JP4221823B2

JP4221823B2 - Receiver integrated refrigerant condenser

Info

Publication number: JP4221823B2
Application number: JP16989499A
Authority: JP
Inventors: 弘樹松尾; 一哉牧薗; 哲滋信田
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 1998-06-16
Filing date: 1999-06-16
Publication date: 2009-02-12
Anticipated expiration: 2019-06-16
Also published as: JP2000074527A

Description

【０００１】
【発明の属する技術分野】
本発明は、冷媒の気液を分離して液冷媒を蓄える受液器を一体に構成した冷媒凝縮器において、受液器への冷媒充填特性の改善に関するもので、車両用空調装置に用いて好適なものである。
【０００２】
【従来の技術】
従来、車両用空調装置においては、車両搭載性の向上を図るために、冷媒凝縮器に受液器を一体に構成して、この冷媒凝縮器と受液器の車両搭載スペースを縮小するようにしたものが種々提案されている（例えば、特開平８−２１９５８８号公報参照）。
【０００３】
この従来技術における冷媒凝縮器は、一般にマルチフロータイプと称されているものであって、図７に示すように、上下方向に配置された一対のヘッダタンク２１、２２を有し、この一対のヘッダタンク２１、２２の間に、水平方向に冷媒を流すチューブ２４を有するコア部２３を配置し、一方の（第１）ヘッダタンク２１の上端側に冷媒の入口側配管ジョイント２６を、下端側に冷媒の出口側配管ジョイント２７をそれぞれ配置している。
【０００４】
そして、両方のヘッダタンク２１、２２内に配置したセパレータ２８ａ、２８ｂ、２９ａ、２９ｂによりヘッダタンク２１、２２内部をそれぞれ上下方向に複数の空間２１ａ〜２１ｃ、２２ａ〜２２ｃに仕切っている。これにより、入口側配管ジョイント２６からの冷媒（圧縮機吐出ガス）を一対のヘッダタンク２１、２２とコア部２３との間で図示の矢印のごとく蛇行状に流通させるようにしている。
【０００５】
また、一対のヘッダタンク２１、２２のうち、冷媒の出入口配管ジョイント２６、２７を設けてない側の第２ヘッダタンク２２に受液器３１を一体に構成し、この受液器３１内部の空間と第２ヘッダタンク２２とをヘッダタンク下方側の部位に設けた第１の連通穴３２にて連通させ、コア部２３の凝縮部３６にて凝縮した液冷媒を第１の連通穴３２を通して受液器３１内部に流入させ、受液器３１内部において冷媒の気液を分離して液冷媒を蓄える。
【０００６】
そして、第１の連通穴３２よりも下方の部位に第２の連通穴３５を配置するとともに、この第１の連通穴３２と第２の連通穴３５との間を仕切るセパレータ２９ｂを第２ヘッダタンク２２内に配置している。これにより、受液器３１内部の液冷媒を第２の連通穴３５から第２ヘッダタンク２２の最下部の空間２２ｃ内に流入させ、さらにコア部２３の過冷却部３７を経て液冷媒を過冷却した後に、第１ヘッダタンク２１の最下部の空間２１ｃを経て過冷却液冷媒を出口側配管ジョイント２７から外部へ流出させている。
【０００７】
【発明が解決しようとする課題】
ところで、上記従来技術について実際に試作検討して、冷凍サイクル内（具体的には、受液器３１内）への冷媒充填特性を評価してみると、冷凍サイクル効率化のために要望される理想通りの冷媒充填特性が得られにくいことが判明した。
【０００８】
図３は冷媒凝縮器２の出口側配管ジョイント２７から流出した液冷媒のサブクール（過冷却度）を縦軸にとり、出口側配管ジョイント２７下流部に設けられるサイトグラス（図１の符号３参照）にて冷媒中から気泡（ガス冷媒）が消滅した時点（泡消点）以降におけるサイクル内への冷媒封入増加分を横軸にとったものである。なお、実験条件としては、冷凍サイクルの圧縮機を駆動する車両エンジン回転数＝１５００ｒｐｍ、外気温度＝３０°Ｃ、空調用室内ファン速度＝最高速（Ｈｉ）設定→風量＝４５０ｍ³／ｈである。
【０００９】
車両用空調装置の冷凍サイクルの場合、将来、冷媒漏れが多少発生しても、冷房性能への影響がないように、冷媒封入量は、通常、泡消点以降、１００ｇ程度の冷媒増加分を追加するように設計しており、そして、この追加分の規定値（泡消点以降の１００ｇの冷媒増加分）には、冷媒封入作業のバラツキを考慮してある程度の範囲の公差を設けている。
【００１０】
従って、図３の特性Ａのように泡消点以降、８０ｇ〜１８０ｇの冷媒封入量の増加分範囲においては、サブクールが略一定値に維持される領域を設定して、この増加分範囲では、サブクールの増加によるサイクル高圧の上昇を防止して、圧縮機動力の増加を抑制することが望まれている。
【００１１】
ところで、上記従来技術の冷媒充填特性を実験検討してみると、図３の従来品▲２▼のごとく受液器３１に冷却風を十分当てた場合は、上記のＡの理想的な冷媒充填特性を得ることができるが、図３の従来品▲１▼のごとく受液器３１を断熱材にて断熱した場合は、Ｂの特性に示すように、泡消点以降、冷媒封入量を増加すると、これに伴って、液冷媒のサブクールが連続的に増加してしまうことが分かった。
【００１２】
このため、冷媒充填特性Ｂでは、泡消点以降、僅かな冷媒量の追加によって過充填サイクル状態となり、高圧上昇による圧縮機動力の増加を招くという問題が発生する。
【００１３】
なお、車両エンジンルームのフロントグリルの冷却風入口部の横幅寸法には、車両デザイン等の面から制約があるので、車両への実際の搭載状態では、受液器３１をフロントグリルの冷却風入口部横幅寸法の範囲外に配置せざるを得ない場合が多々発生する。この結果、受液器３１への冷却風の送風をほとんど期待できない状態となり、図３の従来品▲１▼に近似した使用状態が発生することになる。
【００１４】
そこで、本発明は上記点に鑑み、受液器一体型冷媒凝縮器において、泡消点以降における冷媒封入量の増加分に対して、所定範囲にわたって冷媒サブクールを略一定値に維持できる冷媒充填特性を設定できるようにすることを目的とする。
【００１５】
【課題を解決するための手段】
まず、最初に、従来技術において図３のＢに示す冷媒充填特性になってしまう原因について述べると、従来技術では、凝縮部３６での冷媒流れのターン数を増やして凝縮能力を向上するために、受液器３１が一体化される第２ヘッダタンク２２内部を、セパレータ２９ａ、２９ｂにより上下方向に仕切っている。このため、上側の空間２２ａに比して中間部の空間２２ｂでは凝縮部３６での冷媒流路抵抗により圧力が低くなるので、上側の空間２２ａではその圧力差分だけ、冷媒温度が中間部空間２２ｂより高くなる。例えば、上側の空間２２ａの圧力＝１．５０ＭＰａ（冷媒飽和温度＝５５．３°Ｃ）のとき、中間部空間２２ｂでは、圧力＝１．４５ＭＰａ（冷媒飽和温度＝５３．９°Ｃ）となり、上側の空間２２ａより１．４°Ｃ低い温度となる。
【００１６】
そして、受液器３１への冷却空気の送風が不十分であると、第２ヘッダタンク２２と受液器３１との間はアルミニュウム等の熱伝導性に優れた金属の薄板で仕切られているだけであるので、第２ヘッダタンク２２からの熱伝導により受液器３１においても上下方向に温度差が発生する。すなわち、受液器３１内へ第１の連通穴３２から流入してくる冷媒の温度に比して、受液器３１内上部の冷媒温度が高くなる。
【００１７】
ところで、受液器３１は、本来、サイクル中の余剰冷媒の蓄積機能を受持ち、サイクルからの冷媒漏れに対応するものであって、受液器３１内に液冷媒が溜まり始めてから、液冷媒が受液器３１よりオーバーフローするまでの間は、サイクルの挙動に変化が生じないようにしている。
【００１８】
しかし、サイクル内への冷媒封入時に、泡消点以降、さらに冷媒封入量を増加していくと、受液器３１内での冷媒液面が次第に上昇していき、セパレータ２９ａの高さを越えると、上記理由から第２ヘッダタンク２２内部の上側空間２２ａからの熱伝導により受液器３１内の液冷媒がガス化して、セパレータ２９ａの位置より上方へは液冷媒が上昇しずらいという現象が発生する。
【００１９】
このように、受液器３１内において液冷媒の上昇が困難になると、冷媒封入時にそれ以降追加された冷媒は受液器３１内に蓄積できないので、行き場がなくなって、凝縮器２のコア部２３内に液冷媒がオーバーフローし、前述の特性Ｂとなることが判明した。
【００２０】
このような原因解明に基づいて、本発明では、ヘッダタンク（２２）内の上部空間（２２ａ）内の高温冷媒の熱が受液器（３１）内の液冷媒に伝導するのを抑制できる構成とすることにより、前述の目的を達成しようとするものである。
【００２１】
すなわち、請求項１記載の発明では、コア部（２３）の一端側に配置される第１ヘッダタンク（２１）と、コア部（２３）の他端側に配置される第２ヘッダタンク（２２）とのいずれか一方に、受液器（３１）を一体に構成する受液器一体型冷媒凝縮器において、
一方のヘッダタンク（２２）内に、その内部空間を上下方向に仕切るセパレータ（２９ａ）を配置し、
受液器（３１）はセパレータ（２９ａ）の上下両側にわたる高さ寸法を有しており、
受液器（３１）内における冷媒の気液界面は、冷媒封入量の正常時にはセパレータ（２９ａ）と受液器（３１）の上端面との中間高さに位置するようになっており、
一方のヘッダタンク（２２）と受液器（３１）とが対向する箇所に、セパレータ（２９ａ）の上下両側にわたって延びる連通路（３０）を形成し、
連通路（３０）のうち、セパレータ（２９ａ）の下側部位を受液器（３１）内部の下側部位に連通させる下側連通穴（３３）、および連通路（３０）のうち、セパレータ（２９ａ）の上側部位を受液器（３１）内部の上側部位に連通させる上側連通穴（３４）を受液器（３１）に設け、
一方のヘッダタンク（２２）の内部空間のうちセパレータ（２９ａ）下側の空間（２２ｂ）にはコア部（２３）で凝縮した冷媒が流入するとともに、一方のヘッダタンク（２２）の内部空間のうちセパレータ（２９ａ）の上側空間（２２ａ）には、セパレータ（２９ａ）下側の空間（２２ｂ）よりも上流側部位の温度の高い冷媒が流入するようになっており、
連通路（３０）内には、コア部（２３）で凝縮した冷媒が、セパレータ（２９ａ）下側の空間（２２ｂ）を経由して流入するようになっており、
さらに、連通路（３０）内の冷媒を下側連通穴（３３）および上側連通穴（３４）を介して連通路（３０）の上下両側から受液器（３１）内に流入させるようになっており、
下側連通穴（３３）からの冷媒は、受液器（３１）内の冷媒気液界面よりも下方の液冷媒中に流入するようになっており、
連通路（３０）のうち、セパレータ（２９ａ）の上側部位は、一方のヘッダタンク（２２）の内部空間のうちセパレータ（２９ａ）の上側空間（２２ａ）と受液器（３１）の上側内部空間との間に介在される低温冷媒通路を構成することを特徴としている。
【００２２】
これによると、コア部（２３）で凝縮した冷媒が連通路（３０）を通って、この連通路（３０）の上下両側から受液器（３１）内に流入するから、セパレータ（２９ａ）の上側空間（２２ａ）内の温度の高い冷媒雰囲気と、受液器（３１）との間に、連通路（３０）による温度の低い冷媒雰囲気を介在させることができる。
【００２３】
これにより、一方のヘッダタンク（２２）の上部空間（２２ａ）内部の温度の高い冷媒の熱が受液器（３１）内部の冷媒に伝導するのを抑制することができる。従って、受液器（３１）に冷却風を十分送風できない場合においても、受液器（３１）内部での液冷媒のガス化を良好に抑制でき、受液器（３１）の容積を液冷媒の蓄積のために有効に使用できる。
【００２４】
この結果、一方のヘッダタンク（２２）内に、その内部空間を上下方向に仕切るセパレータ（２９ａ）を配置し、受液器（３１）をセパレータ（２９ａ）の上下両側にわたって配置するタイプの、受液器一体型冷媒凝縮器においても、泡消点以降における冷媒封入量の増加分に対して、所定範囲にわたって冷媒サブクールを略一定値に維持できる冷媒充填特性（図３のＡ特性）を設定できる。よって、過充填サイクル状態の発生に起因する圧縮機動力の増加といった不具合を確実に防止できる。
【００２５】
請求項２記載の発明のように、請求項１に記載の受液器一体型冷媒凝縮器において、セパレータ（２９ａ）下側の空間（２２ｂ）を連通路（３０）に連通させる連通穴（３２）を、下側連通穴（３３）より上方側であって、かつ、上側連通穴（３４）よりも下方側に設ければよい。
また、請求項３記載の発明では、コア部（２３）の一端側に配置される第１ヘッダタンク（２１）と、コア部（２３）の他端側に配置される第２ヘッダタンク（２２）とのいずれか一方に、受液器（３１）を一体に構成する受液器一体型冷媒凝縮器において、
コア部（２３）の上側部にて冷媒を凝縮する凝縮部（３６）を構成するとともに、コア部（２３）の下側部にて冷媒を過冷却する過冷却部（３７）を構成し、
受液器（３１）と一体に構成される一方のヘッダタンク（２２）内に上側および下側の少なくとも２枚のセパレータ（２９ａ、２９ｂ）を配置し、
この２枚のセパレータ（２９ａ、２９ｂ）により一方のヘッダタンク（２２）内を上下方向に３つの空間（２２ａ、２２ｂ、２２ｃ）に仕切り、
受液器（３１）は上側セパレータ（２９ａ）の上下両側にわたる高さ寸法を有しており、
受液器（３１）内における冷媒の気液界面は、冷媒封入量の正常時には上側セパレータ（２９ａ）と受液器（３１）の上端面との中間高さに位置するようになっており、
一方のヘッダタンク（２２）と受液器（３１）とが対向する箇所に、上側セパレータ（２９ａ）の上下両側にわたって延びる連通路（３０）を形成し、
連通路（３０）のうち、上側セパレータ（２９ａ）の下側部位を受液器（３１）内部の下側部位に連通させる下側連通穴（３３）、および連通路（３０）のうち、上側セパレータ（２９ａ）の上側部位を受液器（３１）内部の上側部位に連通させる上側連通穴（３４）を受液器（３１）に設け、
一方のヘッダタンク（２２）の内部空間のうち上側セパレータ（２９ａ）と下側セパレータ（２９ｂ）との間の中間部空間（２２ｂ）には凝縮部（３６）で凝縮した冷媒が流入するとともに、一方のヘッダタンク（２２）の内部空間のうち上側セパレータ（２９ａ）の上側空間（２２ａ）には、中間部空間（２２ｂ）よりも上流側部位の温度の高い冷媒が流入するようになっており、
連通路（３０）内には、凝縮部（３６）で凝縮した冷媒が、中間部空間（２２ｂ）を経由して流入するようになっており、
さらに、連通路（３０）内の冷媒を下側連通穴（３３）および上側連通穴（３４）を介して連通路（３０）の上下両側から受液器（３１）内に流入させるようになっており、
下側連通穴（３３）からの冷媒は、受液器（３１）内の冷媒気液界面よりも下方の液冷媒中に流入するようになっており、
受液器（３１）内に溜まる液冷媒は、一方のヘッダタンク（２２）の内部空間のうち下側セパレータ（２９ｂ）の下側空間（２２ｃ）を通過して過冷却部（３７）に流入するようになっており、
連通路（３０）のうち、上側セパレータ（２９ａ）の上側部位は、一方のヘッダタンク（２２）の内部空間のうち上側セパレータ（２９ａ）の上側空間（２２ａ）と受液器（３１）の上側内部空間との間に介在される低温冷媒通路を構成することを特徴としている。
【００２６】
これによると、コア部（２３）の上下に凝縮部（３６）と過冷却部（３７）を一体に構成する受液器一体型冷媒凝縮器において、請求項１と同様の、良好なる冷媒充填特性（図３のＡ特性）を設定できる。
【００２７】
請求項４記載の発明のように、請求項３に記載の受液器一体型冷媒凝縮器において、中間部空間（２２ｂ）を連通路（３０）に連通させる連通穴（３２）を、下側連通穴（３３）より上方側であって、かつ、上側連通穴（３４）よりも下方側に設ければよい。
なお、請求項１記載の発明および請求項３記載の発明において、いずれか一方のヘッダタンク（２２）に受液器（３１）を一体に構成するとは、別部品を一体に接合する場合と、一体成形品による場合の両方を包含している。
【００２８】
すなわち、請求項５記載の発明のように、一方のヘッダタンク（２２）と受液器（３１）が、互いに別部品として形成された後に一体に接合する構造とすることができる。
【００２９】
また、請求項９記載の発明のように、一方のヘッダタンク（２２）と受液器（３１）を一体の押出し成形部品（３１８）で形成し、この押出し成形部品（３１８）に上下方向に延びる中空形状部（３１９）を形成し、この中空形状部（３１９）により連通路（３０）を形成するようにしてもよい。
【００３０】
これによると、ヘッダタンク（２２）と受液器（３１）とを一体成形すると同時に連通路（３０）を形成できるので、部品加工工数と凝縮器接合箇所の大幅低減を図ることができる。
【００３１】
次に、請求項６記載の発明では、請求項５において、一方のヘッダタンク（２２）の構成部品（２２２）もしくは受液器（３１）の構成部品（３１１）のいずれか一方に、上下方向に延びる凹部（２２２ｂ）を形成し、この凹部（２２２ｂ）により連通路（３０）を形成することを特徴としている。
【００３２】
これによると、ヘッダタンク（２２）もしくは受液器（３１）の構成部品（２２２、３１１）に一体成形した凹部（２２２ｂ）により、簡単に連通路（３０）を形成することができ、製造コストの低減を図ることができる。
【００３３】
また、請求項７記載の発明のごとく、受液器（３１）の構成部品（３１１）の内部に上下方向に延びる仕切り部材（３１６）を配置し、この仕切り部材（３１６）により連通路（３０）を受液器（３１）の内部に形成してもよい。
【００３４】
また、請求項８記載の発明では、受液器（３１）の構成部品（３１１）を押出し成形することにより、受液器（３１）の構成部品（３１１）自身に、上下方向に延びる中空形状部（３１７）を形成し、この中空形状部（３１７）により連通路（３０）を形成することを特徴としている。
【００３５】
これによると、受液器（３１）の構成部品（３１１）自身に押出し成形によって連通路（３０）を簡単に一体成形できる。
【００３６】
なお、請求項１０に記載のごとく走行用エンジンにより駆動される、いわゆる開放型の圧縮機（１）を有する車両用冷凍装置においては、配管接続部等から微小量の冷媒漏れが発生しやすいのであるが、本発明は、このような車両用冷凍装置において要望される冷媒充填特性を良好に満足できるものであり、実用上のメリットが大である。
【００３７】
なお、上記各手段に付した括弧内の符号は、後述する実施形態記載の具体的手段との対応関係を示すものである。
【００３８】
【発明の実施の形態】
以下本発明を図に示す実施形態について説明する。
（第１実施形態）
図１は第１実施形態を示しており、本発明を自動車用空調装置における受液器一体型冷媒凝縮器に適用した例を示している。この自動車用空調装置の冷凍装置（冷凍サイクル）は、冷媒圧縮機１、受液器一体型冷媒凝縮器２、サイトグラス３、温度作動式膨張弁（減圧手段）４および冷媒蒸発器５を、金属製パイプまたはゴム製パイプよりなる冷媒配管によって順次接続した閉回路より構成されている。
【００３９】
冷媒圧縮機１は、自動車のエンジンルーム（図示せず）内に設置された走行用エンジンにベルトと電磁クラッチ（動力断続手段）１ａを介して連結されている。この冷媒圧縮機１は、電磁クラッチ１ａが接続状態となり、エンジンの回転動力が伝達されると、冷媒蒸発器５下流側よりガス冷媒を吸入、圧縮して、高温高圧の過熱ガス冷媒を受液器一体型冷媒凝縮器２へ吐出する。
【００４０】
受液器一体型冷媒凝縮器２は、所定間隔を開けて配置された一対のヘッダタンク、すなわち、第１、第２ヘッダタンク２１、２２を有し、この第１、第２ヘッダタンク２１、２２は上下方向に略円筒状に延びる形状になっている。この第１、第２ヘッダタンク２１、２２の間に熱交換用のコア部２３を配置している。
【００４１】
