒を液相冷媒として蓄える気液分離器１０等からなるものである。
【００２９】
因みに、本実施形態に係る圧縮機７は、冷媒を吸入圧縮する圧縮機構及び圧縮機構を駆動する電動モータが一体となったものであり、本実施形態では、圧縮機７（電動モータ）の回転数をファジィ制御することにより循環冷媒流量を調節して蒸気圧縮式冷凍機（蒸発器６）の冷却能力を制御する。
【００３０】
そして、本実施形態では、減圧器９として、キャピラリチューブや固定絞り等の絞り開度が固定された減圧手段を用い、気液分離器１０は、圧縮機７の吸入側に配置されて分離された気相冷媒を圧縮機７の吸入側に流出する。
【００３１】
また、空調ケーシング１内のうち蒸発器６の空気流れ下流側には、電気ヒータ１１にて加熱された温水を熱源として蒸発器６を通過した空気を加熱する加熱器をなすヒータ１２が配設されているとともに、このヒータ１２を迂回させて空気を下流側に流通させるバイパス通路１３が設けられている。
【００３２】
なお、リザーブタンク１１ａは、温水水位の変動を吸収するタンク手段であり、ポンプ１１ｂは温水を循環させる電動ポンプである。
【００３３】
エアミックスドア１４は、蒸発器６にて冷却されてバイパス通路１３を流通する冷風量とヒータ１２を通過して加熱される空気（暖風）量とを調整するエアミックス手段である。
【００３４】
また、空調ケーシング１の最下流側部位には、車室内乗員の上半身（車室内上方側）に空調空気を吹き出すためのフェイス吹出口１４と、車室内乗員の足元（車室内下方側）に空気を吹き出すためのフット吹出口１５と、車両窓ガラスの内面に向かって空気を吹き出すためのデフロスタ吹出口１６とが形成されており、各吹出口１４〜１６の空気流れ上流側部位には、各吹出口１４〜１６を開閉制御する吹出モード切換ドア１４ａ〜１６ａが設けられている。
【００３５】
なお、圧縮機７、つまり電動モータ及び電気ヒータ１１は、電子制御装置（ＥＣＵ）により制御されており、図２は、圧縮機７の電動モータを駆動するインバータ式の駆動回路、電気ヒータ１１への通電量を制御するヒータ用ＩＧＢＴ、及び電気回路に過電流が流れることを防止する電源遮断用のメインリレー等が設けられた空調装置用電気回路図である。
【００３６】
また、ＥＣＵ１７には、室外空気の温度を検出する外気温度センサ（外気温度検出手段）１７ａ、蒸発器６を通過した直後の空気の温度、つまり蒸発器６の温度を検出する蒸発温度センサ（蒸発器温度検出手段）１７ｂ、室内空気の温度を検出する内気気温度センサ（内気温度検出手段）１７ｃ、車室内に注がれる日射量を検出する日射センサ（日射量検出手段）１７ｄ等の、及び電気ヒータ１１にて加熱された温水の温度を検出する水温センサ１７ｅ等空調センサ群の検出値、並びに乗員が希望する室内温度を設定入力する温度コントロールパネル１７ｆに入力された設定値が入力されている。
【００３７】
次に、圧縮機７の制御方法について述べる。
【００３８】
圧縮機７の回転数、つまり循環冷媒流量の制御は、前述のごとく、ファジィ理論に基づいて制御されるが、その概略は以下のようなものである。
【００３９】
先ず、蒸発器６を通過した直後の目標空気温度（目標エバ後温度ＴＥＯ）と蒸発器６を通過した直後における実際の空気温度（蒸発温度センサ１７ｂの検出温度）ＴＥとの差Ｅｎ（＝ＴＥＯ−ＴＥ）を所定時間毎（本実施形態では、４秒毎）に算出する。
【００４０】
そして、今回算出したＥｎと前回算出したＥｎ−１との差Ｅｄｏｔ（＝Ｅｎ−Ｅｎ−１）、今回算出したＥｎ、図３に示すメンバシップ関数、及び図４に示すルール表に基づいて、前回決定した圧縮機７の回転数ｆｎ−１に対してどれだけ回転数を増減するか、つまり目標増加回転数Δｆを決定する。
【００４１】
そして、前回決定した圧縮機７の回転数ｆｎ−１に対して目標増加回転数Δｆを加算した回転数を目標回転数ｆｎ（＝ｆｎ−１＋Δｆ）として、その目標回転数ｆｎとなるようにモータ駆動回路を制御する。
【００４２】
次に、本実施形態に係る空調装置の運転モードについて述べる。
【００４３】
１．冷房モード（ＭＡＸＣＯＯＬモード）
この運転モードは、蒸発器６を通過した空気の全量がバイパス通路１３を通過するようにエアミックスドア１４の開度を固定したまま、蒸発器６で発生する冷却能力を調節することにより室内に吹き出す空気の温度を調節するモードである。
【００４４】
具体的には、空調装置の始動スイッチが投入されると同時に、空調センサ群の検出値及び温度コントロールパネル１７ｆに入力された設定値を読み込み、この読み込んだ値から下記の数式１に基づいて車室内に吹き出す空気の目標温度（目標吹出空気温度ＴＡＯ）を決定し、この目標吹出温度ＴＡＯと蒸発器６に流入する空気の温度ＴＩＮとの差（＝ＴＡＯ−ＴＩＮ）が所定値となったときに実行される運転モードである。
【００４５】
そして、冷房モードでは、蒸発器６を通過した空気の全量がバイパス通路１３を通過するようにエアミックスドア１４の開度を固定するので、目標吹出温度ＴＡＯ＝目標エバ後温度ＴＥＯとなる。このため、冷房モードでは、圧縮機７の回転数は直接に目標吹出温度ＴＡＯに連動して制御される。
【００４６】
なお、電気ヒータ１１及びポンプ１１ｂは原則停止させるが、冷房モード以外の運転モードから冷房運転モードに切り替えたときには、エアミックスドア１４の開度ＳＷが０％となるまで、ポンプ１１ｂのみ稼動させる。
【００４７】
そして、目標吹出温度ＴＡＯと蒸発器６に流入する空気の温度ＴＩＮとの差（以下、空調能力指数と呼ぶ。）が下降傾向にあるときは、図５に示すように、空調能力指数が−３以下となったときに冷房モードを行い、空調能力指数が上昇傾向にあるときは空調能力指数が−１以下の間のときに冷房モードを行う。
【００４８】
【数１】
ＴＡＯ＝Ｋｓｅｔ×Ｔｓｅｔ−Ｋｒ×Ｔｒ−Ｋａｍ×Ｔａｍ−Ｋｓ×Ｔｓ＋Ｃ
但し、Ｔｒ：内気温度センサ１７ｃの検出温度
Ｔａｍ：外気温度センサ１７ａの検出温度
Ｔｓ：日射センサ１７ｄの検出値
Ｋｓｅｔ、Ｋｒ、Ｋａｍ、Ｋｓ：制御ゲイン
Ｃ：補正用の定数
なお、本実施形態では蒸発器６に流入する空気の温度ＴＩＮを計測する温度センサを備えていないので、本実施形態では下記数式２にて温度ＴＩＮを検出している。
【００４９】
【数２】
ＴＩＮ＝α×Ｔａｍ＋（１−α）×Ｔｒ
但し、α：空調ケーシング１に導入される空気に示す外気の割合
２．暖房（除湿暖房）モード（ＭＡＸＨＯＴモード）
この運転モードは、空調能力指数上昇傾向にあるときであって、空調能力指数が３以上となったときに、及び空調能力指数が下降傾向にあるときであって、空調能力指数が１以上の間のときに行われるモードである。
【００５０】
具体的には、送風機５から送風された空気の全量がヒータ１２を通過するようにエアミックスドア１４の開度を固定したまま、ヒータ１２で発生する加熱能力を調節することにより室内に吹き出す空気の温度を調節するモードである。
【００５１】
ところで、本モードは、温水温度を調節して室内に吹き出す空気の温度を調節するものであるが、暖房運転を行う外気温度が低い季節では、運転に支障が発生しないように窓ガラスの曇りを防止する必要があるので、本実施形態では、蒸発器６にて室内に吹き出す空気を少なくとも露点温度以下まで冷却して除湿した後、この冷却除湿された空気をヒータ１２にて加熱している。
