JP4089063B2

JP4089063B2 - Capacity control method and apparatus for variable capacity compressor

Info

Publication number: JP4089063B2
Application number: JP02378099A
Authority: JP
Inventors: 哲彦深沼; 真広川口
Original assignee: Toyota Industries Corp
Current assignee: Toyota Industries Corp
Priority date: 1999-02-01
Filing date: 1999-02-01
Publication date: 2008-05-21
Anticipated expiration: 2019-02-01
Also published as: JP2000220577A

Description

【０００１】
【発明の属する技術分野】
本発明は、可変容量型圧縮機における容量制御方法及び装置に関するものである。
【０００２】
【従来の技術】
特開平８−３３８３６４号公報に開示される可変容量型圧縮機では、クランク室の圧力と吸入圧領域の吸入圧との差圧に基づいて吐出容量を変えるようになっている。クランク室の圧力は、吐出圧領域である吐出室からクランク室へ冷媒を供給すると共に、クランク室から吸入圧領域である吸入室へ冷媒を抜き出して調整される。吐出室からクランク室へ冷媒を供給するための圧力供給通路上には容量制御用の電磁弁が介在されている。電磁弁の弁体は、ソレノイドの励磁によって閉弁位置側へ付勢される。電磁弁に対する供給電流値は、予め設定された設定室温と検出された検出室温との比較に基づいて決定されるようになっている。設定室温と検出室温との差が大きいほど供給電流値が大きくされ、電磁弁における弁開度が小さくなる。弁開度が小さくなるほど斜板傾角が大きくなり、吐出容量が大きくなる。弁体が閉弁位置に配置されると圧力供給通路が閉じられ、吐出室からクランク室への冷媒供給が停止する。そのため、斜板の傾角が最大傾角となる。ソレノイドが消磁されると弁体が弁開度最大位置の側へ移行し、吐出室からクランク室への冷媒供給が増える。そのため、クランク室内の圧力が増大し、斜板の傾角が最小になる。斜板の最小傾角状態では斜板の傾動に連動する遮断体が吸入通路を閉じ、外部冷媒回路における冷媒循環が停止する。この冷媒循環停止状態は熱負荷低減作用のない状態である。
【０００３】
【発明が解決しようとする課題】
通常、空調装置作動スイッチをＯＮしたときには設定室温と検出室温との差が大きく、電磁弁に対する供給電流値は空調装置作動スイッチのＯＮ時から大きな値となる。そのため、斜板傾角が最小傾角から急激に増大し、斜板が選択された供給電流値に対応した斜板傾角位置を通り越して最大傾角位置まで迅速に移行してしまう場合がある。このような通り越しは、斜板の最大傾角を規定する部材と斜板との衝突をもたらし、衝突音が発生する。又、設定室温と検出室温との差が大きい状態のときに空調装置作動スイッチをＯＦＦすると、電磁弁に対する供給電流値が大きな値から零へ瞬間的に切り換わる。そのため、斜板傾角が大きな傾角から急激に減少し、斜板が最小傾角位置まで迅速に移行する。このような迅速な移行は斜板の最小傾角を規定する部材と斜板との衝突をもたらし、衝突音が発生する。
【０００４】
本発明は、容量制御弁に対する電流供給開始時あるいは電流供給停止時の前記ような衝突音の発生を防止することを目的とする。
【０００５】
【課題を解決するための手段】
そのために本発明は、回転軸と一体的に回転するように、かつ前記回転軸に対して傾角可変に制御圧室に収容された斜板、及び前記斜板の傾角に応じた往復動作を行なうピストンを備え、吐出圧領域から前記制御圧室へ冷媒を供給すると共に、前記制御圧室から吸入圧領域へ冷媒を抜き出し、前記吐出圧領域から前記制御圧室に至る冷媒供給通路上又は前記制御圧室から前記吸入圧領域に至る冷媒抜き出し通路上に電気式容量制御弁を介在し、前記電気式容量制御弁に対する供給電流値（単位時間当たり）を制御して前記吐出圧領域から前記制御圧室への冷媒供給量又は前記制御圧室から前記吸入圧領域への冷媒抜き出し量を制御し、前記制御圧室内の圧力の制御に基づいて前記斜板の傾角を制御する可変容量型圧縮機を対象とし、請求項１の発明では、前記電気式容量制御弁に対する電流供給を開始するときには、指定された供給電流値を供給開始するまでの過程として前記斜板の最大傾角位置での傾角増大速度を抑制するための緩衝用電流供給開始制御を行なうようにした。
【０００６】
また、前記緩衝用電流供給開始制御は、供給電流値零から指定された指定供給電流値まで供給電流値を増大するようにした。
【０００７】
さらに、前記緩衝用電流供給開始制御は、供給電流値零から前記指定供給電流値に達しない増大飛躍限界供給電流値へ供給電流値を不連続的に切り換える供給電流値切り換え状態と、前記増大飛躍限界供給電流値から前記指定供給電流値まで供給電流値を徐々に増大する電流増大供給状態とを含むようにした。
【０００８】
請求項２の発明では、前記電気式容量制御弁に対する電流供給を停止するときには、供給電流値を零とするまでの過程として前記斜板の最小傾角位置での傾角減少速度を抑制するための緩衝用電流供給停止制御を行なうようにした。
【０００９】
また、前記緩衝用電流供給停止制御は、指定された指定供給電流値から供給電流値零まで供給電流値を減少するようにした。
【００１０】
さらに、前記緩衝用電流供給停止制御は、前記指定供給電流値から前記指定供給電流値に達しない減少飛躍限界供給電流値へ供給電流値を不連続的に切り換える供給電流値切り換え状態と、前記減少飛躍限界供給電流値から供給電流値零まで供給電流値を徐々に減少する電流減少供給状態とを含むようにした。
【００１１】
請求項３の発明では、前記電気式容量制御弁に対する電流供給の開始を指令する電流供給開始指令手段と、前記斜板の最大傾角位置での傾角増大速度を抑制するための緩衝用電流供給開始制御を行なう緩衝用電流供給開始制御手段と、供給電流値を指定する供給電流値指定手段と、前記指定供給電流値に達しない増大飛躍限界供給電流値を指定する増大飛躍限界供給電流値指定手段とを備えた容量制御装置を構成し、前記緩衝用電流供給開始制御手段は、前記電流供給開始指令手段の電流供給開始指令に基づいて前記緩衝用電流供給開始制御を行なうようにした。
【００１２】
また、前記緩衝用電流供給開始制御手段は、前記供給電流値指定手段によって指定された指定供給電流値まで供給電流値零から供給電流値を増大するようにした。
【００１３】
さらに、前記緩衝用電流供給開始制御手段は、供給電流値零から前記指定供給電流値に達しない増大飛躍限界供給電流値へ供給電流値を不連続的に切り換え、前記増大飛躍限界供給電流値から前記指定供給電流値まで供給電流値を徐々に増大する電流供給開始制御を行なうようにした。
請求項４の発明では、前記電気式容量制御弁に対する電流供給の停止を指令する電流供給停止指令手段と、前記斜板の最小傾角位置での傾角減少速度を抑制するための緩衝用電流供給停止制御を行なう緩衝用電流供給停止制御手段と、供給電流値を指定する供給電流値指定手段と、減少飛躍限界供給電流値を指定する減少飛躍限界供給電流値指定手段とを備えた容量制御装置を構成し、前記緩衝用電流供給停止制御手段は、前記電流供給停止指令手段の電流供給停止指令に基づいて前記緩衝用電流供給停止制御を行なうようにした。
【００１４】
また、前記緩衝用電流供給停止制御手段は、前記供給電流値指定手段によって指定された指定供給電流値から供給電流値零まで供給電流値を減少するようにした。
【００１５】
さらに、前記緩衝用電流供給停止制御手段は、前記指定供給電流値から前記指定供給電流値に達しない減少飛躍限界供給電流値へ供給電流値を不連続的に切り換え、前記減少飛躍限界供給電流値から供給電流値零まで供給電流値を徐々に減少する電流供給停止制御を行なうようにした。
【００１６】
請求項１及び請求項３の発明では、電気式容量制御弁に対する電流供給が開始されるときには緩衝用電流供給開始制御が行なわれ、斜板傾角の急激な増大が抑制される。緩衝用電流供給開始制御による斜板傾角の急激な増大の抑制は、斜板の最大傾角位置への不要な到達の回避、あるいは斜板が最大傾角位置へ到達したときの傾角増大速度の抑制をもたらす。
【００１７】
また、供給電流値零から指定された供給電流値まで供給電流値を増大する電流増大供給が行われる。
【００１８】
さらに、供給電流値が零から前記指定供給電流値に達しない増大飛躍限界供給電流値へ不連続的に切り換えられた後、増大飛躍限界供給電流値から前記指定供給電流値まで供給電流値を徐々に増大する電流増大供給が行われる。供給電流値を徐々に増大する電流増大供給状態を含む電流供給状態は、斜板傾角の急激な増大を抑制する。供給電流値零から増大飛躍限界供給電流値への供給電流値の不連続的な切り換えは、吐出容量の速やかな増大に寄与する。
【００１９】
請求項２及び請求項４の発明では、電気式容量制御弁に対する電流供給が停止されるときには緩衝用電流供給停止制御が行なわれ、斜板傾角の急激な減少が抑制される。緩衝用電流供給停止制御による斜板傾角の急激な減少の抑制は、斜板が最小傾角位置へ到達したときの傾角減少速度の抑制をもたらす。
【００２０】
また、指定された供給電流値から供給電流値零まで供給電流値を減少する電流減少供給が行われる。
【００２１】
さらに、供給電流値が指定供給電流値から減少飛躍限界供給電流値へ不連続的に切り換えられた後、減少飛躍限界供給電流値から供給電流値零まで供給電流値を徐々に減少する電流減少供給が行われる。供給電流値を徐々に減少する電流減少供給状態を含む電流供給状態は、斜板傾角の急激な減少を抑制する。指定供給電流値から増大飛躍限界供給電流値への不連続的な切り換えは、吐出容量の速やかな減少に寄与する。
【００２２】
【発明の実施の形態】
以下、車両に搭載したクラッチレス可変容量型圧縮機に本発明を具体化した第１の実施の形態を図１〜図６に基づいて説明する。
【００２３】
図１に示すように、シリンダブロック１１の前端にはフロントハウジング１２が接合されている。シリンダブロック１１の後端にはリヤハウジング１３がバルブプレート１４、弁形成プレート１５，１６及びリテーナ形成プレート１７を介して接合固定されている。制御圧室１２１を形成するフロントハウジング１２とシリンダブロック１１との間に架設支持された回転軸１８は、車両エンジン（図示略）から回転駆動力を得る。
【００２４】
回転軸１８には斜板２０が回転軸１８の軸線方向へスライド可能かつ傾動可能に支持されている。図４に示すように、斜板２０に止着されたガイドピン２３，２４の頭部は、回転軸１８に止着された回転支持体１９のガイド孔１９１，１９２にスライド可能に嵌入されている。斜板２０は、ガイド孔１９１，１９２とガイドピン２３，２４との連係により回転軸１８の軸線方向へ傾動可能かつ回転軸１８と一体的に回転可能である。斜板２０の半径中心部がシリンダブロック１１側へ移動すると、斜板２０の傾角が減少する。回転支持体１９と斜板２０との間に介在された傾角減少ばね２５は斜板２０の傾角を減少する方向へ斜板２０を付勢する。
【００２５】
図１及び図３に示すように、シリンダブロック１１の中心部に貫設された収容孔２１内には筒状の遮断体２２がスライド可能に収容されている。遮断体２２と収容孔２１の端面との間に介在された吸入通路開放ばね２６は、遮断体２２を斜板２０側へ付勢している。回転軸１８の後端部はラジアルベアリング２７及び遮断体２２を介して収容孔２１の周面で支持される。リヤハウジング１３の中心部に形成された吸入通路３１は収容孔２１に接続している。遮断体２２の先端面が弁形成プレート１５に当接することにより遮断体２２が斜板２０から離間する方向への移動を規制される。斜板２０が遮断体２２側へ移動するに伴い、斜板２０の傾動がスラストベアリング３７を介して遮断体２２に伝達する。斜板２０の回転はスラストベアリング３７の存在によって遮断体２２への伝達を阻止される。この傾動伝達により遮断体２２が吸入通路開放ばね２６のばね力に抗して弁形成プレート１５側へ移動し、図３に示すように、遮断体２２が弁形成プレート１５に当接する。斜板２０の最小傾角は遮断体２２と弁形成プレート１５との当接によって規定される。図３は斜板２０の最小傾角状態を示す。図１は斜板２０の最大傾角状態を示す。斜板２０の最大傾角は斜板２０と回転支持体１９との当接により規定される。
【００２６】
シリンダブロック１１に貫設されたシリンダボア１１１内にはピストン２８が収容されている。斜板２０の回転運動はシュー２９を介してピストン２８の前後往復運動に変換され、ピストン２８がシリンダボア１１１内を前後動する。
【００２７】
図５に示すように、リヤハウジング１３内には吸入圧領域となる吸入室１３１の及びその周囲に吐出圧領域となる吐出室１３２が区画形成されている。バルブプレート１４には吸入ポート１４１及び吐出ポート１４２が形成されている。弁形成プレート１５上には吸入弁１５１が形成されており、弁形成プレート１６上には吐出弁１６１が形成されている。吸入室１３１内の冷媒はピストン２８の復動動作により吸入ポート１４１から吸入弁１５１を押し退けてシリンダボア１１１内へ流入する。シリンダボア１１１内へ流入した冷媒はピストン２８の往動動作により吐出ポート１４２から吐出弁１６１を押し退けて吐出室１３２へ吐出される。吐出弁１６１はリテーナ形成プレート１７上のリテーナ１７１に当接して開度規制される。