本例の冷媒凝縮器２は、一般にマルチフロータイプと称されているものであって、コア部２３は第１、第２ヘッダタンク２１、２２の間で、水平方向に冷媒を流す偏平チューブ２４を多数並列配置し、この多数の偏平チューブ２４の間にコルゲートフィン２５を介在して接合している。偏平チューブ２４の一端部は第１ヘッダタンク２１内に連通し、他端部は第２ヘッダタンク２２内に連通している。
【００４２】
そして、一方の（第１）ヘッダタンク２１の上端側に冷媒の入口側配管ジョイント（冷媒入口部）２６を配置し接合しており、また、下端側に冷媒の出口側配管ジョイント（冷媒出口部）２７を配置し接合している。
【００４３】
さらに、本例においては、第１ヘッダタンク２１内に第１、第２の２枚のセパレータ２８ａ、２８ｂを配置するとともに、第２ヘッダタンク２２内に第３、第４の２枚のセパレータ２９ａ、２９ｂを配置している。これにより、第１、第２ヘッダタンク２１、２２の内部をそれぞれ上下方向に複数（３個づつ）の空間２１ａ、２１ｂ、２１ｃ、２２ａ、２２ｂ、２２ｃに仕切っている。従って、入口側配管ジョイント２６からの冷媒を第１、第２ヘッダタンク２１、２２とコア部２３との間で蛇行状に流通させる。
【００４４】
ここで、第１ヘッダタンク２１内の上方側の第１セパレータ２８ａに対して第２ヘッダタンク２２内の上方側の第３セパレータ２９ａの高さは低くしてあるが、第１ヘッダタンク２１内の下方側の第２セパレータ２８ｂと第２ヘッダタンク２２内の下方側の第４セパレータ２９ｂは同一高さに配置してある。
【００４５】
また、第２ヘッダタンク２２には、冷媒の気液を分離して液冷媒を蓄える受液器３１が一体に構成してある。この受液器３１も略円筒形状であり、第２ヘッダタンク２２の外面側方（コア部２３と反対側の部位）に配置され、第２ヘッダタンク２２の外面に一体に接合される。受液器３１は第２ヘッダタンク２２より若干低い高さを有しており、受液器３１の上端部は第２ヘッダタンク２２の上側空間２２ａの上端部近くまで延びている。
【００４６】
なお、本例では、冷媒凝縮器２の各部および受液器３１はアルミニュウム材で成形され、一体ろう付けにて組付けられている。
【００４７】
受液器３１内部の空間と第２ヘッダタンク２２との連通構造を本発明では特徴としており、この連通構造について以下詳述すると、図２は第２ヘッダタンク２２と受液器３１の横断面図であり、第２ヘッダタンク２２は、偏平チューブ２４の端部が接合され、支持される断面半円状の第１プレート２２１を有し、この第１プレート２２１に略Ｗ字状の断面形状を持つ第２プレート２２２を接合することにより、略円筒状の形状を構成している。なお、第２ヘッダタンク２２の上下両端部はキャップ部材２２３、２２４（図１）により閉塞される。
【００４８】
一方、受液器３１の円筒本体部３１１は図２に示すように一枚のプレートを円筒状に曲げ加工して接合することにより略円筒状の形状を構成している。そして、受液器３１の上端部はキャップ部材３１２により閉塞されている。また、受液器３１の下端部は取付台座３１３により閉塞されている。この取付台座３１３は円筒本体部３１１に図示しないシール材を介して気密に、かつ、脱着可能にねじ止め固定される。この支持台３１３の上部には、水分吸着用の乾燥剤３１４および異物除去用のフィルタ３１５が一体に設けられている。フィルタ３１５は円筒状の網状体で構成さている。
【００４９】
そして、第２ヘッダタンク２２の第２プレート２２２に平面部２２２ａを形成するとともに、受液器３１の円筒本体部３１１に平面部３１１ａを形成し、この両平面部２２２ａ、３１１ａ同志を当接させて一体に接合するようになっている。ここで、第２プレート２２２の平面部２２２ａの中央部にヘッダタンク内側へ凹んだ凹部２２２ｂを一体成形している。
【００５０】
この凹部２２２ｂは第２プレート２２２の長手方向（上下方向）において、上側空間２２ａおよび中間部空間２２ｂの両方にわたって形成され、この凹部２２２ｂの形成により、第２プレート２２２の外面側と受液器３１の円筒本体部３１１の外面側との間に、これら部材の長手方向（上下方向）に延びる連通路３０を形成している。換言すると、連通路３０は第２ヘッダタンク２２と受液器３１とが対向する箇所に形成されている。連通路３０の上端部は図１に示すように受液器３１の上端部近傍に位置している。
【００５１】
そして、図１に示すように、凹部２２２ｂのうち、第３セパレータ２９ａと第４セパレータ２９ｂとの間の中間部位に第１の連通穴３２を設けて、第２ヘッダタンク２２の中間部空間２２ｂを上記の連通路３０に連通させている。また、受液器３１の円筒本体部３１１の平面部３１１ａのうち、連通路３０の下端部近傍および上端部近傍に対応する部位に、第２（下側）および第３（上側）の連通穴３３、３４を設けて、連通路３０の下端部近傍および上端部近傍の２か所を受液器３１内に連通させている。
【００５２】
ここで、第２の連通穴３３から受液器３１内に流入する冷媒量よりも、第３の連通穴３４から受液器３１内に流入する冷媒量の方を多くするために、第２の連通穴３３の開口面積Ａ₁に比して第３の連通穴３４の開口面積Ａ₂を十分大きくしてある。この点の詳細については後述する。なお、第１〜第３の連通穴３２〜３４は本例ではいずれも縦長の略長方形の形状にしてある。
【００５３】
さらに、第２ヘッダタンク２２の第２プレート２２２の平面部２２２ａおよび受液器３１の円筒本体部３１１の平面部３１１ａのうち、第４セパレータ２９ｂよりも下方の部位に第４の連通穴３５を設けて、受液器３１内部の底部近傍を第２ヘッダタンク２２の下方部空間２２ｃに連通させている。なお、受液器３１内部に溜まる液冷媒は乾燥剤３１４の周囲を通過した後、円筒状の網状体からなるフィルタ３１５の内部に必ず流入し、その後、フィルタ３１５を通過して第４の連通穴３５に流入する。
【００５４】
コア部２３において、第２、第４セパレータ２８ｂ、２９ｂより上方側の部位は、冷媒圧縮機１の吐出ガス冷媒をクーリングファン（図示せず）等により送られてくる室外空気と熱交換させて冷媒を冷却、凝縮させる凝縮部３６を構成している。また、コア部２３において、第２、第４セパレータ２８ｂ、２９ｂより下方側の部位は、受液器３１内部において気液分離された液冷媒を室外空気と熱交換させて過冷却する過冷却部３７を構成している。
【００５５】
従って、本例の冷媒凝縮器２は、冷媒流れの上流側から順次、凝縮部３６、受液器３１、および過冷却部３７を構成するとともに、これらを一体に設けた構成となっている。なお、受液器３１内における冷媒の気液界面は、冷媒封入量の正常時には、第３セパレータ２９ａと受液器３１の上端面との中間高さに位置するようになっている。
【００５６】
また、冷媒凝縮器２は周知のように、自動車エンジンルーム内において最前部（エンジン冷却用ラジエータの前方位置）に配置されて、エンジン冷却用ラジエータと共通のクーリングファンにより冷却される。
【００５７】
次に、冷凍サイクルの他の機器について簡単に説明すると、サイトグラス３は、受液器一体型冷媒凝縮器２の過冷却部３７で過冷却され、出口側配管ジョイント２７より流出してくる冷媒の気液状態を作業者が目視観察して、冷凍装置内封入冷媒量の過不足を点検する冷媒量点検手段として用いるものである。このサイトグラス３は、溶着ガラスにより気密にシールされた覗き窓３ａを有し、この覗き窓３ａから気泡が見られるときは冷媒不足であると判定し、気泡が見られないときは冷媒量が適正量であると判定する。温度作動式膨張弁４は、冷媒蒸発器５の冷媒入口側に接続され、高温高圧の液冷媒を断熱膨張して低温低圧の気液二相の霧状冷媒にする減圧手段として働くもので、冷媒蒸発器５の冷媒出口部の冷媒過熱度を所定値に維持するよう弁開度を自動調整する。
【００５８】
冷媒蒸発器５は、膨張弁４の下流側と冷媒圧縮機１の吸入側との間に接続され、膨張弁４より内部に流入した気液二相状態の冷媒を空調用送風機（図示せず）により送風される室外空気または室内空気と熱交換させて冷媒を蒸発させ、その蒸発潜熱により送風空気を冷却する冷却手段として働く。冷媒蒸発器５は、車室内に設置される空調ユニット（図示せず）のケース内に設けられる。
【００５９】
次に、上記構成において作動を説明する。いま、自動車用空調装置の運転が開始され、電磁クラッチ１ａに通電されると、電磁クラッチ１ａが接続状態となり、自動車エンジンの回転が圧縮機１に伝達され、圧縮機１が冷媒を圧縮し、吐出する。
【００６０】
これにより、圧縮機１から吐出された過熱ガス冷媒は、入口側配管ジョイント２６から凝縮器２の第１ヘッダタンク２１の上部空間２１ａより凝縮部３６の上側チューブ２４を通過した後、第２ヘッダタンク２２の上部空間２２ａに流入する。そして、冷媒はこの上部空間２２ａでＵターンして凝縮部３６の中間部チューブ２４を通過した後、第１ヘッダタンク２１の中間部空間２１ｂに流入する。次に、冷媒はこの中間部空間２１ｂでＵターンして凝縮部３６の下側チューブ２４を通過した後、第２ヘッダタンク２２の中間部空間２２ｂに流入する。
【００６１】
この間に、冷媒はチューブ２４およびフィン２５を介して冷却空気と熱交換して冷却され、ガス冷媒を一部含む飽和液冷媒となる。この飽和液冷媒は、上記の中間部空間２２ｂから第１の連通穴３２を通って連通路３０に流入する。この連通路３０内の冷媒は、連通路３０の下端部近傍の第２の連通穴３３および連通路３０の上端部近傍の第３の連通穴３４を通って受液器３１内に流入する。
【００６２】
そして、受液器３１内において冷媒の気液が分離され、液冷媒が蓄えられる。受液器３１内の液冷媒は第４の連通穴３５を通って第２ヘッダタンク２２の下部空間２２ｃを経由して過冷却部３７を通過する。この過冷却部３７において、液冷媒は再度冷却されて過冷却状態となり、この過冷却液冷媒は第１ヘッダタンク２１の下部空間２１ｃを通って出口側配管ジョイント２７から凝縮器２外へ流出する。
【００６３】
そして、過冷却液冷媒はサイトグラス３を通って、温度作動式膨張弁４に流入する。この膨張弁４において、過冷却液冷媒は減圧され、低温、低圧の気液２相冷媒となる。次いで、この気液２相冷媒は蒸発器５にて空調用空気と熱交換して蒸発し、その蒸発潜熱を空調用空気から吸熱して、空調用空気を冷却する。蒸発器５にて蒸発した過熱ガス冷媒は圧縮機１に吸入され、再度圧縮される。
【００６４】
次に、本発明の要部である「連通路３０、第２、第３の連通穴３３、３４による受液器３１への冷媒流入経路」の形成に伴う冷媒充填特性の改善について詳述する。
【００６５】
本実施形態によると、コア部２３で凝縮した冷媒が連通路３０を通って、この連通路３０の上下両側から受液器３１内に流入するから、セパレータ２９ａの上側空間２２ａ内に形成される温度の高い冷媒雰囲気と、受液器３１との間に、連通路３０による温度の低い冷媒雰囲気を介在させることができる。
【００６６】
これにより、第２ヘッダタンク２２の上部空間２２ａ内部の温度の高い冷媒の熱が受液器３１内部の冷媒に伝導するのをほとんどなくすことができる。従って、受液器３１が車両エンジンルームのフロントグリルの冷却風入口部横幅寸法の範囲外に位置して、受液器３１に冷却風を十分送風できない場合においても、受液器３１内部での液冷媒のガス化を良好に抑制できる。その結果、受液器３１の容積全体を液冷媒の蓄積のために有効に使用できる。
【００６７】
これにより、泡消点以降における冷媒封入量の増加分に対して、所定範囲（８０〜１８０ｇ）にわたって冷媒サブクールを略一定値に維持できる、理想的な冷媒充填特性を設定できる。
【００６８】
図３において本発明品は、従来品▲１▼と同様に受液器３１を断熱した条件にて冷媒充填特性を測定した結果を示しており、本発明品では受液器３１に冷却風を送風しない状態（断熱状態）でも、理想的な冷媒充填特性Ａを設定できることを確認できた。
【００６９】
（第２実施形態）
図４は第２実施形態であり、連通路３０を受液器３１の円筒本体部３１１の内部に形成するものである。すなわち、第２実施形態では第２ヘッダタンク２２の第２プレート２２２の平面部２２２ａに凹部２２２ｂを形成しない代わりに、円筒本体部３１１の内周側に仕切りプレート３１６を接合して、円筒本体部３１１の内周面と仕切りプレート３１６との間に連通路３０を形成している。
【００７０】
従って、第２プレート２２２の平面部２２２ａと受液器３１の円筒本体部３１１の平面部３１１ａを貫通して第１の連通穴３２を設けている。また、図示しないが、仕切りプレート３１６の下端部近傍および上端部近傍の部位に第２の連通穴３３および第３の連通穴３４を設けて、連通路３０の下端部近傍および上端部近傍の２か所を受液器３１内に連通させる。以上により、第２実施形態でも第１実施形態と同様の作用効果を発揮できる。
【００７１】
（第３実施形態）
図５は第３実施形態であり、受液器３１の円筒本体部３１１をアルミニウムの押出し成形により形成するとともに、この円筒本体部３１１の円周方向の一部に上下方向に延びる中空形状部３１７を一体成形している。すなわち、第３実施形態では第２実施形態の仕切りプレート３１６に相当する中空形状部３１７を押出し成形で円筒本体部３１１に一体成形して、この中空形状部３１７により連通路３０を形成している。従って、連通路３０は、受液器３１の構成部品である円筒本体部３１１自身に内蔵させることができる。他の点は、第１、第２実施形態と同じである。
【００７２】
（第４実施形態）
図６は第４実施形態であり、受液器３１の円筒本体部３１１と第２ヘッダタンク２２とをアルミニウムの一体押出し成形部品３１８により形成するとともに、この押出し成形部品３１８において円筒本体部３１１と第２ヘッダタンク２２とが対向する箇所（円筒本体部３１１と第２ヘッダタンク２２との中間部位）に、上下方向に延びる中空形状部３１８を一体成形している。この中空形状部３１８により連通路３０を構成している。なお、第４実施形態では、連通路３０を上下方向に２つ並列に構成している。
【００７３】
第４実施形態では、押出し成形部品３１８の成形後に、連通路３０と受液器３１の円筒本体部３１１内部および第２ヘッダタンク２２内部との連通を行う第１〜第４の連通穴３２〜３５（図６では図示を省略）を開ける。同様に、第２ヘッダタンク２２において、扁平チューブ２４の端部が挿入されるチューブ穴２２５も押出し成形部品３１８の成形後に開けられる。
【００７４】
（他の実施形態）
なお、本発明は上述の実施形態に限定されることなく種々変形可能なものであり、例えば、第１実施形態では、第２ヘッダタンク２２の第２プレート２２２の平面部２２２ａに凹部２２２ｂを形成しているが、この凹部２２２ｂに相当するものを受液器３１の円筒本体部３１１の平面部３１１ａ側に形成しても連通路３０を同様に形成できる。
【００７５】
上述の第１実施形態では、冷媒の出入口ジョイント２６、２７を設けていない第２ヘッダタンク２２に受液器３１を一体に構成しているが、冷媒の出入口ジョイント２６、２７を設けている第１ヘッダタンク２１に受液器３１を一体に構成してもよい。
【００７６】
また、凝縮器２のコア部２３を凝縮部３６のみとし、過冷却部３７をコア部２３から切り離して独立に構成するタイプの受液器一体型冷媒凝縮器に本発明を適用することもできる。
【００７７】
この場合は、第１ヘッダタンク２１における出口側配管ジョイント２７を廃止て、その代わりに、受液器３１にその内部の液冷媒を流出させる出口側配管ジョイント（冷媒出口部）を設置し、この出口側配管ジョイントからの液冷媒を配管を介して過冷却部に流入させるようにすればよい。
【００７８】
また、過冷却部３７を持たない冷凍装置においても、本発明は同様に実施できる。
【図面の簡単な説明】
【図１】本発明の第１実施形態の冷媒凝縮器を示す正面図である。
【図２】図１の要部の横断面図である。
【図３】冷凍サイクル内への冷媒充填特性の実験結果を示すグラフである。
【図４】本発明の第２実施形態の要部の横断面図である。
【図５】本発明の第３実施形態の要部の横断面図である。
【図６】本発明の第４実施形態の要部の横断面図である。
【図７】従来技術の冷媒凝縮器を示すもので、ヘッダータンク部を断面図示した正面図である。
【符号の説明】
１…圧縮機、２…凝縮器、３…サイトグラス、４…膨張弁、５…蒸発器、
２１…第１ヘッダタンク、２１ａ、２１ｂ、２１ｃ…空間、
２２…第２ヘッダタンク、２２ａ、２２ｂ、２２ｃ…空間、２３…コア部、
２４…チューブ、２８ａ、２８ｂ、２９ａ、２９ｂ…第１〜第４セパレータ、
３０…連通路、３１…受液器、３２〜３５…連通穴、３６…凝縮部、
３７…過冷却部。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an improvement in refrigerant filling characteristics of a liquid receiver, in which a liquid receiver that separates gas and liquid of a refrigerant and stores liquid refrigerant is integrated, and is used for a vehicle air conditioner. Is preferred.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, in a vehicle air conditioner, in order to improve vehicle mountability, a liquid receiver is integrated with a refrigerant condenser, and the vehicle mounting space of the refrigerant condenser and the liquid receiver is reduced. Various proposals have been proposed (see, for example, JP-A-8-219588).
[0003]
The refrigerant condenser in this prior art is generally called a multi-flow type, and has a pair of header tanks 21 and 22 arranged in the vertical direction as shown in FIG. A core portion 23 having a tube 24 for flowing a refrigerant in the horizontal direction is arranged between the header tanks 21, 22, a refrigerant inlet side pipe joint 26 is arranged on the upper end side of one (first) header tank 21, and the lower end side The refrigerant outlet side pipe joints 27 are arranged respectively.
[0004]
The header tanks 21 and 22 are partitioned into a plurality of spaces 21a to 21c and 22a to 22c in the vertical direction by separators 28a, 28b, 29a, and 29b arranged in both header tanks 21 and 22, respectively. Thus, the refrigerant (compressor discharge gas) from the inlet side pipe joint 26 is circulated between the pair of header tanks 21 and 22 and the core portion 23 in a meandering manner as indicated by the arrows in the figure.
