JP4032548B2

JP4032548B2 - Receiver integrated refrigerant condenser

Info

Publication number: JP4032548B2
Application number: JP01451199A
Authority: JP
Inventors: 弘樹松尾; 哲滋信田; 恵津夫長谷川; 佳史安芸
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 1999-01-22
Filing date: 1999-01-22
Publication date: 2008-01-16
Anticipated expiration: 2019-01-22
Also published as: JP2000213826A

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。
車両ではスペース的制約が大きいので、車両搭載性を一層改善するためには、受液器タンクの断面積を如何に縮小するかが重要な課題となる。そこで、特開平７−１８０９３０号公報では、受液器への冷媒流入口を受液器内の冷媒液面より下方部位に配置し、そして、この冷媒流入口よりさらに下方部位に受液器からの冷媒流出口を配置している。
【０００３】
これによれば、冷媒流入口からの冷媒が受液器内の冷媒液面より下方部位に流入するので、冷媒液面より上方に冷媒が流入する場合に比して、冷媒の動圧により受液器内の冷媒液面が乱れるのを低減できる。これにより、受液器タンクの断面積が小さくても、冷媒の気液分離作用を良好に発揮できるようにしている。
【０００４】
【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みると、次のごとき不具合が発生することが判明した。
すなわち、上記従来技術では、受液器の下方側に冷媒流入口および冷媒流出口をともに配置しているので、液冷媒雰囲気は受液器の下方側のみに形成され、受液器の上方側は常にガス冷媒の雰囲気が作用している。従って、夏期の冷房時のごとく受液器内に溜められる液冷媒の温度より、受液器周囲の雰囲気温度（車両のエンジンルーム内温度）の方が高い場合には、受液器の全容積を液冷媒の貯留空間として利用できないという問題が生じる。
【０００５】
この問題についてより詳細に説明すると、冷凍サイクルの運転条件が変動して、サイクルとしての余剰冷媒量が増大すると、この余剰冷媒量は本来受液器内に液冷媒として貯留されるべきであるが、上記のように周囲の高温雰囲気からの吸熱により、受液器内の上方空間の温度が受液器内の液冷媒温度より高くなると、受液器内の上方空間では液冷媒が蒸発してガス状になってしまい、液冷媒の貯留空間として利用できない。
【０００６】
その結果、受液器から凝縮器側へ液冷媒が溢れ出てしまい、凝縮器における実質的な冷媒凝縮領域が減少するので、凝縮能力の低下を招き、サイクル高圧が上昇する。このサイクル高圧により圧縮機駆動動力が上昇するとか、あるいは、サイクル機器保護のための高圧スイッチが作動して、サイクルが停止され、冷房不足を生じる。
【０００７】
このような不具合の解消のために、受液器の容量アップを行えば、車両への搭載性の悪化、あるいは凝縮器コア部のサイズ縮小による性能低下を生じる。また、そればかりでなく、受液器断面積の増大による耐圧強度の低下も引き起こす。なお、別の従来技術として、特開平４−１０３９７３号公報では、受液器内の中心部に底部から上方へ延びる冷媒管を配置し、この冷媒管の上部に多数の小孔を開けて、この小孔から受液器内に凝縮冷媒を流入させることより、冷媒の気液分離性を向上させるものが提案されている。
【０００８】
この従来技術によると、冷媒管上部の小孔から凝縮冷媒を受液器内に流入させているものの、冷媒管が受液器内の中心部に位置しているので、凝縮冷媒のほとんどが受液器内の中心部付近に集まり、受液器胴体部の内壁を流入冷媒により直接冷却する作用が得られない。その結果、この従来技術においても、周囲の高温雰囲気からの吸熱により、受液器内の上方空間の温度が受液器内の液冷媒温度より高くなって、受液器内の上方空間では液冷媒が蒸発してガス状になり、液冷媒の貯留空間として利用できないという問題が生じる。
【０００９】
本発明は上記点に鑑みてなされたもので、受液器周囲が高温雰囲気である場合にも、受液器内の上方空間に至るまで液冷媒の貯留空間として利用できるようにすること、および断面積の小さい受液器であっても、良好な冷媒気液分離作用を発揮できるようにすることの両立を図ることを目的とする。
【００１０】
【課題を解決するための手段】
上記目的を達成するために、請求項１記載の発明では、圧縮機（１）から吐出された冷媒ガスを冷却して凝縮させるコア部（２３）と、
コア部（２３）で凝縮した後の冷媒の気液を分離して液冷媒を溜める受液器（３１）とを一体に構成し、受液器（３１）を上下方向に延びるように配置する受液器一体型冷媒凝縮器において、
受液器（３１）内に上下方向に延びる円筒状の仕切り部材（３１７）を配置し、この仕切り部材（３１７）の上端部（３１７ｂ）は開口しており、