【００２８】
回転支持体１９とフロントハウジング１２との間に介在されたスラストベアリング３２は、シリンダボア１１１からピストン２８、シュー２９、斜板２０及びガイドピン２３，２４を介して回転支持体１９に作用する圧縮反力を受け止める。
【００２９】
回転軸１８内の通路５０は制御圧室１２１と遮断体２２の筒内とを連通している。図３に示すように、遮断体２２の周面に貫設された放圧通口２２１は遮断体２２の筒内と収容孔２１とを連通している。
【００３０】
吸入室１３１は通口１４３を介して収容孔２１に連通している。遮断体２２が弁形成プレート１５に当接すると、通口１４３は吸入通路３１から遮断される。吸入室１３１へ冷媒を導入する吸入通路３１と吐出室１３２とは外部冷媒回路３３で接続されている。外部冷媒回路３３上には凝縮器３４、膨張弁３５及び蒸発器３６が介在されている。膨張弁３５は蒸発器３６の出口側のガス温度の変動に応じて冷媒流量を制御する。
【００３１】
吐出室１３２と制御圧室１２１とを接続する冷媒供給通路３８上には図２に示す電気式容量制御弁３９が介在されている。冷媒供給通路３８は吐出圧領域である吐出室１３２の冷媒を制御圧室１２１へ供給する通路である。容量制御弁３９内の感圧手段４７を構成するベローズ４０には吸入室１３１内の圧力（吸入圧）が作用している。吸入室１３１内の吸入圧は熱負荷を反映している。ベローズ４０には弁体４１が接続されており、弁体４１は弁孔４２を開閉する。ベローズ４０内の大気圧及び感圧手段４７を構成する感圧ばね４０１のばね力は、弁孔４２を開く方向へ弁体４１に作用する。容量制御弁３９のソレノイド４３を構成する固定鉄芯４３１は、コイル４３２への電流供給による励磁に基づいて可動鉄芯４３３を引き付ける。即ち、ソレノイド４３の電磁駆動力は、開放付勢ばね４８のばね力に抗して弁孔４２を閉じる方向へ弁体４１を付勢する。追従ばね４９は可動鉄芯４３３を固定鉄芯４３１側へ付勢する。ソレノイド４３は制御コンピュータＣ１の電流供給制御を受ける。
【００３２】
制御コンピュータＣ１は、空調装置作動スイッチ４４のＯＮによってソレノイド４３に電流を供給し、空調装置作動スイッチ４４のＯＦＦによって電流供給を停止する。制御コンピュータＣ１には室温設定器４５及び室温検出器４６が信号接続されている。制御コンピュータＣ１は、室温設定器４５によって設定された目標室温情報及び室温検出器４６によって検出された検出室温情報に基づいてソレノイド４３に対する供給電流値を制御する。弁孔４２における開閉具合、即ち弁開度は、ソレノイド４３で生じる電磁駆動力、追従ばね４９のばね力、開放付勢ばね４８のばね力、感圧手段４７の付勢力のバランスによって決まり、容量制御弁３９は、ソレノイド４３に供給される電流値に応じた吸入圧をもたらす制御を行なう。
【００３３】
供給電流値が高められると弁開度が減少し、吐出室１３２から制御圧室１２１への冷媒供給量が減る。制御圧室１２１内の冷媒は、通路５０、放圧通口２２１及び通口１４３という冷媒抜き出し通路を介して吸入室１３１へ流出しているため、制御圧室１２１内の圧力が下がる。従って、斜板２０の傾角が増大して吐出容量が増える。吐出容量の増大は吸入圧の低下をもたらす。供給電流値が下げられると弁開度が増大し、吐出室１３２から制御圧室１２１への冷媒供給量が増える。従って、制御圧室１２１内の圧力が上がり、斜板２０の傾角が減少して吐出容量が減る。吐出容量の減少は吸入圧の増大をもたらす。
【００３４】
ソレノイド４３に対する供給電流値が零になると弁開度が最大となり、図３に示すように斜板２０の傾角が最小となる。斜板２０の傾角が最小になったときには遮断体２２が吸入通路３１を閉じ、外部冷媒回路３３における冷媒循環が停止する。この冷媒循環停止状態は熱負荷低減作用の停止状態である。
【００３５】
斜板２０の最小傾角は０°よりも僅かに大きくしてある。斜板２０の最小傾角は０°ではないため、斜板傾角が最小の状態においてもシリンダボア１１１から吐出室１３２への吐出は行われている。シリンダボア１１１から吐出室１３２へ吐出された冷媒は冷媒供給通路３８を通って制御圧室１２１へ流入する。制御圧室１２１内の冷媒は、通路５０、放圧通口２２１及び通口１４３という冷媒抜き出し通路を通って吸入室１３１へ流出し、吸入室１３１内の冷媒はシリンダボア１１１内へ吸入されて吐出室１３２へ吐出される。即ち、斜板傾角が最小状態では、吐出圧領域である吐出室１３２、冷媒供給通路３８、制御圧室１２１、前記冷媒抜き出し通路、吸入圧領域である吸入室１３１、シリンダボア１１１を経由する循環通路が圧縮機内にできている。そして、吐出室１３２、制御圧室１２１及び吸入室１３１の間では圧力差が生じている。従って、冷媒が前記循環通路を循環し、冷媒と共に流動する潤滑油が圧縮機内を潤滑する。
【００３６】
ソレノイド４３に対する電流供給を再開すると弁開度が小さくなり、制御圧室１２１内の圧力が下がる。従って、斜板２０の傾角が最小傾角から増大してゆく。斜板２０の傾角が最小傾角から増大すると遮断体２２が弁形成プレート１５から離間し、冷媒が吸入通路３１から吸入室１３１へ流入する。即ち、外部冷媒回路３３における冷媒循環が再開される。
【００３７】
制御コンピュータＣ１は、空調装置作動スイッチ４４のＯＮに伴う容量制御弁３９に対する電流供給の開始の際には緩衝用電流供給開始制御を行なう。又、制御コンピュータＣ１は、空調装置作動スイッチ４４のＯＦＦに伴う容量制御弁３９に対する電流供給の停止の際には緩衝用電流供給停止制御を行なう。
【００３８】
電流供給開始指令手段となる空調装置作動スイッチ４４をＯＮ操作すると、図６に示すように、電流供給開始指令信号Ｓ１が制御コンピュータＣ１に出力される。緩衝用電流供給開始制御手段となる制御コンピュータＣ１は、電流供給開始指令信号Ｓ１の入力に応答して室温設定器４５によって設定された目標室温と、室温検出器４６によって検出された検出温度との比較に基づいて容量制御弁３９に対する指定供給電流値Ｉｘを割り出す。供給電流値指定手段となる制御コンピュータＣ１は、図６の曲線Ｅのうちの上り傾斜部Ｅ１で示すように供給電流値を零から指定供給電流値Ｉｘまで徐々に増大させる緩衝用電流供給開始制御を行なう。緩衝用電流供給開始制御が行われると、容量制御弁３９の弁開度が徐々に減少してゆき、制御圧室１２１内の圧力が徐々に低下してゆく。制御圧室１２１内の緩慢な圧力低下に伴い、斜板２０の傾角が図６の曲線Ｋのうちの上り傾斜部Ｋ１で示すように最小傾角から徐々に増大してゆき、吐出容量が徐々に増大してゆく。斜板２０の傾角が最小傾角から増大すると、外部冷媒回路３３における冷媒循環が行われ、吸入圧が低下してゆく。図６の曲線Ｐのうちの平坦部Ｐ１は空調装置作動スイッチ４４のＯＮ前の吸入圧を表し、曲線Ｐのうちの下り傾斜部Ｐ２は斜板２０の最小傾角からの緩慢な傾角増大に伴う吸入圧変動を表す。
【００３９】
供給電流値が指定供給電流値Ｉｘになると、斜板２０が指定供給電流値Ｉｘに対応する傾角位置へ移行すると共に、吸入圧が指定供給電流値Ｉｘに対応する吸入圧へ収束する。図６の曲線Ｐのうちの平坦部Ｐ３は指定供給電流値Ｉｘに対応する吸入圧を表す。
【００４０】
電流供給停止指令手段となる空調装置作動スイッチ４４をＯＦＦ操作すると、図６に示すように、電流供給停止指令信号Ｓ２が制御コンピュータＣ１に出力される。緩衝用電流供給停止制御手段となる制御コンピュータＣ１は、電流供給停止指令信号Ｓ２の入力に応答して図６の曲線Ｅのうちの下り傾斜部Ｅ２で示すように供給電流値を電流供給停止指令信号Ｓ２の入力時の供給電流値Ｉｙから供給電流値零まで徐々に減少させる緩衝用電流供給停止制御を行なう。緩衝用電流供給停止制御が行われると、容量制御弁３９の弁開度が徐々に増大してゆき、制御圧室１２１内の圧力が徐々に高くなってゆく。制御圧室１２１内の緩慢な圧力上昇に伴い、斜板２０の傾角が図６の曲線Ｋのうちの下り傾斜部Ｋ２で示すように電流供給停止指令信号Ｓ２の入力時の傾角から徐々に減少してゆき、吐出容量が徐々に減少してゆく。斜板２０の傾角が電流供給停止指令信号Ｓ２の入力時の傾角から減少すると吐出容量が減ってゆき、吸入圧が上昇してゆく。図６の曲線Ｐのうちの平坦部Ｐ４は空調装置作動スイッチ４４のＯＦＦ前の吸入圧を表し、曲線Ｐのうちの上り傾斜部Ｐ５は斜板２０の電流供給停止指令信号Ｓ２の入力時の傾角からの緩慢な傾角減少に伴う吸入圧変動を表す。
【００４１】
供給電流値が零になると、斜板２０が最小傾角位置へ移行すると共に、外部冷媒回路３３における冷媒循環が停止する。図６の曲線Ｐのうちの平坦部Ｐ６は外部冷媒回路３３における冷媒循環停止後の吸入圧を表す。
【００４２】
以上のような容量可変動作を行なう第１の実施の形態では以下の効果が得られる。
（１-1）空調装置作動スイッチ４４のＯＮ操作によって電気式容量制御弁３９に対する電流供給が開始されるときには、供給電流値零から指定された指定供給電流値まで供給電流値を徐々に増大する緩衝用電流供給開始制御が行なわれる。緩慢な供給電流値の増大は斜板２０の傾角の急激な増大を抑制する。斜板２０の傾角の急激な増大は、斜板２０の最大傾角を規定する回転支持体１９と斜板２０との衝突をもたらし、衝突音が発生する。供給電流値の緩慢な増大具合は、斜板２０の傾角の増大が供給電流値の増大に対応して追随するように設定されている。このような斜板２０の傾角の急激な増大の抑制は、指定供給電流値に対応した傾角位置からの斜板２０のオーバーランを抑制する。指定供給電流値が最大傾角に対応する場合には、斜板２０の最大傾角位置での傾角増大速度が抑制される。その結果、衝突音をもたらすような回転支持体１９と斜板２０との衝突が回避される。
【００４３】
（１-2）空調装置作動スイッチ４４のＯＦＦ操作によって電気式容量制御弁３９に対する電流供給が停止されるときには、空調装置作動スイッチ４４のＯＦＦ直前の指定供給電流値から供給電流値零まで供給電流値を徐々に減少する緩衝用電流供給停止制御が行なわれる。緩慢な供給電流値の減少は斜板２０の傾角の急激な減少を抑制する。斜板２０の傾角の急激な減少は、斜板２０の最小傾角を規定する弁形成プレート１５と斜板２０に連動する遮断体２２との衝突をもたらし、衝突音が発生する。供給電流値の緩慢な減少具合は、斜板２０の傾角の減少が供給電流値の減少に対応して追随するように設定されている。このような斜板２０の傾角の急激な減少の抑制は、斜板２０の最小傾角位置での傾角減少速度を抑制する。斜板２０の最小傾角位置での傾角減少速度の抑制は、衝突音をもたらすような弁形成プレート１５と遮断体２２との衝突の回避をもたらす。
【００４４】
次に、図７及び図８の第２の実施の形態を説明する。第１の実施の形態と同じ構成部には同じ符号が付してある。
この実施の形態では、吸入室１３１内の吸入圧が圧力検出器５１によって検出されるようになっており、制御圧室１２１内の制御圧が圧力検出器５２によって検出されるようになっている。両圧力検出器５１，５２は検出情報を制御コンピュータＣ２へ送る。制御コンピュータＣ２には（吸入圧−供給電流値）マップ及び（制御圧−供給電流値）マップが記憶されている。制御コンピュータＣ２は、空調装置作動スイッチ４４のＯＮに伴う容量制御弁３９に対する電流供給の開始の際には（吸入圧−供給電流値）マップ及び圧力検出器５１から得られる圧力検出情報を利用した緩衝用電流供給開始制御を行なう。又、制御コンピュータＣ２は、空調装置作動スイッチ４４のＯＦＦに伴う容量制御弁３９に対する電流供給の停止の際には（制御圧−供給電流値）マップ及び圧力検出器５２から得られる圧力検出情報を利用した緩衝用電流供給停止制御を行なう。
【００４５】
電流供給開始指令手段となる空調装置作動スイッチ４４をＯＮ操作すると、図８に示すように、電流供給開始指令信号Ｓ１が制御コンピュータＣ２に出力される。緩衝用電流供給開始制御手段となる制御コンピュータＣ２は、電流供給開始指令信号Ｓ１の入力に応答して室温設定器４５によって設定された目標室温と、室温検出器４６によって検出された検出温度との比較に基づいて容量制御弁３９に対する指定供給電流値Ｉｘを割り出す。又、供給電流値指定手段となる制御コンピュータＣ２は、指定供給電流値Ｉｘ、圧力検出器５１から得られる検出圧力、及び（吸入圧−供給電流値）マップに基づいて増大飛躍限界供給電流値Ｉｚを割り出す。（吸入圧−供給電流値）マップは、吸入圧及び供給電流値を変数として増大飛躍限界供給電流値Ｉｚを求めるマップである。
【００４６】
制御コンピュータＣ２は、図８の曲線Ｄのうちの垂直線Ｄ１で示すように供給電流値を零から増大飛躍限界供給電流値Ｉｚへ不連続的に切り換え、次いで上り傾斜部Ｄ２で示すように供給電流値を増大飛躍限界供給電流値Ｉｚから指定供給電流値Ｉｘまで徐々に増大させる緩衝用電流供給開始制御を行なう。緩衝用電流供給開始制御が行われると、容量制御弁３９の弁開度が増大飛躍限界供給電流値Ｉｚに対応した弁開度まで瞬間的に変化してから徐々に減少してゆき、制御圧室１２１内の圧力が増大飛躍限界供給電流値Ｉｚからの供給電流値の緩慢な増大に追随するような状態で徐々に低下してゆく。制御圧室１２１内の緩慢な圧力低下に伴い、斜板２０の傾角が図８の曲線Ｈのうちの上り傾斜部Ｈ１で示すように最小傾角から徐々に増大してゆき、吐出容量が徐々に増大してゆく。斜板２０の緩慢な傾角増大は、増大飛躍限界供給電流値Ｉｚからの供給電流値の緩慢な減少に追随するような状態で行われる。斜板２０の傾角が最小傾角から増大すると、外部冷媒回路３３における冷媒循環が行われ、吸入圧が低下してゆく。図８の曲線Ｑのうちの平坦部Ｑ１は空調装置作動スイッチ４４のＯＮ前の吸入圧を表し、曲線Ｑのうちの下り傾斜部Ｑ２は斜板２０の最小傾角からの緩慢な傾角増大に伴う吸入圧変動を表す。