【００５２】
そして、電気ヒータ１１は、下記の数式３に決定される目標水温ＴＷＯとなるようにその通電量が制御される。
【００５３】
【数３】
ＴＷＯ＝（ＴＡＯ−ＴＥ）／φ＋ＴＥ
但し、ＴＥ：蒸発温度センサ１７ｂの検出値
φ：熱交換効率
因みに、蒸発器６の冷却能力は、図６に示すように、外気温度ＴＡＭによって決定される目標蒸発器後温度ＴＥＯとなるように制御される。
【００５４】
３．エアミックスモード
この運転モードは、空調能力指数上昇傾向にあるときであって、空調能力指数が−１より大きく、かつ、３未満のときに、及び空調能力指数が下降傾向にあるときであって、空調能力指数が１未満、−３より大きいときに行われるモードである。
【００５５】
具体的には、冷風と温風と混合比をエアミックスドア１４にて調節して室内に吹き出す空気の温度を調節するモードで、主に、春や秋等の中間季節及び除湿運転時に行うものである。
【００５６】
そして、上記数式３により決定された水温と所定温度（本実施形態では、５０℃）のうちいずれか大きい方の値を目標水温ＴＷＯとして電気ヒータ１１を制御するとともに、下記数式４に基づいてエアミックスドア１４の開度ＳＷを決定する。
【００５７】
なお、蒸発器６の制御は暖房モードと同じであり、開度ＳＷは、その値が小さくなるほどヒータ１２を通過する風量が低下することを意味する。
【００５８】
【数４】
ＳＷ＝（ＴＡＯ−ＴＥ）／（ＴＷ−ＴＥ）×１００％
但し、ＴＷ：ヒータ１２に流入する実際の温水温度
４．運転モード移行時
４．１過渡期間モード
このモードは、暖房モード又はエアミックスモードから冷房モードに移行したときであって、目標エバ後温度ＴＥＯの上昇率の絶対値が所定値より大きいときに実行されるモードであり、目標エバ後温度ＴＥＯの上昇率の絶対値が所定値より大きくなったときには、目標エバ後温度ＴＥＯの変化率の絶対値が所定値以下のとき、つまり冷房モード、暖房モード及びエアミックスモードのうちいずれかの運転モードのときに比べて、目標増加回転数Δｆ、つまり循環冷媒流量の変化率の絶対値を小さくした状態で圧縮機７の回転数を低下させていく。
【００５９】
そして、圧縮機７の回転数が所定の下限回転数まで低下したときには、さらに回転数を低下させることなくその下限回転数を維持し、目標エバ後温度ＴＥＯが低下して目標増加回転数Δｆがプラスに転じて圧縮機７の回転数を増大させる必要性が発生した時、又は下限回転数を維持してから所定時間が経過した時に、過渡期間モード終了して前述した通常の圧縮機制御を行う。
【００６０】
具体的には、通常の圧縮機制御時において、圧縮機７の回転数を５０ｒｐｍ〜２００ｒｐｍの範囲で変化させていたとすれば、目標エバ後温度ＴＥＯの上昇率の絶対値が所定値より大きくなったときには、圧縮機７の回転数を２００ｒｐｍで減少させていき、回転数が８００ｒｐｍになったときにその回転数を所定時間（例えば、１０秒）維持するものである。
【００６１】
４．２冷房モード以外の運転モードから冷房運転モードに切り替えるとき
冷房モード以外の運転モードから冷房運転モードに切り替えるときには、蒸発器６で冷却された空気の目標温度ＴＥＯと蒸発器６で冷却された空気の実温度ＴＥとの差の絶対値が所定値（本実施形態では、５℃）以下となるまで冷風の風量が徐々に増加するようにエアミックスドア１４の開度ＳＷを徐々に０％まで低下させる。
【００６２】
４．３暖房モード以外の運転モードから暖房運転モードに切り替えるとき
暖房モード以外の運転モードから暖房運転モードに切り替えるときには、ヒータ１２で加熱された空気の目標温度、すなわち目標水温ＴＷＯとヒータ１２で加熱された空気の実温度、すなわち実温水温度ＴＷとの差の絶対値が所定値（本実施形態では、４℃以下）以下となるまで温風の風量が徐々に増加するようにエアミックスドア１４の開度ＳＷを徐々に１００％まで上昇させる。
【００６３】
なお、図７〜１０は上記作動の制御作動（Ｓ１〜Ｓ４３）を示すフローチャートであり、図１１は上記作動をまとめた図表である。
【００６４】
次に、本実施形態の作用効果を述べる。
【００６５】
図１２（ａ）は本実施形態に係る空調装置において、暖房モード又はエアミックスモードから冷房モードに移行したときの目標エバ後温度ＴＥＯ、圧縮機７の回転数ｆｎ及び蒸発器６で冷却された空気の実温度ＴＥの変化を示すグラフであり、図１２（ｂ）は試作検討に係る空調装置において、暖房モード又はエアミックスモードから冷房モードに移行したときの目標エバ後温度ＴＥＯ、圧縮機７の回転数ｆｎ及び蒸発器６で冷却された空気の実温度ＴＥの変化を示すグラフである。
【００６６】
そして、図１２からも明らかなように、本実施形態では、目標エバ後温度ＴＥＯの上昇率の絶対値が所定値より大きくなったときに、目標増加回転数Δｆの変化率の絶対値を小さくして圧縮機７の回転数を低下させていくので、循環冷媒流量が略０となって圧縮機７が停止してしまうことを防止できる。
【００６７】
したがって、暖房モード又はエアミックスモードから冷房モードに移行したときの過渡期間において、湿度が高い冷風が車室内に吹き出されて空調感が悪化してしまう、及び過渡期間が終了して圧縮機を再起動した時に振動や騒音が発生してしまうといった問題が発生してしまうことを防止できる。
【００６８】
また、本実施形態では、過渡期間においては、圧縮機７の回転数を下限回転数未満まで低下させないので、循環冷媒流量が略０となって圧縮機７が停止してしまうことを確実に防止でき、空調感の悪化及び振動や騒音を確実に防止できる。
【００６９】
（第２実施形態）
圧縮機７の回転数は目標エバ後温度ＴＥＯに基づいて制御されることから、本実施形態は、暖房モード又はエアミックスモードから冷房モードに移行して目標エバ後温度ＴＥＯの上昇率の絶対値が所定値より大きくなったときには、図１３に示すように、目標エバ後温度ＴＥＯの変化率の絶対値が所定値以下のとき、つまり冷房モード、暖房モード及びエアミックスモードのうちいずれかの運転モードのときに比べて、目標エバ後温度ＴＥＯの上昇率の絶対値を小さくなるよに目標エバ後温度ＴＥＯを補正するものである。
【００７０】
なお、本実施形態では、目標エバ後温度ＴＥＯの上昇率の絶対値が所定値より大きくなったときには、目標エバ後温度ＴＥＯを約２℃／ｍｉｎで上昇させていき、目標エバ後温度ＴＥＯと補正後の目標エバ後温度ＴＥＯとの差が所定値（例えば、０．５）以下となったときに、過渡期間モードを解除して、通常の圧縮機制御モードに移行する。
【００７１】
因みに、図１４は本実施形態における冷房モード制御作動（Ｓ４４〜Ｓ５２）を示すフローチャートであり、第１実施形態に係るフローチャートのＳ７〜Ｓ２３がＳ４４〜Ｓ５２に変更されたのみで、その他は第１実施形態と同じである。
【００７２】
以上に述べたように、本実施形態においても、循環冷媒流量が略０となって圧縮機７が停止してしまうことを防止できるので、暖房モード又はエアミックスモードから冷房モードに移行したときの過渡期間において、湿度が高い冷風が車室内に吹き出されて空調感が悪化してしまう、及び過渡期間が終了して圧縮機を再起動した時に振動や騒音が発生してしまうといった問題が発生してしまうことを防止できる。