[0005]
In addition, a receiver 31 is formed integrally with the second header tank 22 on the side where the refrigerant inlet / outlet pipe joints 26 and 27 are not provided, and the space inside the receiver 31. And the second header tank 22 are communicated with each other through a first communication hole 32 provided in a lower part of the header tank, and the liquid refrigerant condensed in the condensing part 36 of the core 23 is received through the first communication hole 32. The liquid refrigerant is stored in the liquid receiver 31 by separating the gas and liquid of the refrigerant in the liquid receiver 31.
[0006]
The second communication hole 35 is disposed below the first communication hole 32, and a separator 29b for partitioning the first communication hole 32 and the second communication hole 35 is provided as a second header. It is arranged in the tank 22. As a result, the liquid refrigerant in the liquid receiver 31 is caused to flow into the lowermost space 22c of the second header tank 22 from the second communication hole 35, and further passed through the supercooling part 37 of the core part 23. After cooling, the supercooled liquid refrigerant flows out from the outlet side pipe joint 27 through the lowermost space 21 c of the first header tank 21.
[0007]
[Problems to be solved by the invention]
By the way, when the above-mentioned prior art is actually tested for trial and the refrigerant filling characteristic in the refrigeration cycle (specifically, in the liquid receiver 31) is evaluated, it is desired to improve the efficiency of the refrigeration cycle. It was found that it was difficult to obtain the ideal refrigerant charging characteristics.
[0008]
FIG. 3 shows a sight glass provided on the downstream side of the outlet side pipe joint 27 with the subcool (supercooling degree) of the liquid refrigerant flowing out from the outlet side pipe joint 27 of the refrigerant condenser 2 taken along the vertical axis (see reference numeral 3 in FIG. 1). The horizontal axis represents the increase in refrigerant filling in the cycle after the point (bubble disappearance point) when bubbles (gas refrigerant) disappeared from the refrigerant. As experimental conditions, the rotational speed of the vehicle engine for driving the compressor of the refrigeration cycle = 1500 rpm, the outside air temperature = 30 ° C., the indoor fan speed for air conditioning = highest speed (Hi) setting → air volume = 450 m^Three/ H.
[0009]
In the case of a refrigeration cycle for a vehicle air conditioner, the refrigerant charging amount is usually about 100 g after the bubble extinction point so that the cooling performance will not be affected even if some refrigerant leakage occurs in the future. It is designed to be added, and the specified value for this additional amount (the amount of increase in the refrigerant of 100 g after the bubble extinction point) has a certain range of tolerance in consideration of variations in the refrigerant filling operation. .
[0010]
Therefore, after the bubble extinction point as shown by the characteristic A in FIG. 3, an area where the subcooling is maintained at a substantially constant value is set in the increase range of the refrigerant filling amount of 80 g to 180 g, and in this increase range, It is desired to prevent an increase in compressor power by preventing an increase in cycle high pressure due to an increase in subcooling.
[0011]
By the way, when the refrigerant filling characteristics of the above-mentioned prior art are examined experimentally, when the cooling air is sufficiently applied to the liquid receiver 31 as in the conventional product (2) in FIG. Although the characteristics can be obtained, when the receiver 31 is insulated with a heat insulating material as in the conventional product (1) in FIG. Then, along with this, it was found that the subcooling of the liquid refrigerant continuously increased.
[0012]
For this reason, in the refrigerant filling characteristic B, after the bubble extinction point, a slight refrigerant amount is added to cause an overfill cycle state, which causes a problem that the compressor power increases due to an increase in high pressure.
[0013]
Note that the width of the cooling air inlet portion of the front grill of the vehicle engine room is restricted from the viewpoint of vehicle design and the like, and therefore, in the actual mounting state on the vehicle, the receiver 31 is connected to the cooling air inlet of the front grill. There are many cases where it must be arranged outside the range of the lateral width dimension. As a result, it becomes almost impossible to expect cooling air to be blown to the liquid receiver 31, and a use state similar to the conventional product (1) in FIG. 3 occurs.
[0014]
Accordingly, in view of the above points, the present invention provides a refrigerant filling characteristic in which the refrigerant subcool can be maintained at a substantially constant value over a predetermined range with respect to the increase in the refrigerant filling amount after the bubble extinction point in the receiver-integrated refrigerant condenser. The purpose is to be able to set.
[0015]
[Means for Solving the Problems]
First, the cause of the refrigerant filling characteristics shown in FIG. 3B in the prior art will be described. In the prior art, in order to increase the number of turns of the refrigerant flow in the condensing unit 36 and improve the condensation capacity. The interior of the second header tank 22 in which the liquid receiver 31 is integrated is partitioned in the vertical direction by separators 29a and 29b. For this reason, since the pressure in the intermediate space 22b is lower than that in the upper space 22a due to the refrigerant flow path resistance in the condensing portion 36, the refrigerant temperature in the upper space 22a is the intermediate space 22b by the pressure difference. Get higher. For example, when the pressure in the upper space 22a = 1.50 MPa (refrigerant saturation temperature = 55.3 ° C.), in the intermediate space 22b, the pressure = 1.45 MPa (refrigerant saturation temperature = 53.9 ° C.), The temperature is 1.4 ° C. lower than the upper space 22a.
[0016]
If the cooling air is not sufficiently blown to the liquid receiver 31, the second header tank 22 and the liquid receiver 31 are partitioned by a thin metal plate having excellent thermal conductivity such as aluminum. Therefore, a temperature difference also occurs in the liquid receiver 31 in the vertical direction due to heat conduction from the second header tank 22. That is, the refrigerant temperature in the upper part of the liquid receiver 31 becomes higher than the temperature of the refrigerant flowing into the liquid receiver 31 from the first communication hole 32.
[0017]
Incidentally, the liquid receiver 31 originally has a function of accumulating excess refrigerant in the cycle and copes with refrigerant leakage from the cycle, and after the liquid refrigerant starts to accumulate in the liquid receiver 31, the liquid refrigerant Until the liquid receiver 31 overflows, the cycle behavior is not changed.
[0018]
However, when the refrigerant filling amount is further increased after the bubble extinction point at the time of filling the refrigerant in the cycle, the liquid level in the liquid receiver 31 gradually rises and exceeds the height of the separator 29a. For the above reason, the liquid refrigerant in the liquid receiver 31 is gasified by heat conduction from the upper space 22a inside the second header tank 22, and the liquid refrigerant is difficult to rise above the position of the separator 29a. Will occur.
[0019]
As described above, when it is difficult to raise the liquid refrigerant in the liquid receiver 31, since the refrigerant added thereafter at the time of filling the refrigerant cannot be accumulated in the liquid receiver 31, there is no place to go, and the core portion of the condenser 2. It was found that the liquid refrigerant overflowed into 23 and the aforementioned characteristic B was obtained.
[0020]
On the basis of such cause elucidation, in the present invention, it is possible to suppress the heat of the high-temperature refrigerant in the upper space (22a) in the header tank (22) from being conducted to the liquid refrigerant in the liquid receiver (31). By doing so, the above-described object is achieved.
[0021]
  That is, in the first aspect of the invention, the first header tank (21) disposed on one end side of the core portion (23) and the second header tank (22) disposed on the other end side of the core portion (23). ), A receiver-integrated refrigerant condenser that integrally configures the receiver (31),