【００４７】
供給電流値が指定供給電流値Ｉｘになると、斜板２０が指定供給電流値Ｉｘに対応する傾角位置へ移行すると共に、吸入圧が指定供給電流値Ｉｘに対応する吸入圧へ収束する。図８の曲線Ｑのうちの平坦部Ｑ３は指定供給電流値Ｉｘに対応する吸入圧を表す。
【００４８】
空調装置作動スイッチ４４をＯＦＦ操作すると、図８に示すように、電流供給停止指令信号Ｓ２が制御コンピュータＣ２に出力される。緩衝用電流供給停止制御手段となる制御コンピュータＣ２は、電流供給停止指令信号Ｓ２の入力に応答して、空調装置作動スイッチ４４のＯＦＦ時の指定供給電流値、圧力検出器５２から得られる検出制御圧、及び（制御圧−供給電流値）マップに基づいて減少飛躍限界供給電流値Ｉｗを割り出す。（制御圧−供給電流値）マップは、制御圧及び供給電流値を変数として減少飛躍限界供給電流値Ｉｗを求めるマップである。
制御コンピュータＣ２は、図８の曲線Ｄのうちの垂直線Ｄ３で示すように供給電流値を空調装置作動スイッチ４４のＯＦＦ直前の指定供給電流値Ｉｙから減少飛躍限界供給電流値Ｉｗへ不連続的に切り換え、次いで下り傾斜部Ｄ４で示すように供給電流値を減少飛躍限界供給電流値Ｉｗから零まで徐々に減少させる緩衝用電流供給停止制御を行なう。緩衝用電流供給停止制御が行われると、容量制御弁３９の弁開度が減少飛躍限界供給電流値Ｉｗに対応した弁開度まで瞬間的に変化してから徐々に増大してゆき、制御圧室１２１内の圧力が減少飛躍限界供給電流値Ｉｗからの供給電流値の緩慢な減少に追随するような状態で徐々に上昇してゆく。制御圧室１２１内の緩慢な圧力上昇に伴い、斜板２０の傾角が図８の曲線Ｈのうちの下り傾斜部Ｈ２で示すように電流供給停止指令信号Ｓ２の入力時の傾角から徐々に減少してゆく。斜板２０の傾角が電流供給停止指令信号Ｓ２の入力時の傾角から減少すると吐出容量が減ってゆき、吸入圧が上昇してゆく。図８の曲線Ｑのうちの平坦部Ｑ４は空調装置作動スイッチ４４のＯＦＦ前の吸入圧を表し、曲線Ｑのうちの上り傾斜部Ｑ５は斜板２０の電流供給停止指令信号Ｓ２の入力時の傾角からの緩慢な傾角減少に伴う吸入圧変動を表す。
【００４９】
供給電流値が零になると、斜板２０が最小傾角位置へ移行すると共に、外部冷媒回路３３における冷媒循環が停止する。図８の曲線Ｑのうちの平坦部Ｑ６は外部冷媒回路３３における冷媒循環停止後の吸入圧を表す。
【００５０】
第２の実施の形態では以下の効果が得られる。
（２-1）空調装置作動スイッチ４４のＯＮ操作によって電気式容量制御弁３９に対する電流供給が開始されるときには、圧力検出器５１と共に増大飛躍限界供給電流値指定手段を構成する制御コンピュータＣ２が検出吸入圧に応じた増大飛躍限界供給電流値を指定する。そして、制御コンピュータＣ２は、供給電流値を零から増大飛躍限界供給電流値Ｉｚまで不連続的に増大し、次いで増大飛躍限界供給電流値Ｉｚから指定された指定供給電流値まで供給電流値を徐々に増大する緩衝用電流供給開始制御を行なう。増大飛躍限界供給電流値Ｉｚは、斜板２０と回転支持体１９との衝突をもたらさないような供給電流値の零からの不連続的な増大量の限界値であって吸入圧に左右される。即ち、供給電流値を零から検出吸入圧に対応した増大飛躍限界供給電流値Ｉｚよりも高い値に不連続的に増大させた場合には斜板２０が回転支持体１９に衝突して衝突音が発生する。供給電流値を零から増大飛躍限界供給電流値Ｉｚへ不連続的に増大させた場合には、斜板２０の最小傾角からの傾角増大が衝突音をもたらすことなく速やかに行われ、容量復帰が速やかに行われる。
【００５１】
（２-2）空調装置作動スイッチ４４のＯＦＦ操作によって電気式容量制御弁３９に対する電流供給が停止されるときには、圧力検出器５２と共に減少飛躍限界供給電流値指定手段を構成する制御コンピュータＣ２が検出制御圧に応じた減少飛躍限界供給電流値を指定する。そして、制御コンピュータＣ２は、空調装置作動スイッチ４４のＯＦＦ直前の指定供給電流値から減少飛躍限界供給電流値Ｉｗまで供給電流値を不連続的に減少し、次いで減少飛躍限界供給電流値Ｉｗから供給電流値零まで供給電流値を徐々に減少する緩衝用電流供給停止制御を行なう。減少飛躍限界供給電流値Ｉｗは、遮断体２２と弁形成プレート１５との衝突をもたらさないような指定供給電流値Ｉｙからの不連続的な減少量の限界値であって検出制御圧に左右される。即ち、供給電流値を指定供給電流値Ｉｙから検出制御圧に対応した減少飛躍限界供給電流値Ｉｗよりも低い値に不連続的に減少させた場合には遮断体２２が弁形成プレート１５に衝突して衝突音が発生する。供給電流値を指定供給電流値Ｉｙから減少飛躍限界供給電流値Ｉｗへ不連続的に減少させた場合には、斜板２０の最小傾角位置への移行が衝突音をもたらすことなく速やかに行われる。
【００５２】
次に、図９及び図１０の第３の実施の形態を説明する。第１の実施の形態と同じ構成部には同じ符号が付してある。
この実施の形態では、電気式容量制御弁５３のソレノイド５３１が励磁されると弁体５３２が弁孔５３３を閉じ、斜板２０が最大傾角位置に移行する。ソレノイド５３１が消磁されると弁体５３２が弁開度最大位置へ移行し、斜板２０が最小傾角位置へ移行する。電流供給開始指令手段及び電流供給停止指令手段となる空調装置作動スイッチ４４がＯＮされると、制御コンピュータＣ３はソレノイド５３１を励磁する。ソレノイド５３１が励磁しているときに空調装置作動スイッチ４４がＯＦＦされると、制御コンピュータＣ３はソレノイド５３１を消磁する。空調装置作動スイッチ４４がＯＮ状態において、制御コンピュータＣ３は、室温検出器４６によって得られた検出温度が室温設定器４５によって設定された目標室温以下になるとソレノイド５３１の消磁を指令する。制御コンピュータＣ３は、検出温度が目標室温を越えるとソレノイド５３１の励磁を指令する。室温検出器４６及び制御コンピュータＣ３は、電流供給開始指令手段及び電流供給停止指令手段を構成する。
【００５３】
ソレノイド５３１を励磁するときには、制御コンピュータＣ３は図１０の曲線Ｆの上り傾斜部Ｆ１で示す緩衝用電流供給開始制御を行なう。供給電流値の最大値は指定供給電流値となる。信号Ｓ３は、空調装置作動スイッチ４４のＯＮ操作時あるいは検出温度が目標室温を越えたときの電流供給開始指令を表す。曲線Ｇの上り傾斜部Ｇ１は供給電流値の増大に伴う斜板２０の傾角増大を表し、曲線Ｒの下り傾斜部Ｒ１は斜板２０の傾角増大に伴う吸入圧の低下を表す。
【００５４】
ソレノイド５３１を消磁するときには、制御コンピュータＣ３は図１０の曲線Ｆの下り傾斜部Ｆ２で示す緩衝用電流供給停止制御を行なう。信号Ｓ４は、空調装置作動スイッチ４４のＯＦＦ操作時あるいは検出温度が目標室温以下になったときの電流供給停止指令を表す。曲線Ｇの下り傾斜部Ｇ２は供給電流値の減少に伴う斜板２０の傾角減少を表し、曲線Ｒの上り傾斜部Ｒ２は斜板２０の傾角減少に伴う吸入圧の上昇を表す。
【００５５】
この実施の形態においても、斜板２０の最大傾角位置における斜板２０の傾角増大速度が抑制され、斜板２０と回転支持体１９との衝突が抑制される。又、斜板２０の最小傾角位置における斜板２０の傾角減少速度が抑制され、遮断体２２と弁形成プレート１５との衝突が抑制される。
【００５６】
本発明では以下のような実施の形態も可能である。
（１）第１の実施の形態において、電流供給開始時には、斜板２０の最大傾角位置における傾角増大速度を抑制するように供給電流値を零から最大値あるいは最大値付近まで連続的に増大した後に指定供給電流値まで連続的に減少させること。このようにすれば容量復帰が早くなる。
（２）制御圧室から吸入圧領域へ冷媒を抜き出す通路上に容量制御弁を介在した可変容量型圧縮機に本発明を適用すること。
（３）供給電流値をデューティ比制御すること。この場合、単位時間当たりの平均供給電流値を供給電流値と見なす。
（４）外部駆動源からクラッチを介して回転軸に駆動力を伝えるクラッチ付き可変容量型圧縮機に本発明を適用すること。
【００５７】
【発明の効果】
以上詳述したように、電気式容量制御弁に対する電流供給を開始するときには、指定された供給電流値を供給開始するまでの過程として前記斜板の最大傾角位置での傾角増大速度を抑制するための緩衝用電流供給開始制御を行なうようにした発明では、斜板の最大傾角位置への不要な到達を回避して衝突音の発生を回避し、さらに斜板が最大傾角位置にきたときの衝突音を抑制し得るという優れた効果を奏する。
【００５８】
電気式容量制御弁に対する電流供給を停止するときには、供給電流値を零とするまでの過程として前記斜板の最小傾角位置での傾角減少速度を抑制するための緩衝用電流供給停止制御を行なうようにした発明では、斜板が最小傾角位置にきたときの衝突音を抑制し得るという優れた効果を奏する。
【図面の簡単な説明】
【図１】第１の実施の形態を示す圧縮機全体の側断面図。
【図２】電気式容量制御弁３９の縦断面図。
【図３】斜板傾角が最小状態にある要部側断面図。
【図４】図１のＡ−Ａ線断面図。
【図５】図１のＢ−Ｂ線断面図。
【図６】供給電流値、斜板傾角、吸入圧の関係を示すグラフ。
【図７】第２の実施の形態を示す圧縮機全体の側断面図。
【図８】供給電流値、斜板傾角、吸入圧の関係を示すグラフ。
【図９】第３の実施の形態を示す圧縮機全体の側断面図。
【図１０】供給電流値、斜板傾角、吸入圧の関係を示すグラフ。
【符号の説明】
１２１…制御圧室、１３１…吸入圧領域となる吸入室、１３２…吐出圧領域となる吐出室、１８…回転軸、２０…斜板、３８…冷媒供給通路、３９…電気式容量制御弁、４４…電流供給開始指令手段及び電流供給停止指令手段となる空調装置作動スイッチ、Ｃ１…緩衝用電流供給開始制御手段、緩衝用電流供給停止制御手段及び供給電流値指定手段となる制御コンピュータ、Ｃ２…緩衝用電流供給開始制御手段、緩衝用電流供給停止制御手段、供給電流値指定手段、増大飛躍限界供給電流値指定手段、及び減少飛躍限界供給電流値指定手段となる制御コンピュータ、Ｃ３…緩衝用電流供給開始制御手段及び緩衝用電流供給停止制御手段となる制御コンピュータ。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a capacity control method and apparatus in a variable capacity compressor.
[0002]
[Prior art]
In the variable displacement compressor disclosed in Japanese Patent Application Laid-Open No. 8-338364, the discharge capacity is changed based on the pressure difference between the crank chamber pressure and the suction pressure in the suction pressure region. The pressure in the crank chamber is adjusted by supplying the refrigerant from the discharge chamber, which is a discharge pressure region, to the crank chamber, and extracting the refrigerant from the crank chamber to the suction chamber, which is a suction pressure region. A solenoid valve for capacity control is interposed on the pressure supply passage for supplying the refrigerant from the discharge chamber to the crank chamber. The valve body of the solenoid valve is biased toward the valve closing position by excitation of the solenoid. The supply current value for the solenoid valve is determined based on a comparison between a preset set room temperature and a detected room temperature. The larger the difference between the set room temperature and the detected room temperature, the larger the supply current value, and the smaller the valve opening of the solenoid valve. As the valve opening decreases, the swash plate