【００７３】
（第３実施形態）
本実施形態は、暖房モード又はエアミックスモードから冷房モードに移行して目標エバ後温度ＴＥＯの上昇率の絶対値が所定値より大きくなったときには、少なくとも冷房モードに移行した時の目標エバ後温度ＴＥＯと冷房モードに移行する直前の目標エバ後温度ＴＥＯとの差に基づいて決定される循環冷媒流量に対応する回転数（以下、過渡期目標回転数と呼ぶ。）となるように圧縮機７の回転数を制御し、その過渡期目標回転数を所定時間保持した後、過渡期間モードを解除して、通常の圧縮機制御モードに移行するものである。
【００７４】
具体的にには、冷房モードに移行した時の目標エバ後温度ＴＥＯと冷房モードに移行する直前の目標エバ後温度ＴＥＯとの差が５℃である場合には、現状の回転数から約３００回転減じた回転数で約２０秒間、圧縮機７を運転した後、過渡期間モードを解除して、通常の圧縮機制御モードに移行する。
【００７５】
これにより、本実施形態においても、循環冷媒流量が略０となって圧縮機７が停止してしまうことを防止できるので、暖房モード又はエアミックスモードから冷房モードに移行したときの過渡期間において、湿度が高い冷風が車室内に吹き出されて空調感が悪化してしまう、及び過渡期間が終了して圧縮機を再起動した時に振動や騒音が発生してしまうといった問題が発生してしまうことを防止できる。
【００７６】
（その他の実施形態）
上述の実施形態では、加熱器として電気ヒータ１１を用いたが、本発明はこれに限定されるものではなく、例えば加熱器として燃焼式ヒータを用いてもよい。
【００７７】
また、上述の実施形態では、加熱器、つまり電気ヒータ１１にて温水を加熱し、この温水を介して室内に吹き出す空気を加熱したが、本発明はこれに限定されるものではなく、加熱器にて直接に室内に吹き出す空気を加熱してもよい。
【００７８】
また、上述の実施形態では、エアミックスドア１４として板ドアを用いたが、本発明はこれに限定されるものではなく、例えば膜状のフィルムドアを用いてよい。
【００７９】
また、上述の実施形態では、車両用に本発明を用いたが、本発明はこれに限定されるものではなく、その他の空調装置にも適用することが可能である。
【００８０】
また、上述の実施形態では、ファジィ理論に基づいて圧縮機７の回転数を制御したが、本発明はこれに限定されるものではない。
【００８１】
また、上述の実施形態では、電動モータにて圧縮機７の回転数を制御することにより循環冷媒流量を制御したが、本発明はこれに限定されるものではなく、例えば可変容量型圧縮機にて吐出容量を制御することにより循環冷媒流量を制御してもよい。
【図面の簡単な説明】
【図１】本発明の第１実施形態に係る空調装置の模式図である。
【図２】本発明の第１実施形態に係る車両用空調装置の電気回路図である。
【図３】本発明の第１実施形態に係る車両用空調装置の制御特性図である。
【図４】本発明の第１実施形態に係る車両用空調装置の制御特性図である。
【図５】本発明の第１実施形態に係る車両用空調装置の制御特性図である。
【図６】本発明の第１実施形態に係る車両用空調装置の制御特性図である。
【図７】本発明の第１実施形態に係る車両用空調装置の制御を示すフローチャートである。
【図８】本発明の第１実施形態に係る車両用空調装置の制御を示すフローチャートである。
【図９】本発明の第１実施形態に係る車両用空調装置の制御を示すフローチャートである。
【図１０】本発明の第１実施形態に係る車両用空調装置の制御を示すフローチャートである。
【図１１】本発明の第１実施形態に係る車両用空調装置の制御を示す図表である。
【図１２】本発明の第１実施形態に係る車両用空調装置の効果を示すグラフである。
【図１３】本発明の第２実施形態に係る車両用空調装置の効果を示すグラフである。
【図１４】本発明の第１実施形態に係る車両用空調装置の制御を示すフローチャートである。
【符号の説明】
１…空調ケーシング、６…蒸発器、７…圧縮機、８…凝縮器、
９…キャピラリーチューブ、１０…アキュムレータ、１１…電気ヒータ、
１２…ヒータ、１４…エアミックスドア。[0001]
TECHNICAL FIELD OF THE INVENTION
TECHNICAL FIELD The present invention relates to an air conditioner using energy other than waste heat such as an electric heater as a heat source for heating air blown into a room, and relates to an electric vehicle using a fuel cell, or an internal combustion engine (engine) and an electric motor. The present invention is effective when applied to an air conditioner for an electric vehicle such as a so-called hybrid vehicle that travels in combination.
[0002]
[Prior art]
BACKGROUND ART As is well known, a vehicle air conditioner having an internal combustion engine (engine) heats air blown into a room using waste heat of the engine as a heat source, and generates air blown into the room by cold generated by a vapor compression refrigerator. The air conditioner comprises a cooler for heating, and an air mix door or the like that adjusts a flow rate of a hot air flowing through the heater to the indoor side and a cool air flowing to the indoor side bypassing the heater. The temperature of the air blown to the heater is adjusted by adjusting the mixing ratio of the cool air and the hot air, that is, the air flow ratio between the air flow flowing through the heater and the air flow bypassing the heater.