この仕切り部材（３１７）により受液器（３１）の内壁に沿って周方向および上下方向に延びる冷媒案内通路（３１８）を形成するとともに、
仕切り部材（３１７）の内側に冷媒の気液分離部（３１９）を形成し、
コア部（２３）で凝縮した後の冷媒を冷媒案内通路（３１８）に流入させる冷媒流入口（３２）を前記冷媒案内通路（３１８）の下方部位に配置し、
冷媒流入口（３２）からの冷媒が冷媒案内通路（３１８）を受液器（３１）の内壁の周方向全周に沿って上昇するようになっており、
仕切り部材（３１７）の上端部（３１７ｂ）と受液器（３１）の上面壁部（３１２）との間に隙間（３２０）を形成し、
冷媒案内通路（３１８）を上昇して上端部（３１７ｂ）に到達した冷媒を隙間（３２０）を通して上端部（３１７ｂ）の周方向から気液分離部（３１９）内に流入させることを特徴としている。
【００１１】
これによると、コア部（２３）で凝縮した冷媒が冷媒案内通路（３１８）を通って、受液器（３１）の内壁に沿って周方向全体を上昇するから、凝縮後の低温冷媒により受液器（３１）の壁面を冷却できるとともに、受液器（３１）の壁面と気液分離部（３１９）との間に温度の低い冷媒雰囲気を介在させることができる。
【００１２】
これにより、受液器（３１）周囲の雰囲気が高温であっても、この高温雰囲気の熱が気液分離部（３１９）内の液冷媒に伝導されることを良好に防止できる。その結果、夏期の高温時においても、また、受液器（３１）に冷却風を十分送風できない搭載レイアウトにおいても、受液器（３１）内の気液分離部（３１９）の容積を上方空間に至るまで液冷媒の貯留空間として有効利用できる。
【００１３】
しかも、冷媒が冷媒案内通路（３１８）を上昇して、仕切り部材（３１７）の上端部（３１７ｂ）に到達すると、この上端部（３１７ｂ）と上面壁部（３１２）との間の隙間（３２０）により、冷媒が上端部（３１７ｂ）から周方向の全周を通って気液分離部３１９内に流入することができる。そのため、気液分離部（３１９）内への流入冷媒が周方向に分散される。
【００１４】
その結果、気液分離部（３１９）内の冷媒液面に作用する冷媒動圧が特定部位に集中せず、広範囲にわたって低い値で均一化される。これにより、冷媒液面の乱れを低減できるので、受液器（３１）の断面積を小さくしても、気液分離作用を良好に発揮できる。
また、請求項２記載の発明では、圧縮機（１）からの冷媒ガスの入口（２６）をコア部（２３）の上方に配置し、コア部（２３）で凝縮した後の冷媒の集合部（２２ｂ）をコア部（２３）の下方に配置しており、この集合部（２２ｂ）から凝縮後の冷媒を冷媒流入口（３２）に流入させることを特徴としている。
【００１５】
これによると、コア部（２３）下方に位置する凝縮冷媒の集合部（２２ｂ）から、やはり下方に位置する冷媒流入口（３２）を通して冷媒案内通路（３１８）の下部に直接冷媒を導くことができ、冷媒流路が簡潔となる。
また、請求項３記載の発明では、仕切り部材（３１７）の円筒状の面に、冷媒案内通路（３１８）を気液分離部（３１９）に直接連通させる連通孔（３２１）を備えることを特徴としている。
【００１６】
これによると、連通孔（３２１）により冷媒案内通路（３１８）を気液分離部（３１９）に直接連通させることができるので、仕切り部材（３１７）の上端部の隙間（３２０）を通して気液分離部（３１９）内に流入する冷媒量が減少して、気液分離部（３１９）内の冷媒液面に作用する冷媒動圧をより一層減少できる。その結果、気液分離作用をさらに向上できる。
請求項３記載の発明による連通孔（３２１）は、具体的には、請求項４記載の発明のように、仕切り部材（３１７）の円筒状の面の周方向および上下方向にわたって複数個備えるようにすればよい。
【００２１】
請求項５記載の発明では、コア部（２３）は、水平方向に配置され冷媒が流れるチューブ（２４）を有しており、このチューブ（２４）の一端部と連通する第１ヘッダタンク（２１）をこのコア部（２３）の一端側において上下方向に延びるように配置し、また、チューブ（２４）の他端部と連通する第２ヘッダタンク（２２）をコア部（２３）の他端側において上下方向に延びるように配置し、第１ヘッダタンク（２１）および第２ヘッダタンク（２２）のいずれか一方に受液器（３１）を一体に接合したことを特徴としている。
【００２２】
本発明は、このようなマルチフロータイプのコア構造を持つ凝縮器において好適に実施できるものである。
また、請求項６記載の発明では、気液分離部（３１９）で分離された液冷媒を過冷却する過冷却部（３５）をコア部（２３）に一体に設け、受液器（３１）の底部付近に液冷媒を過冷部却（３５）へ導くための冷媒流出口（３３）を配置したことを特徴としている。
【００２３】
本発明は、このような過冷部却一体型の凝縮器においても好適に実施できるものである。
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。
【００２４】
【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（冷媒量点検手段）３、温度作動式膨張弁（減圧手段）４、および空調空気を冷却する冷却手段としての冷媒蒸発器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。