tilt angle increases and the discharge capacity increases. When the valve body is disposed at the valve closing position, the pressure supply passage is closed, and the refrigerant supply from the discharge chamber to the crank chamber is stopped. Therefore, the inclination angle of the swash plate becomes the maximum inclination angle. When the solenoid is demagnetized, the valve body moves to the maximum valve opening position, and refrigerant supply from the discharge chamber to the crank chamber increases. This increases the pressure in the crank chamber and minimizes the inclination of the swash plate. In the minimum inclination state of the swash plate, a blocking body interlocking with the inclination of the swash plate closes the suction passage, and refrigerant circulation in the external refrigerant circuit stops. This refrigerant circulation stop state is a state without a heat load reducing action.
[0003]
[Problems to be solved by the invention]
Normally, when the air conditioner operation switch is turned on, the difference between the set room temperature and the detected room temperature is large, and the supply current value to the solenoid valve becomes a large value from when the air conditioner operation switch is turned on. As a result, the swash plate inclination angle suddenly increases from the minimum inclination angle, and the swash plate may quickly pass through the swash plate inclination position corresponding to the selected supply current value to the maximum inclination position. Such a passage causes a collision between the member that defines the maximum inclination angle of the swash plate and the swash plate, and a collision sound is generated. Further, when the air conditioner operation switch is turned off when the difference between the set room temperature and the detected room temperature is large, the supply current value for the solenoid valve is instantaneously switched from a large value to zero. For this reason, the swash plate inclination angle rapidly decreases from a large inclination angle, and the swash plate moves quickly to the minimum inclination position. Such a rapid transition causes a collision between a member that defines the minimum inclination angle of the swash plate and the swash plate, and a collision sound is generated.
[0004]
An object of the present invention is to prevent the occurrence of the above-described collision noise when starting current supply to a capacity control valve or stopping current supply.
[0005]
[Means for Solving the Problems]
For this purpose, the present invention performs a reciprocating operation in accordance with the inclination angle of the swash plate that is housed in the control pressure chamber so as to rotate integrally with the rotation shaft and that can be tilted with respect to the rotation shaft. A piston is provided to supply the refrigerant from the discharge pressure region to the control pressure chamber and to draw out the refrigerant from the control pressure chamber to the suction pressure region and on the refrigerant supply passage from the discharge pressure region to the control pressure chamber or the control An electric capacity control valve is interposed on the refrigerant extraction passage extending from the pressure chamber to the suction pressure region, and the supply current value (per unit time) to the electric capacity control valve is controlled to control the control pressure from the discharge pressure region. A variable capacity compressor that controls a refrigerant supply amount to a chamber or a refrigerant extraction amount from the control pressure chamber to the suction pressure region, and controls an inclination angle of the swash plate based on a control of a pressure in the control pressure chamber. Covered and claim 1 In the present invention, when the current supply to the electric capacity control valve is started, as a process until the supply of the specified supply current value is started, the buffer for suppressing the tilt increase speed at the maximum tilt position of the swash plate Current supply start control was performed.
[0006]
  Also,The buffer current supply start control increases the supply current value from zero supply current value to the specified supply current value specified.DoI did it.
[0007]
  furtherThe buffer current supply start control includes a supply current value switching state in which the supply current value is discontinuously switched from a supply current value of zero to an increase jump limit supply current value that does not reach the specified supply current value, and the increase jump limit. A current increasing supply state in which the supply current value is gradually increased from the supply current value to the specified supply current value.
[0008]
  Claim2According to the invention, when the current supply to the electric capacity control valve is stopped, the buffer current supply for suppressing the rate of decrease in the inclination angle at the minimum inclination position of the swash plate as a process until the supply current value becomes zero. Stop control was performed.
[0009]
  AlsoThe buffer current supply stop control decreases the supply current value from the specified supply current value to the supply current value of zero.DoI did it.
[0010]
  furtherThe buffer current supply stop control includes a supply current value switching state in which the supply current value is discontinuously switched from the specified supply current value to a decrease jump limit supply current value that does not reach the specified supply current value, and the decrease jump. A current decreasing supply state in which the supply current value gradually decreases from the limit supply current value to the supply current value of zero.