  In one header tank (22), a separator (29a) for partitioning the internal space in the vertical direction is arranged,
  The liquid receiver (31) has a height dimension across the upper and lower sides of the separator (29a),
  The gas-liquid interface of the refrigerant in the liquid receiver (31) is positioned at an intermediate height between the separator (29a) and the upper end surface of the liquid receiver (31) when the refrigerant filling amount is normal.
  A communication path (30) extending across the upper and lower sides of the separator (29a) is formed at a location where one header tank (22) and the liquid receiver (31) face each other,
  Of the communication passage (30), the lower communication hole (33) for communicating the lower portion of the separator (29a) to the lower portion of the interior of the liquid receiver (31), and of the communication passage (30), the separator ( 29a) is provided with an upper communication hole (34) for communicating the upper part of the liquid receiver (31) with the upper part of the receiver (31).
  The refrigerant condensed in the core (23) flows into the space (22b) below the separator (29a) in the internal space of one header tank (22), and the internal space of the one header tank (22) Among them, the refrigerant having a higher temperature in the upstream portion than the space (22b) below the separator (29a) flows into the upper space (22a) of the separator (29a),
  In the communication path (30), the refrigerant condensed in the core part (23) flows through the space (22b) below the separator (29a),
  Further, the refrigerant in the communication path (30) flows into the liquid receiver (31) from both the upper and lower sides of the communication path (30) via the lower communication hole (33) and the upper communication hole (34). And
  The refrigerant from the lower communication hole (33) flows into the liquid refrigerant below the refrigerant gas-liquid interface in the liquid receiver (31),
  The upper part of the separator (29a) in the communication passage (30) is the upper space (22a) of the separator (29a) and the upper internal space of the liquid receiver (31) in the internal space of one header tank (22). And a low-temperature refrigerant passage interposed between the two.
[0022]
According to this, since the refrigerant condensed in the core part (23) flows into the liquid receiver (31) from both the upper and lower sides of the communication path (30) through the communication path (30), the separator (29a) A low-temperature refrigerant atmosphere by the communication path (30) can be interposed between the high-temperature refrigerant atmosphere in the upper space (22a) and the liquid receiver (31).
[0023]
Thereby, it can suppress that the heat | fever of the refrigerant | coolant with a high temperature inside the upper space (22a) of one header tank (22) is conducted to the refrigerant | coolant inside a liquid receiver (31). Therefore, even when the cooling air cannot be sufficiently blown to the liquid receiver (31), gasification of the liquid refrigerant inside the liquid receiver (31) can be satisfactorily suppressed, and the volume of the liquid receiver (31) can be reduced. Can be used effectively for the accumulation of.
[0024]
As a result, in one header tank (22), a separator (29a) that divides the internal space in the vertical direction is disposed, and a liquid receiver (31) is disposed over both the upper and lower sides of the separator (29a). Also in the liquid condenser-integrated refrigerant condenser, it is possible to set the refrigerant charging characteristic (A characteristic in FIG. 3) that can maintain the refrigerant subcool at a substantially constant value over a predetermined range with respect to the increase in the refrigerant filling amount after the bubble extinction point. . Therefore, it is possible to reliably prevent problems such as an increase in compressor power due to the occurrence of the overfill cycle state.
[0025]
  As in the invention according to claim 2, in the receiver-integrated refrigerant condenser according to claim 1, the communication hole (32) for communicating the space (22b) below the separator (29a) with the communication path (30). ) May be provided above the lower communication hole (33) and below the upper communication hole (34).
  Moreover, in invention of Claim 3, the 1st header tank (21) arrange | positioned at the one end side of a core part (23), and the 2nd header tank (22) arrange | positioned at the other end side of a core part (23) ), A receiver-integrated refrigerant condenser that integrally configures the receiver (31),
  A condensing part (36) for condensing the refrigerant at the upper part of the core part (23) and a supercooling part (37) for supercooling the refrigerant at the lower part of the core part (23),
  Arranging at least two separators (29a, 29b) on the upper side and the lower side in one header tank (22) configured integrally with the liquid receiver (31),
  The two separators (29a, 29b) partition one header tank (22) in the vertical direction into three spaces (22a, 22b, 22c),
  The liquid receiver (31) has a height dimension across the upper and lower sides of the upper separator (29a),
  The gas-liquid interface of the refrigerant in the liquid receiver (31) is positioned at an intermediate height between the upper separator (29a) and the upper end surface of the liquid receiver (31) when the refrigerant filling amount is normal.
  A communication passage (30) extending over both upper and lower sides of the upper separator (29a) is formed at a location where one header tank (22) and the liquid receiver (31) face each other,
  Of the communication passage (30), the lower communication hole (33) for communicating the lower portion of the upper separator (29a) with the lower portion of the receiver (31), and the upper portion of the communication passage (30). An upper communication hole (34) for communicating the upper part of the separator (29a) with the upper part of the receiver (31) is provided in the receiver (31).
  The refrigerant condensed in the condensing part (36) flows into the intermediate part space (22b) between the upper separator (29a) and the lower separator (29b) in the internal space of one header tank (22), Among the internal space of one header tank (22), the refrigerant having a higher temperature in the upstream portion than the intermediate space (22b) flows into the upper space (22a) of the upper separator (29a). ,
  The refrigerant condensed in the condensing part (36) flows into the communication path (30) via the intermediate part space (22b),
  Further, the refrigerant in the communication path (30) flows into the liquid receiver (31) from both the upper and lower sides of the communication path (30) via the lower communication hole (33) and the upper communication hole (34). And
  The refrigerant from the lower communication hole (33) flows into the liquid refrigerant below the refrigerant gas-liquid interface in the liquid receiver (31),
  The liquid refrigerant accumulated in the liquid receiver (31) passes through the lower space (22c) of the lower separator (29b) in the internal space of one header tank (22) and flows into the supercooling section (37). Is supposed to
  The upper part of the upper separator (29a) in the communication path (30) is the upper space (22a) of the upper separator (29a) and the upper side of the liquid receiver (31) in the internal space of one header tank (22). It is characterized by constituting a low-temperature refrigerant passage interposed between the internal space.
[0026]
According to this, in the receiver-integrated refrigerant condenser in which the condensing part (36) and the supercooling part (37) are integrally formed above and below the core part (23), the same satisfactory refrigerant charging as in claim 1 Characteristics (A characteristics in FIG. 3) can be set.
[0027]
  As in the invention according to claim 4, in the receiver-integrated refrigerant condenser according to claim 3, the communication hole (32) for communicating the intermediate space (22b) with the communication path (30) is provided on the lower side. What is necessary is just to provide above an upper communicating hole (34) above the communicating hole (33).
  Claims1Described inventionAnd the invention of claim 3In this case, the configuration in which the liquid receiver (31) is integrally formed with any one of the header tanks (22) includes both the case where the separate parts are joined together and the case where the parts are integrally formed.