【００２５】
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。
【００２６】
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。
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。
【００２７】
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。
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。
【００２８】
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。
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。
【００２９】
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。
本第１実施形態では、受液器３１内部と第２ヘッダタンク２２との連通構造、および受液器３１内部の気液分離部への冷媒流入通路構成を特徴としており、これらについて以下詳述すると、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、支持される略断面半円状の第１プレート２２１を有し、この第１プレート２２１に略断面半円状の第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により閉塞される。
【００３０】
一方、受液器３１は、略円筒状の形状に構成された胴体部３１１を有しており、この胴体部３１１の上端部はキャップ部材３１２により閉塞されている。なお、第２ヘッダタンク２２と受液器３１は、第２プレート２２２および胴体部３１１の一部に平面部を形成して、その平面部同志を当接させて一体に接合するようになっている。
【００３１】
胴体部３１１の下端部には略円筒状の取付台座３１３が接合され、この取付台座３１３はキャップ部材３１４により閉塞されている。このキャップ部材３１４は取付台座３１３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。
取付台座３１３の上部には、水分吸着用の乾燥剤３１５および異物除去用のフィルタ３１６が一体に設けられている。フィルタ３１６は円筒状の網状体で構成されている。
【００３２】
また、取付台座３１３の上部には上下方向に延びる略円筒状の仕切り部材３１７が配置されている。この仕切り部材３１７は、受液器３１の胴体部３１１内壁との間に所定の隙間を形成することにより、仕切り部材３１７と胴体部３１１内壁との間に周方向および上下方向に延びる冷媒案内通路３１８を形成している。そして、仕切り部材３１７の内周側（乾燥剤３１５の設置部位）に冷媒の気液分離部３１９を形成し、この気液分離部３１９と冷媒案内通路３１８とを仕切り部材３１７により仕切っている。
【００３３】
仕切り部材３１７の下端部は径方向に拡大されて拡大下端部３１７ａを形成し、この拡大下端部３１７ａを取付台座３１３の上面と胴体部３１１内壁の両方に接合している。なお、仕切り部材３１７は本例ではアルミニュウム製であり、ろう付けにより上記接合を行うことができる。
一方、仕切り部材３１７の上端部３１７ｂは受液器３１の上側のキャップ部材（上面壁部）３１２との間に隙間３２０を形成し、冷媒案内通路３１８内の冷媒が仕切り部材３１７の上端部３１７ｂまで上昇した後、隙間３２０を通して上端部３１７ｂの周方向の全周から矢印Ｂのごとく気液分離部３１９内に流入する。
【００３４】
一方、第２ヘッダタンク２２の中間部空間２２ｂの下端部付近において、第２ヘッダタンク２２の第２プレート２２２および受液器３１の胴体部３１１の壁面を貫通する冷媒流入口３２が開けてある。この冷媒流入口３２により、中間部空間２２ｂ内の凝縮後の冷媒が冷媒案内通路３１８の下端部に流入する。従って、本例では、中間部空間２２ｂが凝縮後の冷媒の集合部となる。
【００３５】
そして、第２ヘッダタンク２２の下方部空間２２ｃの上下方向の中間部付近において、第２ヘッダタンク２２の第２プレート２２２および受液器３１の取付台座３１３の壁面を貫通する冷媒流出口３３を設けている。この冷媒流出口３３は、気液分離部３１９内の液冷媒をフィルタ３１６を通して下方部空間２２ｃへと流出させる。
【００３６】
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３４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３５を構成している。
【００３７】