[0011]
  Claim3In the invention, current supply start command means for instructing start of current supply to the electric capacity control valve, and buffer current supply start control for suppressing the tilt increase speed at the maximum tilt position of the swash plate are performed. Buffer current supply start control means; andSupply current value specifying means for specifying a supply current value; and increased jump limit supply current value specifying means for specifying an increased jump limit supply current value that does not reach the specified supply current value;The buffer current supply start control means performs the buffer current supply start control based on a current supply start command of the current supply start command means.
[0012]
  AlsoThe buffering current supply start control means increases the supply current value from zero to the designated supply current value designated by the supply current value designation means.DoI did it.
[0013]
  furtherThe buffer current supply start control means discontinuously switches the supply current value from a supply current value of zero to an increased jump limit supply current value that does not reach the specified supply current value, and from the increase jump limit supply current value, Current supply start control for gradually increasing the supply current value up to the specified supply current value is performed.
  Claim4In this invention, current supply stop command means for instructing stop of current supply to the electric capacity control valve, and buffer current supply stop control for suppressing the inclination decrease rate at the minimum inclination position of the swash plate are performed. Buffer current supply stop control means andSupply current value specifying means for specifying the supply current value, and decrease jump limit supply current value specifying means for specifying the decrease jump limit supply current value;The buffering current supply stop control means performs the buffering current supply stop control based on the current supply stop command of the current supply stop command means.
[0014]
  AlsoThe buffer current supply stop control means decreases the supply current value from the designated supply current value designated by the supply current value designation means to the supply current value zero.DoI did it.
[0015]
  furtherThe buffering current supply stop control means discontinuously switches the supply current value from the specified supply current value to a decrease jump limit supply current value that does not reach the specified supply current value, and from the decrease jump limit supply current value Current supply stop control is performed to gradually decrease the supply current value until the supply current value becomes zero.
[0016]
  Claim 1 and claim3In this invention, when current supply to the electric capacity control valve is started, buffer current supply start control is performed, and a rapid increase in the swash plate inclination angle is suppressed. Suppressing the sudden increase of the swash plate tilt angle by controlling the start of the buffer current supply prevents the swash plate from unnecessarily reaching the maximum tilt position or suppresses the tilt increase rate when the swash plate reaches the maximum tilt position. Bring.
[0017]
  AlsoSupply current value from zero to the specified supply current valueWithSupply current valueIncreaseIncreased current supply is performed.
[0018]
  furtherAfter the supply current value is discontinuously switched from zero to the increase jump limit supply current value that does not reach the specified supply current value, the supply current value is gradually increased from the increase jump limit supply current value to the specified supply current value. Increasing current supply is performed. The current supply state including the current increase supply state in which the supply current value is gradually increased suppresses a rapid increase in the swash plate inclination angle. Discontinuous switching of the supply current value from the supply current value of zero to the increased jump limit supply current value contributes to a rapid increase in discharge capacity.
[0019]
  Claim2And claims4In this invention, when the current supply to the electric capacity control valve is stopped, the buffer current supply stop control is performed, and the rapid decrease of the swash plate inclination angle is suppressed. Suppressing the rapid decrease in the swash plate tilt angle by the buffer current supply stop control brings about the suppression of the tilt decrease rate when the swash plate reaches the minimum tilt position.
[0020]
  AlsoFrom the specified supply current value to zeroWithSupply current valueDecreaseLess current reduction is provided.
[0021]
  furtherAfter the supply current value is discontinuously switched from the specified supply current value to the reduced jump limit supply current value, the current reduction supply gradually decreases the supply current value from the decrease jump limit supply current value to the supply current value zero. Done. The current supply state including the current decrease supply state in which the supply current value is gradually reduced suppresses a rapid decrease in the swash plate inclination angle. Discontinuous switching from the specified supply current value to the increased jump limit supply current value contributes to a rapid decrease in the discharge capacity.
[0022]
DETAILED DESCRIPTION OF THE INVENTION
A first embodiment in which the present invention is embodied in a clutchless variable displacement compressor mounted on a vehicle will be described below with reference to FIGS.
[0023]
As shown in FIG. 1, a front housing 12 is joined to the front end of the cylinder block 11. A rear housing 13 is joined and fixed to the rear end of the cylinder block 11 via a valve plate 14, valve forming plates 15 and 16, and a retainer forming plate 17. A rotating shaft 18 installed and supported between the front housing 12 and the cylinder block 11 forming the control pressure chamber 121 obtains a rotational driving force from a vehicle engine (not shown).
[0024]
A swash plate 20 is supported on the rotary shaft 18 so as to be slidable and tiltable in the axial direction of the rotary shaft 18. As shown in FIG. 4, the heads of the guide pins 23 and 24 fixed to the swash plate 20 are slidably fitted into the guide holes 191 and 192 of the rotary support 19 fixed to the rotary shaft 18. Yes. The swash plate 20 can be tilted in the axial direction of the rotary shaft 18 and can rotate integrally with the rotary shaft 18 by the linkage of the guide holes 191 and 192 and the guide pins 23 and 24. When the radius center portion of the swash plate 20 moves to the cylinder block 11 side, the inclination angle of the swash plate 20 decreases. An inclination reduction spring 25 interposed between the rotary support 19 and the swash plate 20 urges the swash plate 20 in a direction to reduce the inclination angle of the swash plate 20.
[0025]
As shown in FIGS. 1 and 3, a cylindrical blocking body 22 is slidably accommodated in an accommodation hole 21 penetrating in the center of the cylinder block 11. A suction passage opening spring 26 interposed between the blocking body 22 and the end face of the accommodation hole 21 urges the blocking body 22 toward the swash plate 20. The rear end portion of the rotary shaft 18 is supported on the peripheral surface of the accommodation hole 21 via the radial bearing 27 and the blocking body 22. A suction passage 31 formed at the center of the rear housing 13 is connected to the accommodation hole 21. Movement of the blocking body 22 in a direction away from the swash plate 20 is restricted when the distal end surface of the blocking body 22 contacts the valve forming plate 15. As the swash plate 20 moves toward the blocking body 22, the tilt of the swash plate 20 is transmitted to the blocking body 22 via the thrust bearing 37. The rotation of the swash plate 20 is prevented from being transmitted to the blocking body 22 due to the presence of the thrust bearing 37. By this tilt transmission, the blocking body 22 moves toward the valve forming plate 15 against the spring force of the suction passage opening spring 26, and the blocking body 22 contacts the valve forming plate 15 as shown in FIG. The minimum inclination angle of the swash plate 20 is defined by the contact between the blocking body 22 and the valve forming plate 15. FIG. 3 shows the minimum inclination state of the swash plate 20. FIG. 1 shows a maximum inclination state of the swash plate 20. The maximum inclination angle of the swash plate 20 is defined by the contact between the swash plate 20 and the rotary support 19.
[0026]
A piston 28 is accommodated in a cylinder bore 111 penetrating the cylinder block 11. The rotational movement of the swash plate 20 is converted into the back-and-forth reciprocating movement of the piston 28 via the shoe 29, and the piston 28 moves back and forth in the cylinder bore 111.
[0027]
As shown in FIG. 5, in the rear housing 13, a suction chamber 131 serving as a suction pressure region and a discharge chamber 132 serving as a discharge pressure region are formed around the suction chamber 131. A suction port 141 and a discharge port 142 are formed in the valve plate 14. A suction valve 151 is formed on the valve forming plate 15, and a discharge valve 161 is formed on the valve forming plate 16. The refrigerant in the suction chamber 131 flows into the cylinder bore 111 by pushing the suction valve 151 away from the suction port 141 by the backward movement of the piston 28. The refrigerant flowing into the cylinder bore 111 is discharged into the discharge chamber 132 by pushing the discharge valve 161 away from the discharge port 142 by the forward movement of the piston 28. The discharge valve 161 abuts on the retainer 171 on the retainer forming plate 17 and the opening degree is regulated.
[0028]
A thrust bearing 32 interposed between the rotary support 19 and the front housing 12 is applied to the rotary support 19 from the cylinder bore 111 via the piston 28, the shoe 29, the swash plate 20 and the guide pins 23 and 24. Take power.
[0029]
A passage 50 in the rotating shaft 18 communicates the control pressure chamber 121 and the cylinder of the blocking body 22. As shown in FIG. 3, a pressure release port 221 penetrating the peripheral surface of the blocking body 22 communicates the inside of the blocking body 22 with the accommodation hole 21.
[0030]
The suction chamber 131 communicates with the accommodation hole 21 through the communication port 143. When the blocking body 22 comes into contact with the valve forming plate 15, the opening 143 is blocked from the suction passage 31. The suction passage 31 for introducing the refrigerant into the suction chamber 131 and the discharge chamber 132 are connected by an external refrigerant circuit 33. A condenser 34, an expansion valve 35 and an evaporator 36 are interposed on the external refrigerant circuit 33. The expansion valve 35 controls the flow rate of the refrigerant according to the change in the gas temperature on the outlet side of the evaporator 36.
[0031]
An electric capacity control valve 39 shown in FIG. 2 is interposed on the refrigerant supply passage 38 connecting the discharge chamber 132 and the control pressure chamber 121. The refrigerant supply passage 38 is a passage through which the refrigerant in the discharge chamber 132 that is a discharge pressure region is supplied to the control pressure chamber 121. The pressure (suction pressure) in the suction chamber 131 acts on the bellows 40 constituting the pressure-sensitive means 47 in the capacity control valve 39. The suction pressure in the suction chamber 131 reflects the heat load. A valve body 41 is connected to the bellows 40, and the valve body 41 opens and closes the valve hole 42. The spring force of the pressure sensitive spring 401 constituting the atmospheric pressure and pressure sensitive means 47 in the bellows 40 acts on the valve body 41 in the direction of opening the valve hole 42. The fixed iron core 431 constituting the solenoid 43 of the capacity control valve 39 attracts the movable iron core 433 based on excitation by supplying current to the coil 432. That is, the electromagnetic driving force of the solenoid 43 biases the valve body 41 in a direction to close the valve hole 42 against the spring force of the opening biasing spring 48. The follower spring 49 urges the movable iron core 433 toward the fixed iron core 431 side. The solenoid 43 receives the current supply control of the control computer C1.
[0032]
The control computer C1 supplies current to the solenoid 43 when the air conditioner operation switch 44 is turned on, and stops supplying current when the air conditioner operation switch 44 is turned off. A room temperature setter 45 and a room temperature detector 46 are signal-connected to the control computer C1. The control computer C1 controls the supply current value to the solenoid 43 based on the target room temperature information set by the room temperature setter 45 and the detected room temperature information detected by the room temperature detector 46. The degree of opening and closing in the valve hole 42, that is, the valve opening, is determined by the balance of the electromagnetic driving force generated by the solenoid 43, the spring force of the follower spring 49, the spring force of the open biasing spring 48, and the biasing force of the pressure sensing means 47. The control valve 39 performs control for providing suction pressure in accordance with the current value supplied to the solenoid 43.
[0033]
When the supply current value is increased, the valve opening decreases, and the refrigerant supply amount from the discharge chamber 132 to the control pressure chamber 121 decreases. Since the refrigerant in the control pressure chamber 121 flows out to the suction chamber 131 through the refrigerant extraction passages of the passage 50, the pressure release passage 221 and the passage 143, the pressure in the control pressure chamber 121 decreases. Accordingly, the inclination angle of the swash plate 20 increases and the discharge capacity increases. An increase in the discharge capacity causes a decrease in the suction pressure. When the supply current value is lowered, the valve opening increases, and the amount of refrigerant supplied from the discharge chamber 132 to the control pressure chamber 121 increases. Accordingly, the pressure in the control pressure chamber 121 increases, the inclination angle of the swash plate 20 decreases, and the discharge capacity decreases. A decrease in the discharge capacity results in an increase in the suction pressure.