[0003]
[Problems to be solved by the invention]
By the way, in an air conditioner for an electric vehicle, it is difficult to use waste heat generated in a vehicle as a heat source of a heater. Therefore, it is necessary to provide a device dedicated to a heat source such as an electric heater or a combustion heater.
[0004]
For this reason, as in the above-described conventional technique, the air flow rate of the hot air flowing through the heater to the indoor side and the cool air flowing to the indoor side bypassing the heater is adjusted to blow out the room. Adjusting the temperature of the air increases the energy consumption of the air conditioner, that is, the power consumption of the electric heater and the vapor compression refrigerator.
[0005]
Then, the inventor adjusts the cooling capacity generated by the cooler to adjust the temperature of the air blown into the room by adjusting the cooling capacity. The air conditioner has at least three operation modes, a dehumidification mode (dehumidification heating mode) for heating air having a temperature lower than the dew point temperature to a predetermined temperature, and an air mix mode for adjusting the temperature of air blown into a room by an air mix door. As a result of studying the prototype of the device, the following problems occurred.
[0006]
That is, in the air mixing mode or the dehumidifying heating mode performed during the dehumidifying operation or the like, since the cool air cooled by the cooler is reheated by the heater, the air temperature immediately after passing through the cooler is actually It becomes lower than the temperature of the air blown into the room.
[0007]
On the other hand, in the cooling mode, the temperature of the air blown into the room is adjusted by adjusting the cooling capacity generated in the cooler by setting the amount of hot air to 0, so that the air temperature immediately after passing through the cooler and the air actually blown into the room Is almost equal to the temperature.
[0008]
The refrigerating capacity generated by the cooler controls the circulating refrigerant flow rate by controlling the number of revolutions of the compressor such that the temperature of the air passing through the cooler becomes a target temperature (target post-evaporation temperature TEO). Therefore, the target post-evaporation temperature TEO in the air mix mode or the dehumidifying heating mode may be lower than the target post-evaporation temperature TEO in the cooling mode.
[0009]
For this reason, when switching from the air mix mode or the dehumidifying heating mode to the cooling mode, the target post-evaporation temperature TEO sharply increases, and the cooling capacity becomes excessive for a predetermined time (transient period) from when the operation mode is switched. Therefore, as shown in FIG. 12B, a state occurs in which the flow rate of the circulating refrigerant becomes substantially zero by stopping the compressor or the like.
[0010]
Therefore, during the transition period in which the circulating refrigerant flow rate becomes substantially zero, the problem is that cold air with high humidity is blown into the vehicle interior and the feeling of air conditioning deteriorates, and the compressor is restarted after the transition period ends. This causes problems such as generation of vibration and noise.
[0011]
In view of the above points, the present invention firstly provides a new air conditioner different from the conventional one, and secondly, prevents the air conditioning feeling from being greatly deteriorated when the operation mode is switched. Aim.
[0012]
[Means for Solving the Problems]
In order to achieve the above object, according to the first aspect of the present invention, a cooler (6) that exchanges heat between air blown into a room and a depressurized refrigerant to cool the air blown into a room, A compressor (7) that absorbs heat from the air blown into the room by the cooler (6) and compresses the evaporated refrigerant and supplies the compressed refrigerant to the radiator (8); and a heater (12) that heats the air blown into the room. Flow rate control means for controlling the flow rate of the circulating refrigerant so that the temperature of the air passing through the cooler (6) becomes the target temperature (TEO). When the value is larger than the predetermined value, the absolute value of the change rate of the circulating refrigerant flow is made smaller than when the absolute value of the change rate of the target temperature (TEO) is equal to or less than the predetermined value.
[0013]
As a result, it is possible to prevent the circulating refrigerant flow rate from becoming substantially zero, so that in the transitional period, cold air having a high humidity is blown into the vehicle interior and the air-conditioning feeling deteriorates, and the transitional period ends and the compression is completed. It is possible to prevent problems such as generation of vibration and noise when the machine is restarted.
[0014]
According to the second aspect of the present invention, a cooler (6) for exchanging heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room, and from the air blown into the room by the cooler (6). A compressor (7) that compresses the refrigerant that has absorbed and evaporated and supplies it to a radiator (8), a heater (12) that heats air blown into the room, and a target air that has passed through the cooler (6). Target temperature determining means for determining the temperature (TEO), flow rate controlling means for controlling the circulating refrigerant flow rate such that the temperature of the air passing through the cooler (6) becomes the target temperature (TEO), and target temperature determining means. When the determined absolute value of the rate of increase of the target temperature (TEO) is larger than a predetermined value, the target temperature is determined to be lower than the absolute value of the change rate of the target temperature (TEO) determined by the target temperature determining means. Reduce the absolute value of the rise rate of (TEO) Characterized in that it comprises a target temperature correction means for.
[0015]
As a result, it is possible to prevent the circulating refrigerant flow rate from becoming substantially zero, so that in the transitional period, cold air having a high humidity is blown into the vehicle interior and the air-conditioning feeling deteriorates, and the transitional period ends and the compression is completed. It is possible to prevent problems such as generation of vibration and noise when the machine is restarted.
[0016]
According to the third aspect of the present invention, the cooler (6) that exchanges heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room, and the air blown into the room by the cooler (6). A compressor (7) that compresses the refrigerant that has absorbed and evaporated and supplies it to a radiator (8), a heater (12) that heats air blown into the room, and a temperature of the air that has passed through the cooler (6). Flow rate control means for controlling the flow rate of the circulating refrigerant so that the temperature of the air reaches the target temperature (TEO), a cooling mode for adjusting the temperature of the air blown into the room by adjusting the cooling capacity generated by the cooler (6), and cooling. Operating mode switching means for switching between a dehumidifying mode in which the air blown into the room is reduced to a dew point temperature or lower by a heater (6) and then a heater (12) heats the air lowered to a dew point temperature or lower to a predetermined temperature. With flow control The step is to reduce the absolute value of the change rate of the circulating refrigerant flow rate for a predetermined time from the time when the mode is switched from the dehumidification mode to the cooling mode, compared to the absolute value of the change rate of the circulating refrigerant flow rate in the dehumidification mode or the cooling mode. It is characterized by.
[0017]
As a result, it is possible to prevent the circulating refrigerant flow rate from becoming substantially zero, so that in the transitional period, cold air having a high humidity is blown into the vehicle interior and the air-conditioning feeling deteriorates, and the transitional period ends and the compression is completed. It is possible to prevent problems such as generation of vibration and noise when the machine is restarted.
[0018]
In the invention described in claim 4, the cooler (6) that exchanges heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room, and from the air blown into the room by the cooler (6). A compressor (7) that compresses the refrigerant that has absorbed and evaporated and supplies it to a radiator (8), a heater (12) that heats air blown into the room, and a target air that has passed through the cooler (6). Target temperature determining means for determining the temperature (TEO); flow rate controlling means for controlling the flow rate of the circulating refrigerant so that the temperature of the air passing through the cooler (6) becomes the target temperature (TEO); In the dehumidification mode or the cooling mode, the absolute value of the rate of change of the target temperature (TEO) is compared with the absolute value of the rate of change of the target temperature (TEO) determined by the target temperature determining means in the dehumidification mode or the cooling mode. Target temperature compensation to decrease Characterized in that it comprises a means.