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３４、受液器３１、および過冷却部３５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、すなわち、液面レベルＡは、冷媒封入量の正常時には、第３セパレータ２９ａ付近の高さにあるので、冷媒流入口３２は冷媒液面Ａより十分低い位置にある。
【００３８】
また、冷媒凝縮器２は、通常、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。
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。
【００３９】
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３４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３４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３４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。
【００４０】
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から冷媒流入口３２を通って受液器３１内の冷媒案内通路３１８に流入する。この冷媒案内通路３１８内の冷媒は、胴体部３１１の内壁面の周方向の全周に沿って上昇する。
【００４１】
そして、冷媒案内通路３１８を形成する円筒状仕切り部材３１７の上端部３１７ｂに冷媒が到達すると、この上端部３１７ｂとキャップ部材３１２との間の隙間３２０により、上端部３１７ｂから周方向の全周を通って、仕切り部材３１７内側の気液分離部３１９内に流入し、ここで、冷媒の気液が比重差により分離され、液冷媒が下部に蓄えられる。
【００４２】
そして、気液分離部３１９下部の液冷媒はフィルタ３１６を通過した後に、冷媒流出口３３から第２ヘッダタンク２２の下方部空間２２ｃへと流出する。さらに、下方部空間２２ｃの液冷媒は過冷却部３５を通過して、この過冷却部３５において再度冷却されるので、液冷媒は過冷却状態となる。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。
【００４３】
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。
【００４４】
ところで、受液器３１の必要内容積は、一定期間（例えば、空調装置の保証期間）内に、冷凍サイクルの配管ジョイント部等から外部へ洩れると予想される冷媒洩れ量と、冷凍サイクルの運転条件の変動により発生する冷媒量変動分（熱交換器内冷媒量＋配管内冷媒量の変動分）との総和を受液器３１内に蓄えることができるように決定する。
【００４５】
しかしながら、車両搭載状態において受液器３１が周辺機器と密集する位置に配置され、受液器３１周囲への風回りが悪い場合には、夏期の高外気温時であると、受液器３１周囲の雰囲気温度の方が受液器３１内液冷媒温度より高くなる事態が発生する。このような場合には、受液器３１内で本来液冷媒として蓄えられるべき液冷媒が周囲からの吸熱により蒸発されられる現象が発生し、受液器３１の全タンク容量を液溜空間として利用できなくなる。
【００４６】
そこで、本実施形態においては、受液器３１内の気液分離部３１９への冷媒流入形態の改善により上記不具合を解消している。
すなわち、コア部２３の凝縮部３４で凝縮した冷媒は第２ヘッダタンク２２の中間部空間２２ｂから冷媒流入口３２を通って冷媒案内通路３１８の底部に流入した後、胴体部３１１の内壁面の周方向の全周に沿って上昇する。このように、凝縮部３４で冷却され、凝縮した低温の凝縮冷媒が胴体部３１１の内壁面の全周に沿って上昇するので、胴体部３１１の内壁面の全周を低温の凝縮冷媒により良好に冷却できる。これと同時に、冷媒案内通路３１８が受液器３１の胴体部３１１と気液分離部３１９との間に位置して温度の低い冷媒雰囲気を形成するので、胴体部３１１の熱が気液分離部３１９内部の液冷媒に伝導するのを良好に防止できる。
【００４７】
この結果、気液分離部３１９内の液冷媒が受液器３１周囲の高温雰囲気から吸熱して蒸発することを良好に防止できるので、気液分離部３１９内の容積を上方部まで液溜空間として有効に利用できる。
さらには、冷媒が冷媒案内通路３１８を上昇して、円筒状仕切り部材３１７の上端部３１７ｂに到達すると、この上端部３１７ｂとキャップ部材３１２との間の隙間３２０により、上端部３１７ｂから矢印Ｂのごとく周方向の全周を通って、仕切り部材３１７内側の気液分離部３１９内に流入する。そのため、気液分離部３１９内への流入冷媒が周方向に分散される。
【００４８】
その結果、気液分離部３１９内の冷媒液面Ａに対して、特定の部位に流入冷媒の動圧が集中することがなく、流入冷媒の動圧が広範囲にわたって低い値で均一化される。これにより、冷媒液面Ａの乱れを低減できるので、受液器３１の胴体部３１１の断面積を小さくしても、気液分離作用を良好に発揮できる。
（第２実施形態）
図２は第２実施形態であり、第１実施形態における円筒状の仕切り部材３１７に、冷媒案内通路３１８を気液分離部３１９に連通させる複数の連通孔３２１が備えられている。