[0034]
When the supply current value to the solenoid 43 becomes zero, the valve opening becomes maximum, and the inclination angle of the swash plate 20 becomes minimum as shown in FIG. When the inclination angle of the swash plate 20 is minimized, the blocking body 22 closes the suction passage 31 and the refrigerant circulation in the external refrigerant circuit 33 is stopped. This refrigerant circulation stop state is a stop state of the heat load reducing action.
[0035]
The minimum inclination angle of the swash plate 20 is slightly larger than 0 °. Since the minimum inclination angle of the swash plate 20 is not 0 °, the discharge from the cylinder bore 111 to the discharge chamber 132 is performed even when the swash plate inclination angle is minimum. The refrigerant discharged from the cylinder bore 111 into the discharge chamber 132 flows into the control pressure chamber 121 through the refrigerant supply passage 38. The refrigerant in the control pressure chamber 121 flows out into the suction chamber 131 through the refrigerant extraction passages of the passage 50, the pressure release passage 221 and the passage 143, and the refrigerant in the suction chamber 131 is sucked into the cylinder bore 111 and discharged. It is discharged into the chamber 132. That is, when the inclination angle of the swash plate is minimum, the discharge chamber 132 that is the discharge pressure region, the refrigerant supply passage 38, the control pressure chamber 121, the refrigerant extraction passage, the suction chamber 131 that is the suction pressure region, and the circulation passage through the cylinder bore 111 Is made in the compressor. A pressure difference is generated between the discharge chamber 132, the control pressure chamber 121, and the suction chamber 131. Accordingly, the refrigerant circulates in the circulation passage, and the lubricating oil flowing together with the refrigerant lubricates the inside of the compressor.
[0036]
When the current supply to the solenoid 43 is resumed, the valve opening decreases, and the pressure in the control pressure chamber 121 decreases. Accordingly, the inclination angle of the swash plate 20 increases from the minimum inclination angle. When the inclination angle of the swash plate 20 increases from the minimum inclination angle, the blocking body 22 is separated from the valve forming plate 15, and the refrigerant flows into the suction chamber 131 from the suction passage 31. That is, the refrigerant circulation in the external refrigerant circuit 33 is resumed.
[0037]
The control computer C1 performs buffer current supply start control when starting current supply to the capacity control valve 39 when the air conditioner operation switch 44 is turned ON. Further, the control computer C1 performs buffer current supply stop control when the current supply to the capacity control valve 39 is stopped when the air conditioner operation switch 44 is turned OFF.
[0038]
When the air conditioner operation switch 44 serving as a current supply start command means is turned ON, a current supply start command signal S1 is output to the control computer C1, as shown in FIG. The control computer C1 serving as a buffering current supply start control means responds to the input of the current supply start command signal S1 with the target room temperature set by the room temperature setter 45 and the detected temperature detected by the room temperature detector 46. Based on the comparison, the designated supply current value Ix for the capacity control valve 39 is determined. The control computer C1 serving as the supply current value designating means gradually increases the supply current value from zero to the designated supply current value Ix as shown by the upward slope E1 in the curve E in FIG. To do. When the buffer current supply start control is performed, the valve opening degree of the capacity control valve 39 gradually decreases, and the pressure in the control pressure chamber 121 gradually decreases. As the pressure in the control pressure chamber 121 slowly decreases, the inclination angle of the swash plate 20 gradually increases from the minimum inclination angle as shown by the upward inclined portion K1 in the curve K in FIG. 6, and the discharge capacity gradually increases. It will increase. When the inclination angle of the swash plate 20 increases from the minimum inclination angle, the refrigerant circulation in the external refrigerant circuit 33 is performed, and the suction pressure decreases. The flat part P1 in the curve P in FIG. 6 represents the suction pressure before the air conditioner operation switch 44 is turned on, and the downward inclination part P2 in the curve P is accompanied by a slow increase in inclination from the minimum inclination of the swash plate 20. Represents fluctuations in suction pressure.
[0039]
When the supply current value becomes the designated supply current value Ix, the swash plate 20 moves to the tilt position corresponding to the designated supply current value Ix, and the suction pressure converges to the suction pressure corresponding to the designated supply current value Ix. A flat portion P3 in the curve P in FIG. 6 represents the suction pressure corresponding to the designated supply current value Ix.
[0040]
When the air conditioner operation switch 44 serving as the current supply stop command means is turned off, a current supply stop command signal S2 is output to the control computer C1, as shown in FIG. In response to the input of the current supply stop command signal S2, the control computer C1 serving as the buffering current supply stop control means sets the supply current value to the current supply stop command as indicated by the downward slope E2 in the curve E of FIG. Buffer current supply stop control for gradually decreasing the supply current value Iy at the time of input of the signal S2 from the supply current value zero is performed. When the buffer current supply stop control is performed, the valve opening of the capacity control valve 39 gradually increases, and the pressure in the control pressure chamber 121 gradually increases. As the pressure in the control pressure chamber 121 rises slowly, the inclination angle of the swash plate 20 gradually decreases from the inclination angle when the current supply stop command signal S2 is input, as indicated by the downward inclination portion K2 of the curve K in FIG. As a result, the discharge capacity gradually decreases. When the tilt angle of the swash plate 20 decreases from the tilt angle when the current supply stop command signal S2 is input, the discharge capacity decreases and the suction pressure increases. The flat part P4 in the curve P in FIG. 6 represents the suction pressure before the air conditioner operation switch 44 is turned off, and the upward inclined part P5 in the curve P is when the current supply stop command signal S2 of the swash plate 20 is input. Represents fluctuations in suction pressure associated with a slow decrease in tilt angle.
[0041]
When the supply current value becomes zero, the swash plate 20 moves to the minimum inclination position and the refrigerant circulation in the external refrigerant circuit 33 stops. A flat portion P6 in the curve P in FIG. 6 represents the suction pressure after the refrigerant circulation is stopped in the external refrigerant circuit 33.
[0042]
The following effects are obtained in the first embodiment that performs the variable capacitance operation as described above.
(1-1) When the current supply to the electric capacity control valve 39 is started by turning on the air conditioner operation switch 44, the supply current value is gradually increased from the supply current value zero to the designated designated supply current value. Buffer current supply start control is performed. The slow increase in the supply current value suppresses a rapid increase in the inclination angle of the swash plate 20. A sudden increase in the inclination angle of the swash plate 20 causes a collision between the rotary support 19 that defines the maximum inclination angle of the swash plate 20 and the swash plate 20, and a collision sound is generated. The slow increase in the supply current value is set such that the increase in the inclination angle of the swash plate 20 follows the increase in the supply current value. Such suppression of the rapid increase in the tilt angle of the swash plate 20 suppresses overrun of the swash plate 20 from the tilt position corresponding to the designated supply current value. When the designated supply current value corresponds to the maximum tilt angle, the tilt increase rate at the maximum tilt position of the swash plate 20 is suppressed. As a result, a collision between the rotary support 19 and the swash plate 20 that causes a collision sound is avoided.
[0043]
(1-2) When the current supply to the electric capacity control valve 39 is stopped by the OFF operation of the air conditioner operation switch 44, the supply current from the specified supply current value immediately before the air conditioner operation switch 44 is turned OFF to the supply current value of zero. Buffer current supply stop control is performed to gradually decrease the value. The slow decrease in the supply current value suppresses a rapid decrease in the inclination angle of the swash plate 20. The sudden decrease in the inclination angle of the swash plate 20 causes a collision between the valve forming plate 15 that defines the minimum inclination angle of the swash plate 20 and the blocking body 22 interlocked with the swash plate 20, and a collision sound is generated. The slow decrease in the supply current value is set so that the decrease in the tilt angle of the swash plate 20 follows the decrease in the supply current value. Such suppression of the rapid decrease in the tilt angle of the swash plate 20 suppresses the tilt decrease rate at the minimum tilt position of the swash plate 20. Suppression of the inclination decreasing speed at the minimum inclination position of the swash plate 20 results in avoiding the collision between the annuloplasty plate 15 and the blocking body 22 that causes a collision sound.
[0044]
Next, a second embodiment of FIGS. 7 and 8 will be described. The same components as those in the first embodiment are denoted by the same reference numerals.
In this embodiment, the suction pressure in the suction chamber 131 is detected by the pressure detector 51, and the control pressure in the control pressure chamber 121 is detected by the pressure detector 52. . Both pressure detectors 51 and 52 send detection information to the control computer C2. The control computer C2 stores a (suction pressure-supply current value) map and a (control pressure-supply current value) map. The control computer C2 utilizes the (suction pressure-supply current value) map and the pressure detection information obtained from the pressure detector 51 when starting the current supply to the capacity control valve 39 when the air conditioner operation switch 44 is turned on. Buffer current supply start control is performed. Further, the control computer C2 displays the (control pressure-supply current value) map and the pressure detection information obtained from the pressure detector 52 when the current supply to the capacity control valve 39 is stopped when the air conditioner operation switch 44 is turned off. The buffer current supply stop control used is performed.
[0045]
When the air conditioner operation switch 44 serving as a current supply start command means is turned on, a current supply start command signal S1 is output to the control computer C2, as shown in FIG. The control computer C2 serving as the buffering current supply start control means is configured to set the target room temperature set by the room temperature setter 45 in response to the input of the current supply start command signal S1 and the detected temperature detected by the room temperature detector 46. Based on the comparison, the designated supply current value Ix for the capacity control valve 39 is determined. Further, the control computer C2 serving as the supply current value designating means, based on the designated supply current value Ix, the detected pressure obtained from the pressure detector 51, and the (suction pressure-supply current value) map, increases the leap limit supply current value Iz. Is determined. The (suction pressure-supply current value) map is a map for obtaining the increased jump limit supply current value Iz using the suction pressure and the supply current value as variables.
[0046]
The control computer C2 discontinuously switches the supply current value from zero to the increased jump limit supply current value Iz as indicated by the vertical line D1 in the curve D of FIG. 8, and then supplies the supply current as indicated by the upward slope D2. Buffer current supply start control for gradually increasing the current value from the increased jump limit supply current value Iz to the specified supply current value Ix is performed. When the buffer current supply start control is performed, the valve opening of the capacity control valve 39 instantaneously changes to the valve opening corresponding to the increased jump limit supply current value Iz and then gradually decreases. The pressure in the chamber 121 gradually decreases in a state that follows a slow increase in the supply current value from the increased jump limit supply current value Iz. As the pressure in the control pressure chamber 121 slowly decreases, the inclination angle of the swash plate 20 gradually increases from the minimum inclination angle as shown by the upward inclination portion H1 in the curve H in FIG. It will increase. The slow inclination angle increase of the swash plate 20 is performed in a state of following a slow decrease in the supply current value from the increase jump limit supply current value Iz. When the inclination angle of the swash plate 20 increases from the minimum inclination angle, the refrigerant circulation in the external refrigerant circuit 33 is performed, and the suction pressure decreases. A flat part Q1 in the curve Q in FIG. 8 represents the suction pressure before the air conditioner operation switch 44 is turned on, and a downward inclined part Q2 in the curve Q is accompanied by a slow increase in inclination from the minimum inclination of the swash plate 20. Represents fluctuations in suction pressure.
[0047]
When the supply current value becomes the designated supply current value Ix, the swash plate 20 moves to the tilt position corresponding to the designated supply current value Ix, and the suction pressure converges to the suction pressure corresponding to the designated supply current value Ix. A flat portion Q3 in the curve Q of FIG. 8 represents the suction pressure corresponding to the designated supply current value Ix.