[0019]
As a result, it is possible to prevent the circulating refrigerant flow rate from becoming substantially zero, so that in the transitional period, cold air having a high humidity is blown into the vehicle interior and the air-conditioning feeling deteriorates, and the transitional period ends and the compression is completed. It is possible to prevent problems such as generation of vibration and noise when the machine is restarted.
[0020]
According to the fifth aspect of the present invention, a cooler (6) for exchanging heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room, and the air blown into the room by the cooler (6). A compressor (7) that compresses the refrigerant that has absorbed and evaporated and supplies it to a radiator (8), a heater (12) that heats air blown into the room, and a temperature of the air that has passed through the cooler (6). And a flow rate control means for controlling the flow rate of the circulating refrigerant so that the target temperature (TEO) is attained. When the absolute value of the rate of increase of the target temperature (TEO) is larger than a predetermined value, the flow rate control means It is characterized in that the flow rate is not reduced below a predetermined flow rate.
[0021]
As a result, it is possible to prevent the circulating refrigerant flow rate from becoming substantially zero, so that in the transitional period, cold air having a high humidity is blown into the vehicle interior and the air-conditioning feeling deteriorates, and the transitional period ends and the compression is completed. It is possible to prevent problems such as generation of vibration and noise when the machine is restarted.
[0022]
According to the invention described in claim 6, the cooler (6) that exchanges heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room, and the air blown into the room by the cooler (6). A compressor (7) that compresses the refrigerant that has absorbed and evaporated and supplies it to a radiator (8), a heater (12) that heats air blown into the room, and a temperature of the air that has passed through the cooler (6). Flow rate control means for controlling the flow rate of the circulating refrigerant so that the temperature of the air reaches the target temperature (TEO), a cooling mode for adjusting the temperature of the air blown into the room by adjusting the cooling capacity generated by the cooler (6), and cooling. Operating mode switching means for switching between a dehumidifying mode in which the air blown into the room is reduced to a dew point temperature or lower by a heater (6) and then a heater (12) heats the air lowered to a dew point temperature or lower to a predetermined temperature. With flow control Stage a predetermined time from when switching to the cooling mode from the dehumidification mode is characterized in that it does not reduce the circulating coolant flow to a predetermined flow rate or less.
[0023]
As a result, it is possible to prevent the circulating refrigerant flow rate from becoming substantially zero, so that in the transitional period, cold air having a high humidity is blown into the vehicle interior and the air-conditioning feeling deteriorates, and the transitional period ends and the compression is completed. It is possible to prevent problems such as generation of vibration and noise when the machine is restarted.
[0024]
Incidentally, reference numerals in parentheses of the above-mentioned units are examples showing the correspondence with specific units described in the embodiments described later.
[0025]
BEST MODE FOR CARRYING OUT THE INVENTION
(1st Embodiment)
In the present embodiment, the air conditioner according to the present invention is applied to an electric vehicle, and FIG. 1 is a schematic diagram of the air conditioner according to the present embodiment.
[0026]
The air-conditioning casing 1 is a duct means forming a flow path of air blown into the room, and an air-inflow port 2 for introducing air inside the vehicle and an outside air for introducing air outside the vehicle interior are provided at an upstream portion of the air-flow of the air-conditioning casing 1. An inlet 3 is formed, and the amount of inside air and the amount of outside air introduced into the air conditioning casing 1 are adjusted by an inside / outside air switching door 4.
[0027]
The blower 5 is a centrifugal fan that blows air into the room, and the evaporator 6 is a cooler that exchanges heat between the air blown from the blower 5 and the refrigerant and evaporates the liquid-phase refrigerant to cool the air. is there.
[0028]
Here, the evaporator 6 is a low-pressure side heat exchanger of the vapor compression refrigerator. As is well known, the vapor compression refrigerator cools the compressor 7 that sucks and compresses the refrigerant and the refrigerant that is discharged from the compressor 7. Radiator 8, a decompressor 9 for decompressing the cooled refrigerant, and a gas-liquid separator 10 for separating the refrigerant flowing out of the evaporator 6 into a gas-phase refrigerant and a liquid-phase refrigerant and storing excess refrigerant as a liquid-phase refrigerant Etc.
[0029]
Incidentally, the compressor 7 according to the present embodiment has a compression mechanism that sucks and compresses refrigerant and an electric motor that drives the compression mechanism integrated. In the present embodiment, the rotation of the compressor 7 (electric motor) is performed. The cooling capacity of the vapor compression refrigerator (evaporator 6) is controlled by controlling the number of circulating refrigerants by fuzzy control of the number.
[0030]
In the present embodiment, a decompression device having a fixed throttle opening such as a capillary tube or a fixed throttle is used as the decompressor 9, and the gas-liquid separator 10 is arranged and separated on the suction side of the compressor 7. The vapor-phase refrigerant flows out to the suction side of the compressor 7.
[0031]
A heater 12 serving as a heater that heats the air that has passed through the evaporator 6 using the hot water heated by the electric heater 11 as a heat source is disposed in the airflow casing 1 on the downstream side of the air flow of the evaporator 6. In addition, a bypass passage 13 that bypasses the heater 12 and allows air to flow downstream is provided.
[0032]
The reserve tank 11a is a tank unit that absorbs fluctuations in the hot water level, and the pump 11b is an electric pump that circulates the hot water.
[0033]
The air mix door 14 is an air mix unit that adjusts the amount of cool air that is cooled by the evaporator 6 and flows through the bypass passage 13 and the amount of air (warm air) that is heated by passing through the heater 12.
[0034]
A face outlet 14 for blowing out conditioned air to the upper body (upper side of the passenger compartment) of the passenger in the passenger compartment is provided at the most downstream portion of the air-conditioning casing 1, and air is discharged to the feet of the passenger in the passenger compartment (lower side of the passenger compartment). Are formed, and a defroster outlet 16 for blowing out air toward the inner surface of the vehicle window glass is formed. Blow-out mode switching doors 14a to 16a for controlling opening and closing of the blow-out ports 14 to 16 are provided.
[0035]
The compressor 7, that is, the electric motor and the electric heater 11 are controlled by an electronic control unit (ECU), and FIG. 2 shows an inverter-type drive circuit for driving the electric motor of the compressor 7 and the electric heater 11. FIG. 3 is an electric circuit diagram for an air conditioner provided with a heater IGBT for controlling the amount of current supplied to the heater and a main relay for shutting off a power supply for preventing an overcurrent from flowing in the electric circuit.
[0036]
The ECU 17 includes an outside air temperature sensor (outside air temperature detecting means) 17a for detecting the temperature of the outdoor air, and an evaporating temperature sensor (evaporating temperature) for detecting the temperature of the air immediately after passing through the evaporator 6, that is, the temperature of the evaporator 6. Device temperature detecting means) 17b, an indoor air temperature sensor (indoor air temperature detecting means) 17c for detecting the temperature of indoor air, a solar radiation sensor (solar radiation detecting means) 17d for detecting the amount of solar radiation poured into the passenger compartment, and the like. A detection value of a group of air conditioning sensors such as a water temperature sensor 17e for detecting the temperature of the hot water heated by the electric heater 11, and a set value input to a temperature control panel 17f for setting and inputting a desired indoor temperature by an occupant are input. I have.