[0028]
  That is, the claim5As described in the present invention, the one header tank (22) and the liquid receiver (31) may be integrally joined after being formed as separate parts.
[0029]
  Claims9As in the described invention, one of the header tank (22) and the liquid receiver (31) is formed by an integral extruded part (318), and the extruded part (318) has a hollow shape part extending in the vertical direction ( 319) may be formed, and the communication path (30) may be formed by the hollow portion (319).
[0030]
According to this, since the header tank (22) and the liquid receiver (31) can be integrally formed and the communication path (30) can be formed at the same time, the number of parts processing man-hours and the condenser joint location can be greatly reduced.
[0031]
  Next, the claim6In the described invention, the claims5, A concave portion (222b) extending in the vertical direction is formed in either one of the component (222) of one header tank (22) or the component (311) of the liquid receiver (31). ) To form the communication path (30).
[0032]
According to this, the communication path (30) can be easily formed by the recess (222b) formed integrally with the components (222, 311) of the header tank (22) or the liquid receiver (31), and the manufacturing cost is reduced. Can be reduced.
[0033]
  Claims7As described in the invention, a partition member (316) extending in the vertical direction is arranged inside the component (311) of the liquid receiver (31), and the communication path (30) is connected to the liquid receiver by the partition member (316). It may be formed inside (31).
[0034]
  Claims8In the described invention, the component (311) of the liquid receiver (31) is extruded to form the hollow part (317) extending vertically in the component (311) itself of the liquid receiver (31). It forms, and the communicating path (30) is formed by this hollow shape part (317), It is characterized by the above-mentioned.
[0035]
According to this, the communicating path (30) can be easily integrally formed by extrusion molding on the component (311) itself of the liquid receiver (31).
[0036]
  Claims10In the vehicular refrigeration apparatus having a so-called open type compressor (1) driven by the traveling engine as described in 1., a small amount of refrigerant leaks easily from a pipe connection portion or the like. Can satisfactorily satisfy the refrigerant filling characteristics required in such a vehicle refrigeration apparatus, and has a great practical advantage.
[0037]
In addition, the code | symbol in the parenthesis attached | subjected to each said means shows the correspondence with the specific means of embodiment description later mentioned.
[0038]
DETAILED DESCRIPTION OF THE INVENTION
The present invention will be described below with reference to embodiments shown in the drawings.
(First embodiment)
FIG. 1 shows a first embodiment and shows an example in which the present invention is applied to a receiver-integrated refrigerant condenser in an automotive air conditioner. This refrigeration apparatus (refrigeration cycle) for an automotive air conditioner includes a refrigerant compressor 1, a receiver-integrated refrigerant condenser 2, a sight glass 3, a temperature-operated expansion valve (decompression means) 4, and a refrigerant evaporator 5. It is composed of a closed circuit sequentially connected by a refrigerant pipe made of a metal pipe or a rubber pipe.
[0039]
The refrigerant compressor 1 is connected to a traveling engine installed in an engine room (not shown) of an automobile via a belt and an electromagnetic clutch (power intermittent means) 1a. In the refrigerant compressor 1, when the electromagnetic clutch 1a is in the connected state and the rotational power of the engine is transmitted, the refrigerant is sucked and compressed from the downstream side of the refrigerant evaporator 5 to receive the high-temperature and high-pressure superheated gas refrigerant. The refrigerant is discharged to the condenser-integrated refrigerant condenser 2.
[0040]
The liquid receiver-integrated refrigerant condenser 2 includes a pair of header tanks arranged at predetermined intervals, that is, first and second header tanks 21 and 22, and the first and second header tanks 21, 22, 22 has a shape extending in a substantially cylindrical shape in the vertical direction. A heat exchanging core portion 23 is disposed between the first and second header tanks 21 and 22.
[0041]
The refrigerant condenser 2 of this example is generally referred to as a multi-flow type, and the core portion 23 is a flat tube 24 that allows the refrigerant to flow in the horizontal direction between the first and second header tanks 21 and 22. Are arranged in parallel, and the corrugated fins 25 are interposed between the flat tubes 24. One end of the flat tube 24 communicates with the first header tank 21, and the other end communicates with the second header tank 22.
[0042]
A refrigerant inlet side pipe joint (refrigerant inlet part) 26 is arranged and joined to the upper end side of one (first) header tank 21, and the refrigerant outlet side pipe joint (refrigerant outlet part) is connected to the lower end side. ) 27 is arranged and joined.
[0043]
Further, in this example, the first and second separators 28a and 28b are disposed in the first header tank 21, and the third and fourth separators 29a are disposed in the second header tank 22. 29b. Thus, the interiors of the first and second header tanks 21 and 22 are partitioned into a plurality (three in each) of spaces 21a, 21b, 21c, 22a, 22b, and 22c in the vertical direction. Therefore, the refrigerant from the inlet side pipe joint 26 is circulated between the first and second header tanks 21 and 22 and the core portion 23 in a meandering manner.
[0044]
Here, although the height of the upper third separator 29 a in the second header tank 22 is lower than the upper first separator 28 a in the first header tank 21, The lower second separator 28b and the lower fourth separator 29b in the second header tank 22 are arranged at the same height.
[0045]
The second header tank 22 is integrally formed with a liquid receiver 31 that separates the gas-liquid refrigerant and stores the liquid refrigerant. The liquid receiver 31 also has a substantially cylindrical shape, is disposed on the outer surface side of the second header tank 22 (on the side opposite to the core portion 23), and is integrally joined to the outer surface of the second header tank 22. The liquid receiver 31 has a slightly lower height than the second header tank 22, and the upper end of the liquid receiver 31 extends to the vicinity of the upper end of the upper space 22 a of the second header tank 22.
[0046]
In this example, each part of the refrigerant condenser 2 and the liquid receiver 31 are formed of an aluminum material and assembled by integral brazing.
[0047]
The communication structure between the space inside the liquid receiver 31 and the second header tank 22 is a feature of the present invention. This communication structure will be described in detail below. FIG. 2 is a cross-sectional view of the second header tank 22 and the liquid receiver 31. The second header tank 22 includes a first plate 221 having a semicircular cross section that is supported by being joined to an end of the flat tube 24, and the first plate 221 has a substantially W-shaped cross section. The substantially cylindrical shape is comprised by joining the 2nd plate 222 which has. The upper and lower ends of the second header tank 22 are closed by cap members 223 and 224 (FIG. 1).
[0048]
On the other hand, the cylindrical main body 311 of the liquid receiver 31 has a substantially cylindrical shape by bending and joining one plate into a cylindrical shape as shown in FIG. The upper end of the liquid receiver 31 is closed by a cap member 312. Further, the lower end portion of the liquid receiver 31 is closed by the mounting base 313. The mounting base 313 is screwed and fixed to the cylindrical main body 311 through a sealing material (not shown) so as to be airtight and detachable. A drying agent 314 for adsorbing moisture and a filter 315 for removing foreign matter are integrally provided on the upper portion of the support base 313. The filter 315 is composed of a cylindrical mesh.
[0049]
Then, the flat portion 222a is formed on the second plate 222 of the second header tank 22, and the flat portion 311a is formed on the cylindrical body portion 311 of the liquid receiver 31, and both the flat portions 222a and 311a are brought into contact with each other. Are joined together. Here, a recessed portion 222b that is recessed inward of the header tank is integrally formed at the center of the flat surface portion 222a of the second plate 222.