[0048]
When the air conditioner operation switch 44 is turned off, a current supply stop command signal S2 is output to the control computer C2 as shown in FIG. The control computer C2 serving as a buffering current supply stop control means responds to the input of the current supply stop command signal S2 and the detection control obtained from the specified supply current value when the air conditioner operation switch 44 is OFF and the pressure detector 52. Decrease jump limit supply current value Iw is determined based on the pressure and (control pressure-supply current value) map. The (control pressure-supply current value) map is a map for obtaining a decrease jump limit supply current value Iw using the control pressure and the supply current value as variables.
The control computer C2 discontinuously changes the supply current value from the designated supply current value Iy immediately before the air conditioner operation switch 44 is turned OFF to the reduced jump limit supply current value Iw, as indicated by the vertical line D3 in the curve D of FIG. Next, buffer current supply stop control is performed to gradually decrease the supply current value from the reduced jump limit supply current value Iw to zero as indicated by the downward slope D4. When the buffer current supply stop control is performed, the valve opening of the capacity control valve 39 is instantaneously changed to the valve opening corresponding to the reduced jump limit supply current value Iw and then gradually increased. The pressure in the chamber 121 gradually increases in a state that follows a slow decrease in the supply current value from the decrease jump limit supply current value Iw. As the pressure in the control pressure chamber 121 rises slowly, the inclination angle of the swash plate 20 gradually decreases from the inclination angle when the current supply stop command signal S2 is input, as indicated by the downward inclination portion H2 of the curve H in FIG. I will do it. When the tilt angle of the swash plate 20 decreases from the tilt angle when the current supply stop command signal S2 is input, the discharge capacity decreases and the suction pressure increases. The flat part Q4 in the curve Q in FIG. 8 represents the suction pressure before the air conditioner operation switch 44 is turned off, and the upward inclined part Q5 in the curve Q is when the current supply stop command signal S2 of the swash plate 20 is input. Represents fluctuations in suction pressure associated with a slow decrease in tilt angle.
[0049]
When the supply current value becomes zero, the swash plate 20 moves to the minimum inclination position and the refrigerant circulation in the external refrigerant circuit 33 stops. A flat portion Q6 in the curve Q in FIG. 8 represents the suction pressure after the refrigerant circulation is stopped in the external refrigerant circuit 33.
[0050]
In the second embodiment, the following effects can be obtained.
(2-1) When the current supply to the electric capacity control valve 39 is started by the ON operation of the air conditioner operation switch 44, the control computer C2 constituting the increase jump limit supply current value specifying means together with the pressure detector 51 detects Specify the increase jump limit supply current value according to the suction pressure. Then, the control computer C2 discontinuously increases the supply current value from zero to the increased jump limit supply current value Iz, and then gradually increases the supply current value from the increase jump limit supply current value Iz to the specified supply current value. The buffer current supply start control is increased. The increased jump limit supply current value Iz is a limit value of a discontinuous increase amount from zero of the supply current value that does not cause a collision between the swash plate 20 and the rotary support 19, and depends on the suction pressure. . That is, when the supply current value is discontinuously increased from zero to a value higher than the increased jump limit supply current value Iz corresponding to the detected suction pressure, the swash plate 20 collides with the rotary support 19 and the collision sound Occurs. When the supply current value is discontinuously increased from zero to the increased jump limit supply current value Iz, the inclination of the swash plate 20 from the minimum inclination is rapidly increased without causing a collision sound, and the capacity is restored. Promptly.
[0051]
(2-2) When the current supply to the electric capacity control valve 39 is stopped by the OFF operation of the air conditioner operation switch 44, the control computer C2 that constitutes the decrease jump limit supply current value designation means together with the pressure detector 52 detects Specify the decrease jump limit supply current value according to the control pressure. Then, the control computer C2 discontinuously decreases the supply current value from the designated supply current value immediately before the air conditioner operation switch 44 is turned off to the decrease jump limit supply current value Iw, and then supplies from the decrease jump limit supply current value Iw. Buffer current supply stop control is performed to gradually decrease the supply current value until the current value becomes zero. The decrease jump limit supply current value Iw is a limit value of a discontinuous decrease amount from the specified supply current value Iy that does not cause the collision between the blocking body 22 and the valve forming plate 15, and depends on the detection control pressure. The That is, when the supply current value is discontinuously decreased from the specified supply current value Iy to a value lower than the decrease jump limit supply current value Iw corresponding to the detected control pressure, the blocking body 22 collides with the valve forming plate 15. A collision sound is generated. When the supply current value is discontinuously decreased from the specified supply current value Iy to the decrease jump limit supply current value Iw, the transition of the swash plate 20 to the minimum inclination position is promptly performed without causing a collision sound. .
[0052]
Next, a third embodiment of FIGS. 9 and 10 will be described. The same components as those in the first embodiment are denoted by the same reference numerals.
In this embodiment, when the solenoid 531 of the electric capacity control valve 53 is excited, the valve body 532 closes the valve hole 533 and the swash plate 20 moves to the maximum tilt position. When the solenoid 531 is demagnetized, the valve body 532 moves to the maximum valve opening position, and the swash plate 20 moves to the minimum tilt position. When the air conditioner operation switch 44 serving as a current supply start command unit and a current supply stop command unit is turned on, the control computer C3 excites the solenoid 531. If the air conditioner operation switch 44 is turned off while the solenoid 531 is energized, the control computer C3 demagnetizes the solenoid 531. When the air conditioner operation switch 44 is in the ON state, the control computer C3 commands the demagnetization of the solenoid 531 when the detected temperature obtained by the room temperature detector 46 falls below the target room temperature set by the room temperature setter 45. The control computer C3 commands excitation of the solenoid 531 when the detected temperature exceeds the target room temperature. The room temperature detector 46 and the control computer C3 constitute current supply start command means and current supply stop command means.
[0053]
When the solenoid 531 is excited, the control computer C3 performs the buffer current supply start control indicated by the upward slope portion F1 of the curve F in FIG. The maximum value of the supply current value is the designated supply current value. Signal S3 represents a current supply start command when the air conditioner operation switch 44 is turned on or when the detected temperature exceeds the target room temperature. The ascending slope portion G1 of the curve G represents an increase in the tilt angle of the swash plate 20 as the supply current value increases, and the descending slope portion R1 of the curve R represents a decrease in the suction pressure as the tilt angle of the swash plate 20 increases.
[0054]
When the solenoid 531 is demagnetized, the control computer C3 performs the buffer current supply stop control indicated by the downward slope F2 of the curve F in FIG. The signal S4 represents a current supply stop command when the air conditioner operation switch 44 is turned off or when the detected temperature is equal to or lower than the target room temperature. A downwardly inclined portion G2 of the curve G represents a decrease in the inclination angle of the swash plate 20 as the supply current value decreases, and an upward inclined portion R2 of the curve R represents an increase in the suction pressure accompanying a decrease in the inclination angle of the swashplate 20.
[0055]
Also in this embodiment, the increasing speed of the inclination of the swash plate 20 at the maximum inclination position of the swash plate 20 is suppressed, and the collision between the swash plate 20 and the rotary support 19 is suppressed. In addition, the rate of decrease in the inclination of the swash plate 20 at the minimum inclination position of the swash plate 20 is suppressed, and the collision between the blocking body 22 and the valve forming plate 15 is suppressed.
[0056]
In the present invention, the following embodiments are also possible.
(1) In the first embodiment, at the start of current supply, the supply current value is continuously increased from zero to the maximum value or near the maximum value so as to suppress the inclination increase speed at the maximum inclination position of the swash plate 20. Later, continuously reduce to the specified supply current value. In this way, the capacity recovery is accelerated.
(2) The present invention is applied to a variable displacement compressor in which a displacement control valve is interposed on a passage for extracting the refrigerant from the control pressure chamber to the suction pressure region.
(3) The duty ratio of the supply current value is controlled. In this case, the average supply current value per unit time is regarded as the supply current value.
(4) The present invention is applied to a variable displacement compressor with a clutch that transmits a driving force from an external drive source to a rotating shaft via a clutch.
[0057]
【The invention's effect】
As described above in detail, when the current supply to the electric capacity control valve is started, in order to suppress the inclination increase speed at the maximum inclination position of the swash plate as a process until the supply of the designated supply current value is started. In the invention for performing the buffer current supply start control, the unnecessary arrival of the swash plate at the maximum tilt position is avoided to avoid the generation of a collision sound, and the collision when the swash plate reaches the maximum tilt position. There is an excellent effect that the sound can be suppressed.
[0058]
When the current supply to the electric capacity control valve is stopped, the buffer current supply stop control is performed to suppress the inclination reduction rate at the minimum inclination position of the swash plate as a process until the supply current value becomes zero. In the invention made in this way, there is an excellent effect that it is possible to suppress a collision sound when the swash plate comes to the minimum inclination position.
[Brief description of the drawings]
FIG. 1 is a side sectional view of an entire compressor showing a first embodiment.
FIG. 2 is a longitudinal sectional view of an electric capacity control valve 39;
FIG. 3 is a side cross-sectional view of a main part in a state where a swash plate tilt angle is in a minimum state.
4 is a cross-sectional view taken along line AA in FIG.
FIG. 5 is a sectional view taken along line BB in FIG. 1;
FIG. 6 is a graph showing a relationship between a supply current value, a swash plate inclination angle, and a suction pressure.
FIG. 7 is a side sectional view of the whole compressor showing a second embodiment.
FIG. 8 is a graph showing the relationship between the supply current value, the swash plate tilt angle, and the suction pressure.
FIG. 9 is a side sectional view of the whole compressor showing a third embodiment.
FIG. 10 is a graph showing the relationship between the supply current value, the swash plate tilt angle, and the suction pressure.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 121 ... Control pressure chamber, 131 ... Suction chamber used as a suction pressure area, 132 ... Discharge chamber used as a discharge pressure area, 18 ... Rotating shaft, 20 ... Swash plate, 38 ... Refrigerant supply passage, 39 ... Electric capacity control valve, 44... Air conditioner operation switch serving as current supply start command means and current supply stop command means, C1... Control computer serving as buffer current supply start control means, buffer current supply stop control means and supply current value designating means, C2. Buffer current supply start control means, buffer current supply stop control means, supply current value designation means, increase jump limit supply current value designation means, and control computer to be a decrease jump limit supply current value designation means, C3... Buffer current A control computer serving as supply start control means and buffer current supply stop control means.