[0037]
Next, a control method of the compressor 7 will be described.
[0038]
The control of the rotation speed of the compressor 7, that is, the flow rate of the circulating refrigerant is controlled based on the fuzzy theory as described above, and the outline thereof is as follows.
[0039]
First, a difference En (= TEO) between the target air temperature (target post-evaporation temperature TEO) immediately after passing through the evaporator 6 and the actual air temperature (detection temperature of the evaporation temperature sensor 17b) TE immediately after passing through the evaporator 6. −TE) is calculated every predetermined time (in this embodiment, every 4 seconds).
[0040]
Then, based on the difference Edot (= En−En−1) between En calculated this time and En−1 calculated last time, En calculated this time, the membership function shown in FIG. 3, and the rule table shown in FIG. How much the rotational speed is increased or decreased with respect to the previously determined rotational speed fn-1 of the compressor 7, that is, the target increase rotational speed Δf is determined.
[0041]
Then, the rotation speed obtained by adding the target increase rotation speed Δf to the rotation speed fn−1 of the compressor 7 previously determined is set as the target rotation speed fn (= fn−1 + Δf), and the motor is set so that the target rotation speed fn is obtained. Control the drive circuit.
[0042]
Next, an operation mode of the air conditioner according to the present embodiment will be described.
[0043]
1. Cooling mode (MAX COOL mode)
In this operation mode, the cooling capacity generated in the evaporator 6 is adjusted while the opening of the air mix door 14 is fixed so that the entire amount of the air that has passed through the evaporator 6 passes through the bypass passage 13. This is a mode for adjusting the temperature of the blown air.
[0044]
Specifically, at the same time when the start switch of the air conditioner is turned on, the detection value of the air conditioning sensor group and the set value input to the temperature control panel 17f are read, and the vehicle is read from the read value based on the following equation 1. The target temperature of the air to be blown into the room (target blow-off air temperature TAO) is determined, and when the difference between the target blow-out temperature TAO and the temperature TIN of the air flowing into the evaporator 6 (= TAO-TIN) becomes a predetermined value. This is the operation mode to be executed.
[0045]
Then, in the cooling mode, the opening degree of the air mix door 14 is fixed so that the entire amount of the air that has passed through the evaporator 6 passes through the bypass passage 13, so that the target outlet temperature TAO = the target post-evaporation temperature TEO. For this reason, in the cooling mode, the rotation speed of the compressor 7 is controlled directly in conjunction with the target outlet temperature TAO.
[0046]
Although the electric heater 11 and the pump 11b are stopped in principle, when the operation mode other than the cooling mode is switched to the cooling operation mode, only the pump 11b is operated until the opening degree SW of the air mix door 14 becomes 0%.
[0047]
When the difference between the target outlet temperature TAO and the temperature TIN of the air flowing into the evaporator 6 (hereinafter, referred to as the air-conditioning capacity index) tends to decrease, as shown in FIG. The cooling mode is performed when the air conditioning capacity index becomes 3 or less, and the cooling mode is performed when the air conditioning capacity index is less than −1 when the air conditioning capacity index is increasing.
[0048]
(Equation 1)
TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × Ts + C
Here, Tr: the detected temperature of the inside air temperature sensor 17c Tam: the detected temperature of the outside air temperature sensor 17a Ts: the detected values Kset, Kr, Kam, and Ks of the solar radiation sensor 17d: control gain C: a constant for correction In this embodiment, Since a temperature sensor for measuring the temperature TIN of the air flowing into the evaporator 6 is not provided, the temperature TIN is detected by the following equation 2 in the present embodiment.
[0049]
(Equation 2)
TIN = α × Tam + (1−α) × Tr
Where α is the ratio of the outside air shown in the air introduced into the air conditioning casing 1. Heating (dehumidification heating) mode (MAX HOT mode)
This operation mode is when the air conditioning capacity index is on the rise, when the air conditioning capacity index is 3 or more, and when the air conditioning capacity index is on the decline, and the air conditioning capacity index is 1 or more. This is the mode that is performed during the interval.
[0050]
Specifically, while the opening degree of the air mix door 14 is fixed so that the entire amount of air blown from the blower 5 passes through the heater 12, the heating capacity generated by the heater 12 is adjusted to blow air into the room. This is a mode for adjusting the temperature of the camera.
[0051]
By the way, in this mode, the temperature of the hot water is adjusted to adjust the temperature of the air blown into the room.However, in the season when the outside air temperature for the heating operation is low, the fogging of the window glass is prevented so as not to hinder the operation. Therefore, in the present embodiment, the air blown into the room by the evaporator 6 is cooled to at least the dew point temperature and dehumidified, and the cooled and dehumidified air is heated by the heater 12.
[0052]
The amount of power supplied to the electric heater 11 is controlled so that the target water temperature TWO is determined by the following equation (3).
[0053]
[Equation 3]
TWO = (TAO-TE) / φ + TE
However, TE: the detection value of the evaporation temperature sensor 17b φ: heat exchange efficiency In consideration of the above, the cooling capacity of the evaporator 6 is set to the target post-evaporator temperature TEO determined by the outside air temperature TAM as shown in FIG. Controlled.
[0054]
3. Air mix mode This operation mode is used when the air conditioning capacity index is on the rise, when the air conditioning capacity index is greater than −1 and less than 3, and when the air conditioning capacity index is on the decrease. This mode is performed when the air conditioning capacity index is less than 1 and greater than -3.
[0055]
Specifically, a mode in which the mixing ratio of cold air and hot air is adjusted by the air mixing door 14 to adjust the temperature of the air blown into the room, and is mainly performed during the middle season such as spring or autumn and during the dehumidifying operation. It is.
[0056]
Then, the electric heater 11 is controlled using the larger of the water temperature determined by the above equation 3 and the predetermined temperature (50 ° C. in the present embodiment) as the target water temperature TWO, and the air temperature is calculated based on the following equation 4 The opening degree SW of the mix door 14 is determined.
[0057]
The control of the evaporator 6 is the same as in the heating mode, and the smaller the value of the opening degree SW, the lower the amount of air passing through the heater 12.
[0058]
(Equation 4)
SW = (TAO-TE) / (TW-TE) × 100%
TW: actual temperature of hot water flowing into heater 12 At the time of transition to the operation mode 4.1 Transient period mode This mode is executed when the mode is shifted from the heating mode or the air mix mode to the cooling mode, and the absolute value of the rate of increase of the target post-evaporation temperature TEO is larger than a predetermined value. When the absolute value of the rate of increase of the target post-evaporation temperature TEO is greater than a predetermined value, the absolute value of the rate of change of the target post-evaporation temperature TEO is equal to or lower than a predetermined value, that is, in the cooling mode and the heating mode. And the rotational speed of the compressor 7 is reduced in a state in which the target increased rotational speed Δf, that is, the absolute value of the rate of change of the circulating refrigerant flow rate, is smaller than in any one of the operation modes of the air mix mode.