【００４９】
この連通孔３２１は周方向および上下方向にわたって複数設けてあり、冷媒案内通路３１８内の冷媒の一部を円筒状仕切り部材３１７の上端部３１７ｂに到達する前に、連通孔３２１から直接気液分離部３１９内へ流入させるようにしたものである。
これよると、冷媒案内通路３１８内の冷媒の一部が連通孔３２１から気液分離部３１９側へ直接流入するので、仕切り部材３１７の上端部３１７ｂから気液分離部３１９の冷媒液面Ａに向かう冷媒が減少する。そのため、冷媒液面Ａに作用する冷媒流れの動圧が一層小さくなり、冷媒液面Ａが安定するので、気液分離作用をより一層改善できる。
【００５０】
（第３実施形態）
図３は第３実施形態であり、第１、第２実施形態では、入口側配管ジョイント２６をコア部２３の上方に配置し、コア部２３で凝縮した後の冷媒の集合部（第２ヘッダタンク２２の中間部空間２２ｂ）を下方に配置して、冷媒流入口３２をコア部２３の下方に配置しているが、第３実施形態ではこれとは逆に、入口側配管ジョイント２６をコア部２３の下方に配置し、コア部２３で凝縮した後の冷媒の集合部（第２ヘッダタンク２２の上部空間２２ａ）を上方に配置して、冷媒流入口３２もコア部２３の上方に配置している。
【００５１】
これに伴って、受液器３１内部の上部に冷媒案内部材３２２を配置している。すなわち、受液器３１内に形成される気液分離部３１９の冷媒液面より上方で、かつ、冷媒流入口３２より下方の部位に冷媒案内部材３２２を配置している。この冷媒案内部材３２２はその中央部において上方へ突出する凸部３２２ａと、この凸部３２２ａの底部の周囲にて周方向に延びる冷媒受け面３２２ｂとを有しており、この冷媒受け面３２２ｂに受液器３１の胴体部３１１の内壁に沿って周方向から冷媒を気液分離部３１９内に流入させる複数の連通孔（連通路）３２２ｃを形成している。
【００５２】
なお、冷媒案内部材３２２は例えば、アルミニュウム製として、受液器３１の胴体部３１１にろうけにより接合すればよい。
第３実施形態によると、入口側配管ジョイント２６からのガス冷媒がコア部２３を下方から上方へと蛇行状に流れて、この間に冷媒が凝縮し、そして、この凝縮後の冷媒は第２ヘッダタンク２２の上部空間２２ａに集合し、ここから、冷媒は冷媒流入口３２を通って受液器３１の上方空間に流入する。この流入冷媒は、冷媒案内部材３２２の中心部の上方への凸部３２２ａにより外周側の凹部をなす冷媒受け面３２２ｂ上に集まり、この冷媒受け面３２２ｂの周方向に複数設けられた連通孔３２２ｃにより冷媒を胴体部３１１の内壁に沿って周方向の全周から気液分離部３１９内に流入させる。
【００５３】
このように、胴体部３１１の内壁に沿って周方向の全周から冷媒を気液分離部３１９内に流入させることにより、気液分離部３１９内の冷媒液面Ａに作用する動圧が均一化され、低い値となる。これにより、冷媒液面Ａの乱れを低減でき、気液分離作用を良好に発揮できる。
また、胴体部３１１の内壁に沿って周方向の全周から流下する低温の凝縮冷媒の流れによって、気液分離部３１９内部の液冷媒を周囲の高温雰囲気より低温に維持することができるので、受液器３１内部の容積を上部に至るまで液溜空間として有効利用できる。
【００５４】
（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以下のごとく種々変形可能である。
▲１▼上述の実施形態では、仕切り部材３１７、あるいは冷媒案内部材３２２をアルミニュウム製として、受液器３１の胴体部３１１にろう付けにより接合する場合について説明したが、例えば、仕切り部材３１７、あるいは冷媒案内部材３２２を樹脂製とし、熱交換器のろう付け後に、受液器３１内に組み込む構造としてもよい。
【００５５】
▲２▼上述の実施形態では、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。
▲３▼凝縮器２のコア部２３を凝縮部３４のみとし、過冷却部３５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。
【００５６】
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。
また、過冷却部３５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、受液器側部分は断面図示している。
【図２】本発明の第２実施形態の冷媒凝縮器を示す正面図で、受液器側部分は断面図示している。
【図３】本発明の第３実施形態の冷媒凝縮器を示す正面図で、受液器側部分は断面図示している。
【符号の説明】
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、２６…入口側配管ジョイント（入口）、３１…受液器、
３２…冷媒流入口、３３…冷媒流出口、３４…凝縮部、３５…過冷却部、
３１７…仕切り部材、３１８…冷媒案内通路、３１９…気液分離部、
３２０…隙間、３２２…冷媒案内部材。[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 made.