Claims

回転軸と一体的に回転するように、かつ前記回転軸に対して傾角可変に制御圧室に収容された斜板、及び前記斜板の傾角に応じた往復動作を行なうピストンを備え、吐出圧領域から前記制御圧室へ冷媒を供給すると共に、前記制御圧室から吸入圧領域へ冷媒を抜き出し、前記吐出圧領域から前記制御圧室に至る冷媒供給通路上又は前記制御圧室から前記吸入圧領域に至る冷媒抜き出し通路上に電気式容量制御弁を介在し、前記電気式容量制御弁に対する供給電流値を制御して前記吐出圧領域から前記制御圧室への冷媒供給量又は前記制御圧室から前記吸入圧領域への冷媒抜き出し量を制御し、前記制御圧室内の圧力の制御に基づいて前記斜板の傾角を制御する可変容量型圧縮機において、
前記電気式容量制御弁に対する電流供給を開始するときには、指定された供給電流値を供給開始するまでの過程として前記斜板の最大傾角位置での傾角増大速度を抑制するための緩衝用電流供給開始制御を行ない、
前記緩衝用電流供給開始制御は、供給電流値零から指定された指定供給電流値まで供給電流値を増大するものであって、供給電流値零から前記指定供給電流値に達しない増大飛躍限界供給電流値へ供給電流値を不連続的に切り換える供給電流値切り換え状態と、前記増大飛躍限界供給電流値から前記指定供給電流値まで供給電流値を徐々に増大する電流増大供給状態とを含む可変容量型圧縮機における容量制御方法。A swash plate that is housed in a control pressure chamber so as to rotate integrally with the rotation shaft and that can be tilted with respect to the rotation shaft; The refrigerant is supplied from the region to the control pressure chamber, the refrigerant is extracted from the control pressure chamber to the suction pressure region, and the suction pressure is supplied from the discharge pressure region to the control pressure chamber or from the control pressure chamber. An electric capacity control valve is interposed on the refrigerant extraction passage leading to the region, and the supply current value to the electric capacity control valve is controlled to supply the refrigerant supply amount from the discharge pressure region to the control pressure chamber or the control pressure chamber A variable displacement compressor that controls the amount of refrigerant extracted from the suction pressure region to the suction pressure region and controls the tilt angle of the swash plate based on the control of the pressure in the control pressure chamber;
When the current supply to the electric capacity control valve is started, the buffer current supply is started to suppress the tilt increase speed at the maximum tilt position of the swash plate as a process until the specified supply current value is started. It has control of the row,
The buffer current supply start control increases the supply current value from a supply current value of zero to a specified supply current value, and does not reach the specified supply current value from the supply current value of zero. A variable capacitor including a supply current value switching state that switches the supply current value to a current value discontinuously, and a current increase supply state that gradually increases the supply current value from the increased jump limit supply current value to the specified supply current value Capacity control method in a type compressor.

回転軸と一体的に回転するように、かつ前記回転軸に対して傾角可変に制御圧室に収容された斜板、及び前記斜板の傾角に応じた往復動作を行なうピストンを備え、吐出圧領域から前記制御圧室へ冷媒を供給すると共に、前記制御圧室から吸入圧領域へ冷媒を抜き出し、前記吐出圧領域から前記制御圧室に至る冷媒供給通路上又は前記制御圧室から前記吸入圧領域に至る冷媒抜き出し通路上に電気式容量制御弁を介在し、前記電気式容量制御弁に対する供給電流値を制御して前記吐出圧領域から前記制御圧室への冷媒供給量又は前記制御圧室から前記吸入圧領域への冷媒抜き出し量を制御し、前記制御圧室内の圧力の制御に基づいて前記斜板の傾角を制御する可変容量型圧縮機において、  A swash plate that is housed in a control pressure chamber so as to rotate integrally with the rotary shaft and that can be tilted with respect to the rotary shaft, and a piston that performs reciprocating operation according to the tilt angle of the swash plate, The refrigerant is supplied from the region to the control pressure chamber, the refrigerant is extracted from the control pressure chamber to the suction pressure region, and the suction pressure from the discharge pressure region to the control pressure chamber or from the control pressure chamber. An electric capacity control valve is interposed on the refrigerant extraction passage leading to the region, and a supply current value to the electric capacity control valve is controlled to supply a refrigerant supply amount from the discharge pressure region to the control pressure chamber or the control pressure chamber A variable displacement compressor that controls the amount of refrigerant extracted from the suction pressure region to the suction pressure region and controls the tilt angle of the swash plate based on the control of the pressure in the control pressure chamber;
前記電気式容量制御弁に対する電流供給を停止するときには、供給電流値を零とするまでの過程として前記斜板の最小傾角位置での傾角減少速度を抑制するための緩衝用電流供給停止制御を行ない、  When stopping the current supply to the electric capacity control valve, a buffer current supply stop control is performed to suppress the rate of inclination decrease at the minimum inclination position of the swash plate as a process until the supply current value becomes zero. ,
前記緩衝用電流供給停止制御は、指定された指定供給電流値から供給電流値零まで供給電流値を減少するものであって、前記指定供給電流値から前記指定供給電流値に達しない減少飛躍限界供給電流値へ供給電流値を不連続的に切り換える供給電流値切り換え状態と、前記減少飛躍限界供給電流値から供給電流値零まで供給電流値を徐々に減少する電流減少供給状態とを含む可変容量型圧縮機における容量制御方法。  The buffer current supply stop control is to reduce a supply current value from a designated designated supply current value to a supply current value of zero, and a decrease jump limit that does not reach the designated supply current value from the designated supply current value A variable capacity including a supply current value switching state that switches the supply current value to a supply current value discontinuously, and a current reduction supply state that gradually decreases the supply current value from the reduced jump limit supply current value to the supply current value of zero Capacity control method in a type compressor.

回転軸と一体的に回転するように、かつ前記回転軸に対して傾角可変に制御圧室に収容された斜板、及び前記斜板の傾角に応じた往復動作を行なうピストンを備え、吐出圧領域から前記制御圧室へ冷媒を供給すると共に、前記制御圧室から吸入圧領域へ冷媒を抜き出し、前記吐出圧領域から前記制御圧室に至る冷媒供給通路上又は前記制御圧室から前記吸入圧領域に至る冷媒抜き出し通路上に電気式容量制御弁を介在し、前記電気式容量制御弁に対する供給電流値を制御して前記吐出圧領域から前記制御圧室への冷媒供給量又は前記制御圧室から前記吸入圧領域への冷媒抜き出し量を制御し、前記制御圧室内の圧力の制御に基づいて前記斜板の傾角を制御する可変容量型圧縮機において、  A swash plate that is housed in a control pressure chamber so as to rotate integrally with the rotary shaft and that can be tilted with respect to the rotary shaft, and a piston that performs reciprocating operation according to the tilt angle of the swash plate, The refrigerant is supplied from the region to the control pressure chamber, the refrigerant is extracted from the control pressure chamber to the suction pressure region, and the suction pressure from the discharge pressure region to the control pressure chamber or from the control pressure chamber. An electric capacity control valve is interposed on the refrigerant extraction passage leading to the region, and a supply current value to the electric capacity control valve is controlled to supply a refrigerant supply amount from the discharge pressure region to the control pressure chamber or the control pressure chamber A variable displacement compressor that controls the amount of refrigerant extracted from the suction pressure region to the suction pressure region and controls the tilt angle of the swash plate based on the control of the pressure in the control pressure chamber;
前記電気式容量制御弁に対する電流供給の開始を指令する電流供給開始指令手段と、  Current supply start command means for commanding start of current supply to the electric capacity control valve;
前記斜板の最大傾角位置での傾角増大速度を抑制するための緩衝用電流供給開始制御を行なう緩衝用電流供給開始制御手段と、  Buffer current supply start control means for performing buffer current supply start control for suppressing the tilt increase speed at the maximum tilt position of the swash plate;
供給電流値を指定する供給電流値指定手段と、  Supply current value specifying means for specifying a supply current value;
前記指定供給電流値に達しない増大飛躍限界供給電流値を指定する増大飛躍限界供給電流値指定手段とを備え、  An increased jump limit supply current value specifying means for specifying an increased jump limit supply current value that does not reach the specified supply current value;
前記緩衝用電流供給開始制御手段は、前記電流供給開始指令手段の電流供給開始指令に基づいて前記緩衝用電流供給開始制御を行ない、前記供給電流値指定手段によって指定された指定供給電流値まで供給電流値零から供給電流値を増大するものであって、供給電流値零から前記増大飛躍限界供給電流値指定手段によって指定された増大飛躍限界供給電流値へ供給電流値を不連続的に切り換え、前記増大飛躍限界供給電流値から前記指定供給電流値まで供給電流値を徐々に増大する電流供給開始制御を行なう可変容量型圧縮機における容量制御装置。  The buffer current supply start control means performs the buffer current supply start control based on the current supply start command of the current supply start command means, and supplies up to the designated supply current value designated by the supply current value designation means The supply current value is increased from zero current value, the supply current value is discontinuously switched from the supply current value zero to the increased jump limit supply current value specified by the increase jump limit supply current value specifying means, A capacity control device in a variable capacity compressor that performs current supply start control for gradually increasing a supply current value from the increase jump limit supply current value to the specified supply current value.

回転軸と一体的に回転するように、かつ前記回転軸に対して傾角可変に制御圧室に収容された斜板、及び前記斜板の傾角に応じた往復動作を行なうピストンを備え、吐出圧領域から前記制御圧室へ冷媒を供給すると共に、前記制御圧室から吸入圧領域へ冷媒を抜き出し、前記吐出圧領域から前記制御圧室に至る冷媒供給通路上又は前記制御圧室から前記吸入圧領域に至る冷媒抜き出し通路上に電気式容量制御弁を介在し、前記電気式容量制御弁に対する供給電流値を制御して前記吐出圧領域から前記制御圧室への冷媒供給量又は前記制御圧室から前記吸入圧領域への冷媒抜き出し量を制御し、前記制御圧室内の圧力の制御に基づいて前記斜板の傾角を制御する可変容量型圧縮機において、  A swash plate that is housed in a control pressure chamber so as to rotate integrally with the rotary shaft and that can be tilted with respect to the rotary shaft, and a piston that performs reciprocating operation according to the tilt angle of the swash plate, The refrigerant is supplied from the region to the control pressure chamber, the refrigerant is extracted from the control pressure chamber to the suction pressure region, and the suction pressure from the discharge pressure region to the control pressure chamber or from the control pressure chamber. An electric capacity control valve is interposed on the refrigerant extraction passage leading to the region, and a supply current value to the electric capacity control valve is controlled to supply a refrigerant supply amount from the discharge pressure region to the control pressure chamber or the control pressure chamber A variable displacement compressor that controls the amount of refrigerant extracted from the suction pressure region to the suction pressure region and controls the tilt angle of the swash plate based on the control of the pressure in the control pressure chamber;
前記電気式容量制御弁に対する電流供給の停止を指令する電流供給停止指令手段と、  Current supply stop command means for commanding stop of current supply to the electric capacity control valve;
前記斜板の最小傾角位置での傾角減少速度を抑制するための緩衝用電流供給停止制御を行なう緩衝用電流供給停止制御手段と、  Buffer current supply stop control means for performing buffer current supply stop control for suppressing the tilt decrease rate at the minimum tilt position of the swash plate;
供給電流値を指定する供給電流値指定手段と、  Supply current value specifying means for specifying a supply current value;
減少飛躍限界供給電流値を指定する減少飛躍限界供給電流値指定手段とを備え、  With a decrease leap limit supply current value specifying means for specifying a decrease leap limit supply current value,
前記緩衝用電流供給停止制御手段は、前記電流供給停止指令手段の電流供給停止指令に基づいて前記緩衝用電流供給停止制御を行ない、前記供給電流値指定手段によって指定された指定供給電流値から供給電流値零まで供給電流値を減少するものであって、前記指定供給電流値から前記減少飛躍限界供給電流値指定手段によって指定された減少飛躍限界供給電流値へ供給電流値を不連続的に切り換え、前記減少飛躍限界供給電流値から供給電流値零まで供給電流値を徐々に減少する電流供給停止制御を行なう可変容量型圧縮機における容量制御装置。  The buffer current supply stop control means performs the buffer current supply stop control based on the current supply stop command of the current supply stop command means, and supplies from the designated supply current value designated by the supply current value designation means The supply current value is reduced to zero current value, and the supply current value is discontinuously switched from the specified supply current value to the decrease jump limit supply current value specified by the decrease jump limit supply current value specifying means. A capacity control device in a variable capacity compressor that performs current supply stop control for gradually decreasing the supply current value from the decrease jump limit supply current value to the supply current value of zero.