[0050]
The concave portion 222b is formed over both the upper space 22a and the intermediate space 22b in the longitudinal direction (vertical direction) of the second plate 222. By forming the concave portion 222b, the outer surface side of the second plate 222 and the liquid receiver 31 are formed. A communication passage 30 extending in the longitudinal direction (vertical direction) of these members is formed between the cylindrical main body portion 311 and the outer surface side thereof. In other words, the communication path 30 is formed at a location where the second header tank 22 and the liquid receiver 31 face each other. The upper end of the communication path 30 is located near the upper end of the liquid receiver 31 as shown in FIG.
[0051]
Then, as shown in FIG. 1, a first communication hole 32 is provided in an intermediate portion between the third separator 29 a and the fourth separator 29 b in the recess 222 b, and an intermediate space 22 b of the second header tank 22 is provided. Is communicated with the communication passage 30 described above. Further, the second (lower side) and third (upper side) communication holes are formed in the portions corresponding to the vicinity of the lower end portion and the vicinity of the upper end portion of the communication passage 30 in the flat surface portion 311a of the cylindrical main body portion 311 of the liquid receiver 31. 33 and 34 are provided, and two places near the lower end portion and near the upper end portion of the communication path 30 are communicated with the liquid receiver 31.
[0052]
Here, in order to increase the amount of refrigerant flowing into the liquid receiver 31 from the third communication hole 34 rather than the amount of refrigerant flowing into the liquid receiver 31 from the second communication hole 33, Opening area A of the communication hole 33₁Compared to the opening area A of the third communication hole 34₂Is large enough. Details of this point will be described later. Note that the first to third communication holes 32 to 34 are all in the shape of a vertically long, substantially rectangular shape in this example.
[0053]
Furthermore, a fourth communication hole 35 is provided in a portion below the fourth separator 29b in the flat portion 222a of the second plate 222 of the second header tank 22 and the flat portion 311a of the cylindrical main body 311 of the liquid receiver 31. It is provided so that the vicinity of the bottom inside the liquid receiver 31 communicates with the lower part space 22 c of the second header tank 22. Note that the liquid refrigerant accumulated in the liquid receiver 31 passes through the periphery of the desiccant 314, and then surely flows into the filter 315 formed of a cylindrical mesh, and then passes through the filter 315 to pass through the fourth communication. It flows into the hole 35.
[0054]
In the core portion 23, the portion above the second and fourth separators 28 b and 29 b allows the discharge gas refrigerant of the refrigerant compressor 1 to exchange heat with outdoor air sent by a cooling fan (not shown) or the like. A condensing unit 36 that cools and condenses the refrigerant is configured. Further, in the core portion 23, a portion below the second and fourth separators 28 b and 29 b is a supercooling portion that supercools the liquid refrigerant separated in the liquid receiver 31 by heat exchange with outdoor air. 37 is constituted.
[0055]
Therefore, the refrigerant condenser 2 of the present example is configured such that the condensing unit 36, the liquid receiver 31, and the supercooling unit 37 are sequentially formed from the upstream side of the refrigerant flow, and these are integrally provided. Note that the gas-liquid interface of the refrigerant in the liquid receiver 31 is positioned at an intermediate height between the third separator 29 a and the upper end surface of the liquid receiver 31 when the refrigerant filling amount is normal.
[0056]
As is well known, the refrigerant condenser 2 is disposed at the foremost part (a front position of the engine cooling radiator) in the automobile engine room, and is cooled by a cooling fan common to the engine cooling radiator.
[0057]
Next, the other devices of the refrigeration cycle will be briefly described. The sight glass 3 is supercooled by the supercooling portion 37 of the receiver-integrated refrigerant condenser 2 and flows out from the outlet side pipe joint 27. This is used as a refrigerant quantity checking means for visually checking the gas-liquid state of the refrigerant and checking whether the refrigerant quantity in the refrigeration apparatus is excessive or insufficient. This sight glass 3 has a viewing window 3a hermetically sealed with welded glass. When bubbles are seen from the viewing window 3a, it is determined that the refrigerant is insufficient. When no bubbles are seen, the amount of refrigerant is It is determined that the amount is appropriate. The temperature-actuated expansion valve 4 is connected to the refrigerant inlet side of the refrigerant evaporator 5 and serves as a decompression means for adiabatic expansion of the high-temperature and high-pressure liquid refrigerant into a low-temperature and low-pressure gas-liquid two-phase mist refrigerant, The valve opening is automatically adjusted so as to maintain the refrigerant superheat degree at the refrigerant outlet of the refrigerant evaporator 5 at a predetermined value.
[0058]
The refrigerant evaporator 5 is connected between the downstream side of the expansion valve 4 and the suction side of the refrigerant compressor 1. The refrigerant in the gas-liquid two-phase state that has flowed into the interior from the expansion valve 4 is blown into an air conditioner (not shown). ) To exchange heat with the outdoor air or indoor air blown to evaporate the refrigerant and to serve as cooling means for cooling the blown air by the latent heat of evaporation. The refrigerant evaporator 5 is provided in a case of an air conditioning unit (not shown) installed in the passenger compartment.
[0059]
Next, the operation in the above configuration will be described. Now, when the operation of the automotive air conditioner is started and the electromagnetic clutch 1a is energized, the electromagnetic clutch 1a is in a connected state, the rotation of the automobile engine is transmitted to the compressor 1, and the compressor 1 compresses the refrigerant, Discharge.
[0060]
As a result, the superheated gas refrigerant discharged from the compressor 1 passes through the upper tube 24 of the condensing unit 36 from the upper space 21a of the first header tank 21 of the condenser 2 from the inlet side pipe joint 26, and then the second header. It flows into the upper space 22 a of the tank 22. The refrigerant makes a U-turn in the upper space 22 a and passes through the intermediate tube 24 of the condensing unit 36, and then flows into the intermediate space 21 b of the first header tank 21. Next, the refrigerant makes a U-turn in the intermediate space 21 b and passes through the lower tube 24 of the condenser 36, and then flows into the intermediate space 22 b of the second header tank 22.
[0061]
During this time, the refrigerant is cooled by exchanging heat with the cooling air via the tubes 24 and the fins 25 and becomes a saturated liquid refrigerant partially including a gas refrigerant. The saturated liquid refrigerant flows into the communication path 30 from the intermediate space 22b through the first communication hole 32. The refrigerant in the communication path 30 flows into the liquid receiver 31 through the second communication hole 33 near the lower end of the communication path 30 and the third communication hole 34 near the upper end of the communication path 30.
[0062]
And the gas-liquid of a refrigerant | coolant is isolate | separated in the liquid receiver 31, and a liquid refrigerant is stored. The liquid refrigerant in the liquid receiver 31 passes through the fourth communication hole 35 and passes through the subcooling portion 37 via the lower space 22 c of the second header tank 22. In this supercooling section 37, the liquid refrigerant is cooled again to be in a supercooled state, and this supercooled liquid refrigerant flows out of the condenser 2 from the outlet side pipe joint 27 through the lower space 21 c of the first header tank 21. .
[0063]