[0059]
Then, when the rotation speed of the compressor 7 has decreased to the predetermined lower limit rotation speed, the lower limit rotation speed is maintained without further lowering the rotation speed, and the target post-evaporation temperature TEO decreases to reduce the target increase rotation speed Δf. When it becomes necessary to increase the rotation speed of the compressor 7 by turning to plus, or when a predetermined time has elapsed after maintaining the lower limit rotation speed, the transient period mode is terminated and the normal compressor control described above is performed. Do.
[0060]
Specifically, if the rotation speed of the compressor 7 is changed in the range of 50 rpm to 200 rpm during normal compressor control, the absolute value of the rate of increase of the target post-evaporation temperature TEO becomes larger than a predetermined value. In this case, the rotation speed of the compressor 7 is reduced at 200 rpm, and when the rotation speed reaches 800 rpm, the rotation speed is maintained for a predetermined time (for example, 10 seconds).
[0061]
4.2 Switching from operation mode other than cooling mode to cooling operation mode When switching from operation mode other than cooling mode to cooling operation mode, target temperature TEO of air cooled by evaporator 6 and cooling by evaporator 6 The opening degree SW of the air mix door 14 is gradually reduced to 0% so that the flow rate of the cool air gradually increases until the absolute value of the difference from the actual temperature TE of the air becomes equal to or less than a predetermined value (5 ° C. in the present embodiment). To lower.
[0062]
4.3 When switching from operation mode other than heating mode to heating operation mode When switching from operation mode other than heating mode to heating operation mode, target temperature of air heated by heater 12, that is, target water temperature TWO and heating by heater 12 The air mixing door 14 is configured to gradually increase the flow rate of the hot air until the absolute value of the difference between the measured actual temperature of the air, that is, the actual hot water temperature TW, becomes equal to or less than a predetermined value (4 ° C. or less in the present embodiment). Is gradually increased to 100%.
[0063]
7 to 10 are flowcharts showing the control operations (S1 to S43) of the above operations, and FIG. 11 is a table summarizing the above operations.
[0064]
Next, the operation and effect of the present embodiment will be described.
[0065]
FIG. 12A shows the air conditioner according to the present embodiment, in which the target post-evaporation temperature TEO, the rotational speed fn of the compressor 7 and the evaporator 6 are cooled when the mode is shifted from the heating mode or the air mix mode to the cooling mode. FIG. 12B is a graph showing a change in the actual temperature TE of the air. FIG. 12B shows the target post-evaporation temperature TEO when the air conditioner shifts from the heating mode or the air mix mode to the cooling mode, and the compressor 7. 4 is a graph showing changes in the rotation speed fn and the actual temperature TE of the air cooled by the evaporator 6.
[0066]
As is apparent from FIG. 12, in the present embodiment, when the absolute value of the rate of increase of the target post-evaporation temperature TEO becomes larger than a predetermined value, the absolute value of the rate of change of the target increased rotational speed Δf is reduced. As a result, the rotation speed of the compressor 7 is reduced, so that it is possible to prevent the circulating refrigerant flow from becoming substantially zero and stopping the compressor 7.
[0067]
Therefore, in the transitional period when the mode is shifted from the heating mode or the air mix mode to the cooling mode, cool air with high humidity is blown into the vehicle interior to deteriorate the air conditioning feeling, and the compressor is restarted after the transitional period ends. It is possible to prevent a problem such as generation of vibration or noise when starting up.
[0068]
Further, in the present embodiment, the rotational speed of the compressor 7 is not reduced to less than the lower limit rotational speed during the transition period, so that the compressor 7 is reliably prevented from being stopped due to the circulating refrigerant flow rate becoming substantially zero. It is possible to surely prevent deterioration of the air conditioning feeling and vibration and noise.
[0069]
(2nd Embodiment)
Since the rotation speed of the compressor 7 is controlled based on the target post-evaporation temperature TEO, the present embodiment shifts from the heating mode or the air mix mode to the cooling mode, and the absolute value of the rate of increase of the target post-evaporation temperature TEO Is larger than a predetermined value, as shown in FIG. 13, when the absolute value of the rate of change of the target post-evaporation temperature TEO is equal to or less than a predetermined value, that is, when one of the cooling mode, the heating mode, and the air mix mode is operated. The target post-evaporation temperature TEO is corrected so that the absolute value of the rate of increase of the target post-evaporation temperature TEO becomes smaller than in the mode.
[0070]
In the present embodiment, when the absolute value of the rate of increase of the target post-evaporation temperature TEO becomes larger than a predetermined value, the target post-evaporation temperature TEO is increased at approximately 2 ° C./min. When the difference from the corrected target post-evaporation temperature TEO becomes equal to or less than a predetermined value (for example, 0.5), the transient period mode is canceled and the mode shifts to the normal compressor control mode.
[0071]
Incidentally, FIG. 14 is a flowchart showing the cooling mode control operation (S44 to S52) in the present embodiment. In the flowchart according to the first embodiment, only S7 to S23 are changed to S44 to S52. This is the same as the embodiment.
[0072]
As described above, also in the present embodiment, it is possible to prevent the compressor 7 from stopping due to the circulating refrigerant flow rate becoming substantially zero, so that when the mode is shifted from the heating mode or the air mix mode to the cooling mode. During the transition period, there is a problem that the cold air with high humidity is blown into the passenger compartment and the feeling of air conditioning is deteriorated, and vibration and noise are generated when the compressor is restarted after the transition period ends. Can be prevented.
[0073]
(Third embodiment)
In the present embodiment, when the mode is shifted from the heating mode or the air mix mode to the cooling mode and the absolute value of the rate of increase of the target post-evaporation temperature TEO becomes larger than a predetermined value, at least the target post-evaporation temperature at the time of shifting to the cooling mode. The compressor 7 has a rotation speed (hereinafter, referred to as a transitional period target rotation speed) corresponding to the circulating refrigerant flow rate determined based on the difference between TEO and the target post-evaporation temperature TEO immediately before shifting to the cooling mode. After the target rotation speed in the transition period is maintained for a predetermined time, the transition period mode is released, and the process shifts to the normal compressor control mode.
[0074]
Specifically, when the difference between the target post-evaporation temperature TEO at the time of transition to the cooling mode and the target post-evaporation temperature TEO immediately before transition to the cooling mode is 5 ° C., about 300 After the compressor 7 has been operated at the reduced rotation speed for about 20 seconds, the transition period mode is released, and a transition is made to the normal compressor control mode.
[0075]
Thereby, also in the present embodiment, it is possible to prevent the circulating refrigerant flow rate from becoming substantially zero and the compressor 7 from stopping, so that in the transition period when the mode is shifted from the heating mode or the air mix mode to the cooling mode, The problem is that cold air with high humidity is blown into the passenger compartment and the feeling of air conditioning deteriorates, and problems such as vibration and noise occurring when the compressor is restarted after the transition period ends. Can be prevented.
[0076]
(Other embodiments)
In the above embodiment, the electric heater 11 is used as the heater, but the present invention is not limited to this. For example, a combustion heater may be used as the heater.
[0077]
In the above-described embodiment, the heater, that is, the hot water is heated by the electric heater 11, and the air blown into the room is heated through the hot water. However, the present invention is not limited to this. May directly heat the air blown into the room.