Then, the supercooled liquid refrigerant flows into the temperature-operated expansion valve 4 through the sight glass 3. In the expansion valve 4, the supercooled liquid refrigerant is decompressed to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. Next, this gas-liquid two-phase refrigerant evaporates by exchanging heat with air-conditioning air in the evaporator 5, absorbs the latent heat of evaporation from the air-conditioning air, and cools the air-conditioning air. The superheated gas refrigerant evaporated in the evaporator 5 is sucked into the compressor 1 and compressed again.
[0064]
Next, the improvement of the refrigerant charging characteristic accompanying the formation of “the refrigerant inflow path to the liquid receiver 31 by the communication passage 30, the second and third communication holes 33, 34”, which is a main part of the present invention, will be described in detail. .
[0065]
According to the present embodiment, since the refrigerant condensed in the core portion 23 passes through the communication path 30 and flows into the liquid receiver 31 from both the upper and lower sides of the communication path 30, it is formed in the upper space 22a of the separator 29a. A low-temperature refrigerant atmosphere by the communication path 30 can be interposed between the high-temperature refrigerant atmosphere and the liquid receiver 31.
[0066]
As a result, the heat of the high-temperature refrigerant in the upper space 22a of the second header tank 22 can be hardly transmitted to the refrigerant in the liquid receiver 31. Therefore, even when the liquid receiver 31 is located outside the range of the lateral width dimension of the cooling air inlet portion of the front grill of the vehicle engine room and the cooling air cannot be sufficiently blown to the liquid receiver 31, Gasification of the liquid refrigerant can be satisfactorily suppressed. As a result, the entire volume of the liquid receiver 31 can be used effectively for the accumulation of liquid refrigerant.
[0067]
Thereby, it is possible to set an ideal refrigerant charging characteristic that can maintain the refrigerant subcool at a substantially constant value over a predetermined range (80 to 180 g) with respect to the increase in the refrigerant filling amount after the bubble extinction point.
[0068]
In FIG. 3, the product of the present invention shows the result of measuring the refrigerant filling characteristics under the condition that the receiver 31 is insulated as in the case of the conventional product (1). It was confirmed that the ideal refrigerant charging characteristic A can be set even in a state where the air is not blown (insulated state).
[0069]
(Second Embodiment)
FIG. 4 shows a second embodiment in which the communication path 30 is formed inside the cylindrical main body 311 of the liquid receiver 31. That is, in the second embodiment, the partition plate 316 is joined to the inner peripheral side of the cylindrical main body portion 311 instead of forming the concave portion 222b in the flat surface portion 222a of the second plate 222 of the second header tank 22, and the cylindrical main body portion. A communication path 30 is formed between the inner peripheral surface of 311 and the partition plate 316.
[0070]
Accordingly, the first communication hole 32 is provided through the flat portion 222 a of the second plate 222 and the flat portion 311 a of the cylindrical main body 311 of the liquid receiver 31. In addition, although not shown, the second communication hole 33 and the third communication hole 34 are provided in the vicinity of the lower end portion and the upper end portion of the partition plate 316, so that 2 near the lower end portion and the upper end portion of the communication path 30. The place is communicated with the liquid receiver 31. As described above, the second embodiment can exhibit the same functions and effects as those of the first embodiment.
[0071]
(Third embodiment)
FIG. 5 shows a third embodiment, in which a cylindrical body 311 of the liquid receiver 31 is formed by extrusion molding of aluminum, and a hollow-shaped portion 317 that extends vertically in a part of the circumferential direction of the cylindrical body 311. Is integrally molded. That is, in the third embodiment, the hollow shape portion 317 corresponding to the partition plate 316 of the second embodiment is integrally formed with the cylindrical body portion 311 by extrusion molding, and the communication passage 30 is formed by the hollow shape portion 317. . Therefore, the communication path 30 can be incorporated in the cylindrical main body 311 itself that is a component of the liquid receiver 31. Other points are the same as those in the first and second embodiments.
[0072]
(Fourth embodiment)
FIG. 6 shows a fourth embodiment, in which the cylindrical body 311 and the second header tank 22 of the liquid receiver 31 are formed by an integrally extruded part 318 made of aluminum. In this extruded part 318, the cylindrical body 311 and A hollow portion 318 extending in the vertical direction is integrally formed at a location (an intermediate portion between the cylindrical main body portion 311 and the second header tank 22) facing the second header tank 22. The hollow portion 318 constitutes the communication path 30. In the fourth embodiment, two communication passages 30 are configured in parallel in the vertical direction.
[0073]
In the fourth embodiment, after the extrusion molding component 318 is formed, the first to fourth communication holes 32 to perform communication between the communication path 30 and the inside of the cylindrical body 311 of the liquid receiver 31 and the inside of the second header tank 22. 35 (not shown in FIG. 6) is opened. Similarly, in the second header tank 22, the tube hole 225 into which the end of the flat tube 24 is inserted is also opened after the extrusion molded part 318 is formed.
[0074]
(Other embodiments)
The present invention is not limited to the above-described embodiment and can be variously modified. For example, in the first embodiment, the concave portion 222b is formed in the flat portion 222a of the second plate 222 of the second header tank 22. However, the communication passage 30 can be formed in the same manner even if a portion corresponding to the concave portion 222b is formed on the flat surface portion 311a side of the cylindrical main body portion 311 of the liquid receiver 31.
[0075]
In the first embodiment described above, the liquid receiver 31 is integrally formed in the second header tank 22 that is not provided with the refrigerant inlet / outlet joints 26, 27, but the refrigerant inlet / outlet joints 26, 27 are provided first. The liquid receiver 31 may be integrated with the one header tank 21.
[0076]
Further, the present invention can be applied to a liquid receiver integrated refrigerant condenser of a type in which the core portion 23 of the condenser 2 is only the condensing portion 36 and the supercooling portion 37 is separated from the core portion 23 and configured independently. .
[0077]
In this case, the outlet-side piping joint 27 in the first header tank 21 is abolished, and instead, an outlet-side piping joint (refrigerant outlet portion) that causes the liquid refrigerant in the receiver 31 to flow out is installed. The liquid refrigerant from the outlet side pipe joint may be allowed to flow into the supercooling part via the pipe.
[0078]
Further, the present invention can be similarly implemented in a refrigeration apparatus that does not have the supercooling unit 37.
[Brief description of the drawings]
FIG. 1 is a front view showing a refrigerant condenser according to a first embodiment of the present invention.
2 is a cross-sectional view of the main part of FIG.
FIG. 3 is a graph showing experimental results of refrigerant charging characteristics in the refrigeration cycle.
FIG. 4 is a cross-sectional view of a main part of a second embodiment of the present invention.
FIG. 5 is a cross-sectional view of a main part of a third embodiment of the present invention.
FIG. 6 is a cross-sectional view of a main part of a fourth embodiment of the present invention.
FIG. 7 is a front view showing a header tank section in cross-section, showing a conventional refrigerant condenser.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Condenser, 3 ... Sight glass, 4 ... Expansion valve, 5 ... Evaporator,
21 ... 1st header tank, 21a, 21b, 21c ... space,
22 ... 2nd header tank, 22a, 22b, 22c ... space, 23 ... core part,
24 ... Tube, 28a, 28b, 29a, 29b ... First to fourth separators,
30 ... Communication path, 31 ... Liquid receiver, 32-35 ... Communication hole, 36 ... Condensing part,
37 ... Supercooling part.

Claims

A liquid receiver that integrally constitutes a liquid receiver (31) that cools and condenses the superheated refrigerant gas discharged from the compressor (1), separates the gas-liquid of the condensed refrigerant, and stores the liquid refrigerant. In the integrated refrigerant condenser,
A core portion (23) having a tube (24) arranged in the horizontal direction, in which a refrigerant flows in the tube (24);
A first header tank (21) arranged to extend in the vertical direction on one end side of the core portion (23), and communicated with one end portion of the tube (24);
A second header tank (22) arranged to extend in the vertical direction on the other end side of the core portion (23) and communicating with the other end portion of the tube (24);
The liquid receiver (31) is integrated with either one of the first header tank (21) and the second header tank (22), and
In this one header tank (22), a separator (29a) for partitioning the internal space in the vertical direction is arranged,
The liquid receiver (31) has a height dimension across the upper and lower sides of the separator (29a),
The gas-liquid interface of the refrigerant in the liquid receiver (31) is positioned at an intermediate height between the separator (29a) and the upper end surface of the liquid receiver (31) when the refrigerant filling amount is normal. And
In the place where the one header tank (22) and the liquid receiver (31) face each other, a communication path (30) extending across the upper and lower sides of the separator (29a) is formed,
Of the communication passage (30), a lower communication hole (33) for communicating a lower portion of the separator (29a) with a lower portion of the receiver (31), and the communication passage (30) Among them, the liquid receiver (31) is provided with an upper communication hole (34) for communicating the upper part of the separator (29a) with the upper part of the receiver (31).
The refrigerant condensed in the core portion (23) flows into the space (22b) below the separator (29a) in the internal space of the one header tank (22), and the one header tank (22). In the inner space, the upper space (22a) of the separator (29a) flows into the refrigerant having a higher temperature in the upstream portion than the space (22b) below the separator (29a),
The refrigerant condensed in the core part (23) flows into the communication path (30) via the space (22b) below the separator (29a),
Further, the refrigerant in the communication path (30) is transferred from the upper and lower sides of the communication path (30) into the liquid receiver (31) through the lower communication hole (33) and the upper communication hole (34). It is supposed to flow in,
The refrigerant from the lower communication hole (33) flows into the liquid refrigerant below the refrigerant gas-liquid interface in the receiver (31),
The upper part of the separator (29a) in the communication path (30) is the upper space (22a) of the separator (29a) in the internal space of the one header tank (22) and the liquid receiver (31). The receiver-integrated refrigerant condenser is configured to constitute a low-temperature refrigerant passage interposed between the upper internal space and the inner space.

A communication hole (32) for communicating the space (22b) below the separator (29a) with the communication passage (30) is above the lower communication hole (33) and the upper communication hole. The receiver-integrated refrigerant condenser according to claim 1, wherein the refrigerant condenser is provided at a lower side than (34).

A liquid receiver that integrally constitutes a liquid receiver (31) that cools and condenses the superheated refrigerant gas discharged from the compressor (1), separates the gas-liquid of the condensed refrigerant, and stores the liquid refrigerant. In the integrated refrigerant condenser,
A core portion (23) having a tube (24) arranged in the horizontal direction, in which a refrigerant flows in the tube (24);
A first header tank (21) arranged to extend in the vertical direction on one end side of the core portion (23), and communicated with one end portion of the tube (24);
A second header tank (22) arranged to extend in the vertical direction on the other end side of the core portion (23) and communicating with the other end portion of the tube (24);
A condensing part (36) for condensing the refrigerant is formed at the upper part of the core part (23), and a supercooling part (37) for supercooling the refrigerant at the lower part of the core part (23) is formed. And
The liquid receiver (31) is integrated with either one of the first header tank (21) and the second header tank (22), and
At least two separators (29a, 29b) on the upper side and the lower side are arranged in this one header tank (22),
With the two separators (29a, 29b), the one header tank (22) is partitioned into three spaces (22a, 22b, 22c) in the vertical direction,
The liquid receiver (31) has a height dimension across the upper and lower sides of the upper separator (29a),
The gas-liquid interface of the refrigerant in the liquid receiver (31) is positioned at an intermediate height between the upper separator (29a) and the upper end surface of the liquid receiver (31) when the refrigerant filling amount is normal. And
A communication passage (30) extending across the upper and lower sides of the upper separator (29a) is formed at a location where the one header tank (22) and the liquid receiver (31) face each other,
Of the communication passage (30), a lower communication hole (33) for communicating a lower portion of the upper separator (29a) with a lower portion of the receiver (31), and the communication passage (30) Among these, the upper receiving hole (34) for communicating the upper part of the upper separator (29a) with the upper part inside the receiver (31) is provided in the receiver (31),
Of the internal space of the one header tank (22), the refrigerant condensed in the condensing part (36) is placed in the intermediate part space (22b) between the upper separator (29a) and the lower separator (29b). The refrigerant having a higher temperature in the upstream portion than the intermediate space (22b) flows into the upper space (22a) of the upper separator (29a) in the inner space of the one header tank (22). Inflow,
In the communication path (30), the refrigerant condensed in the condensing part (36) flows through the intermediate part space (22b),
Further, the refrigerant in the communication path (30) is transferred from the upper and lower sides of the communication path (30) into the liquid receiver (31) through the lower communication hole (33) and the upper communication hole (34). It is supposed to flow in,
The refrigerant from the lower communication hole (33) flows into the liquid refrigerant below the refrigerant gas-liquid interface in the receiver (31),
The liquid refrigerant that accumulates in the liquid receiver (31) passes through the lower space (22c) of the lower separator (29b) in the internal space of the one header tank (22), and the supercooling part ( 37)
The upper part of the upper separator (29a) in the communication passage (30) is the upper space (22a) of the upper separator (29a) in the internal space of the one header tank (22) and the liquid receiver. A receiver-integrated refrigerant condenser comprising a low-temperature refrigerant passage interposed between the upper internal space of (31).

A communication hole (32) for communicating the intermediate space (22b) with the communication passage (30) is located above the lower communication hole (33) and more than the upper communication hole (34). The receiver-integrated refrigerant condenser according to claim 3, wherein the refrigerant condenser is provided on a lower side.

5. The receiver according to claim 1, wherein the one header tank (22) and the liquid receiver (31) are joined together after being formed as separate parts. Liquid condenser integrated refrigerant condenser.

A concave portion (222b) extending in the vertical direction is formed in one of the component (222) of the one header tank (22) or the component (311) of the receiver (31),
The receiver-integrated refrigerant condenser according to claim 5, wherein the recess (222b) forms the communication path (30).

A partition member (316) extending in the vertical direction is disposed inside the component (311) of the liquid receiver (31), and the partition path (30) allows the communication path (30) to be connected to the liquid receiver (31). The receiver-integrated refrigerant condenser according to claim 5, wherein the receiver-integrated refrigerant condenser is formed inside the receiver.

By extruding the component (311) of the liquid receiver (31), a hollow shape portion (317) extending in the vertical direction is formed in the component (311) of the liquid receiver (31) itself,
The receiver-integrated refrigerant condenser according to claim 5, wherein the communication path (30) is formed by the hollow portion (317).

The one header tank (22) and the liquid receiver (31) are formed of an integral extruded part (318),
A hollow-shaped portion (319) extending in the vertical direction is formed in the extruded part (318),
The receiver-integrated refrigerant condenser according to any one of claims 1 to 4, wherein the communication path (30) is formed by the hollow portion (319).

A compressor (1) driven by a traveling engine to compress and discharge refrigerant;
A condenser (2) for condensing superheated refrigerant gas discharged from the compressor (1);
A liquid receiver (31) for separating the gas-liquid of the refrigerant condensed in the condenser (2) and storing the liquid refrigerant;
Decompression means (4) for decompressing and expanding the liquid refrigerant flowing out of the receiver (31);
An evaporator (5) for evaporating the gas-liquid two-phase refrigerant decompressed by the decompression means (4),
In the vehicular refrigeration system consisting of a closed circuit in which these devices are sequentially connected,
The said refrigerator (2) and the said liquid receiver (31) were comprised with the liquid receiver integrated refrigerant condenser as described in any one of Claim 1 thru | or 9, The refrigeration apparatus for vehicles characterized by the above-mentioned. .