[0078]
Further, in the above-described embodiment, a plate door is used as the air mix door 14, but the present invention is not limited to this, and for example, a film-like film door may be used.
[0079]
Further, in the above embodiment, the present invention is used for a vehicle, but the present invention is not limited to this, and can be applied to other air conditioners.
[0080]
Further, in the above-described embodiment, the rotation speed of the compressor 7 is controlled based on fuzzy logic, but the present invention is not limited to this.
[0081]
In the above-described embodiment, the circulating refrigerant flow rate is controlled by controlling the number of revolutions of the compressor 7 with the electric motor. However, the present invention is not limited to this. The circulating refrigerant flow rate may be controlled by controlling the discharge capacity.
[Brief description of the drawings]
FIG. 1 is a schematic diagram of an air conditioner according to a first embodiment of the present invention.
FIG. 2 is an electric circuit diagram of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 3 is a control characteristic diagram of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 4 is a control characteristic diagram of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 5 is a control characteristic diagram of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 6 is a control characteristic diagram of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 7 is a flowchart illustrating control of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 8 is a flowchart illustrating control of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 9 is a flowchart showing control of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 10 is a flowchart illustrating control of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 11 is a chart showing control of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 12 is a graph showing an effect of the vehicle air conditioner according to the first embodiment of the present invention.
FIG. 13 is a graph showing an effect of the vehicle air conditioner according to the second embodiment of the present invention.
FIG. 14 is a flowchart illustrating control of the vehicle air conditioner according to the first embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Air-conditioning casing, 6 ... Evaporator, 7 ... Compressor, 8 ... Condenser,
9: capillary tube, 10: accumulator, 11: electric heater,
12 ... heater, 14 ... air mix door.

Claims

A cooler (6) for exchanging heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room;
A compressor (7) that absorbs heat from air blown into the room by the cooler (6) and compresses the evaporated refrigerant to supply the compressed refrigerant to a radiator (8);
A heater (12) for heating the air blown into the room,
Flow rate control means for controlling the circulating refrigerant flow rate so that the temperature of the air passing through the cooler (6) becomes a target temperature (TEO);
When the absolute value of the rate of increase in the target temperature (TEO) is greater than a predetermined value, the flow rate control means may determine whether the flow rate of the circulating refrigerant is greater than when the absolute value of the rate of change in the target temperature (TEO) is equal to or less than a predetermined value. An air conditioner characterized by reducing the absolute value of the change rate of the air conditioner.

A cooler (6) for exchanging heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room;
A compressor (7) that absorbs heat from air blown into the room by the cooler (6) and compresses the evaporated refrigerant to supply the compressed refrigerant to a radiator (8);
A heater (12) for heating the air blown into the room,
Target temperature determining means for determining a target temperature (TEO) of the air having passed through the cooler (6);
Flow rate control means for controlling a circulating refrigerant flow rate such that the temperature of the air passing through the cooler (6) becomes the target temperature (TEO);
When the absolute value of the rate of increase of the target temperature (TEO) determined by the target temperature determining means is larger than a predetermined value, the absolute value of the rate of change of the target temperature (TEO) determined by the target temperature determining means becomes a predetermined value. An air conditioner comprising: target temperature correction means for reducing the absolute value of the rate of increase of the target temperature (TEO) as compared with the following cases.

A cooler (6) for exchanging heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room;
A compressor (7) that absorbs heat from the air blown into the room by the cooler (6) and compresses the evaporated refrigerant to supply the compressed refrigerant to a radiator (8);
A heater (12) for heating the air blown into the room,
Flow rate control means for controlling the circulating refrigerant flow rate so that the temperature of the air passing through the cooler (6) becomes a target temperature (TEO);
A cooling mode in which the temperature of the air blown into the room is adjusted by adjusting the cooling capacity generated in the cooler (6), and after the air blown into the room in the cooler (6) is reduced to a dew point temperature or lower. Operating mode switching means for switching between a dehumidification mode in which the air lowered to a dew point temperature or lower by the heater (12) is heated to a predetermined temperature,
The flow rate control unit is configured such that, for a predetermined time from when the mode is switched from the dehumidification mode to the cooling mode, the change rate of the circulating refrigerant flow rate is compared with the absolute value of the circulating refrigerant flow rate in the dehumidification mode or the cooling mode. An air conditioner characterized by reducing the absolute value of.

A cooler (6) for exchanging heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room;
A compressor (7) that absorbs heat from the air blown into the room by the cooler (6) and compresses the evaporated refrigerant to supply the compressed refrigerant to a radiator (8);
A heater (12) for heating the air blown into the room,
Target temperature determining means for determining a target temperature (TEO) of the air having passed through the cooler (6);
Flow rate control means for controlling a circulating refrigerant flow rate such that the temperature of the air passing through the cooler (6) becomes the target temperature (TEO);
A cooling mode in which the temperature of the air blown into the room is adjusted by adjusting the cooling capacity generated in the cooler (6), and after the air blown into the room in the cooler (6) is reduced to a dew point temperature or lower. Operating mode switching means for switching between a dehumidification mode in which air having a temperature lower than the dew point temperature is lowered to a predetermined temperature in the heater (12), and
At a predetermined time after switching from the dehumidification mode to the cooling mode, compared to the absolute value of the rate of change of the target temperature (TEO) determined by the target temperature determination means in the dehumidification mode or the cooling mode, An air conditioner comprising: target temperature correction means for reducing an absolute value of a change rate of a target temperature (TEO).

A cooler (6) for exchanging heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room;
A compressor (7) that absorbs heat from air blown into the room by the cooler (6) and compresses the evaporated refrigerant to supply the compressed refrigerant to a radiator (8);
A heater (12) for heating the air blown into the room,
Flow rate control means for controlling the circulating refrigerant flow rate so that the temperature of the air passing through the cooler (6) becomes a target temperature (TEO);
The air conditioner according to claim 1, wherein the flow rate control means does not reduce the circulating refrigerant flow rate to a predetermined flow rate or less when an absolute value of the rate of increase of the target temperature (TEO) is larger than a predetermined value.

A cooler (6) for exchanging heat between the air blown into the room and the depressurized refrigerant to cool the air blown into the room;
A compressor (7) that absorbs heat from air blown into the room by the cooler (6) and compresses the evaporated refrigerant to supply the compressed refrigerant to a radiator (8);
A heater (12) for heating the air blown into the room,
Flow rate control means for controlling the circulating refrigerant flow rate so that the temperature of the air passing through the cooler (6) becomes a target temperature (TEO);
A cooling mode in which the temperature of the air blown into the room is adjusted by adjusting the cooling capacity generated in the cooler (6), and after the air blown into the room in the cooler (6) is reduced to a dew point temperature or lower. Operating mode switching means for switching between a dehumidification mode in which the air lowered to a dew point temperature or lower by the heater (12) is heated to a predetermined temperature,
The air conditioner according to claim 1, wherein the flow control unit does not reduce the circulating refrigerant flow rate to a predetermined flow rate or less for a predetermined time after switching from the dehumidification mode to the cooling mode.