Since a vehicle has a large space restriction, how to reduce the cross-sectional area of the receiver tank is an important issue in order to further improve the mountability of the vehicle. Therefore, in Japanese Patent Laid-Open No. 7-180930, the refrigerant inlet to the liquid receiver is disposed at a position below the refrigerant liquid surface in the liquid receiver, and the liquid receiver is further below the refrigerant inlet from the liquid receiver. The refrigerant outlet is arranged.
[0003]
According to this, since the refrigerant from the refrigerant inlet flows into a portion below the refrigerant liquid level in the receiver, it is received by the dynamic pressure of the refrigerant as compared with the case where the refrigerant flows above the refrigerant liquid level. It is possible to reduce the disturbance of the refrigerant liquid level in the liquid container. Thereby, even if the cross-sectional area of the liquid receiver tank is small, the gas-liquid separation action of the refrigerant can be satisfactorily exhibited.
[0004]
[Problems to be solved by the invention]
By the way, when the above-mentioned prior art is actually examined by trial manufacture, it has been found that the following problems occur.
That is, in the above prior art, since the refrigerant inlet and the refrigerant outlet are both arranged on the lower side of the liquid receiver, the liquid refrigerant atmosphere is formed only on the lower side of the liquid receiver, and the upper side of the liquid receiver. The atmosphere of gas refrigerant is always acting. Therefore, if the ambient temperature (temperature in the engine room of the vehicle) around the receiver is higher than the temperature of the liquid refrigerant stored in the receiver as during cooling in summer, the total volume of the receiver There arises a problem that cannot be used as a storage space for liquid refrigerant.
[0005]
This problem will be described in more detail. When the operating condition of the refrigeration cycle changes and the amount of surplus refrigerant as the cycle increases, this surplus refrigerant amount should be originally stored as liquid refrigerant in the receiver. When the temperature of the upper space in the receiver is higher than the temperature of the liquid refrigerant in the receiver due to heat absorption from the surrounding high-temperature atmosphere as described above, the liquid refrigerant evaporates in the upper space in the receiver. It becomes gaseous and cannot be used as a liquid refrigerant storage space.
[0006]
As a result, the liquid refrigerant overflows from the receiver to the condenser side, and the substantial refrigerant condensing region in the condenser is reduced, resulting in a reduction in condensing capacity and an increase in cycle high pressure. This cycle high pressure increases the compressor drive power or activates a high pressure switch for protecting the cycle equipment to stop the cycle, resulting in insufficient cooling.
[0007]
If the capacity of the liquid receiver is increased in order to solve such a problem, the mounting property on the vehicle is deteriorated, or the performance is lowered due to the size reduction of the condenser core part. Moreover, not only that, but also a decrease in pressure-resistant strength due to an increase in the cross-sectional area of the receiver is caused. As another conventional technique, in Japanese Patent Laid-Open No. 4-103973, a refrigerant pipe extending upward from the bottom is arranged in the center of the liquid receiver, and a large number of small holes are opened in the upper part of the refrigerant pipe. Proposals have been made to improve the gas-liquid separation of the refrigerant by allowing the condensed refrigerant to flow into the liquid receiver through the small holes.
[0008]
According to this prior art, although the condensed refrigerant is allowed to flow into the receiver from the small hole in the upper part of the refrigerant pipe, most of the condensed refrigerant is received because the refrigerant pipe is located at the center of the receiver. The action of gathering in the vicinity of the central portion in the liquid container and directly cooling the inner wall of the liquid receiver body by the inflowing refrigerant cannot be obtained. As a result, also in this prior art, the temperature of the upper space in the receiver is higher than the liquid refrigerant temperature in the receiver due to heat absorption from the surrounding high temperature atmosphere, and the liquid in the upper space in the receiver is liquid. The refrigerant evaporates into a gaseous state, causing a problem that it cannot be used as a liquid refrigerant storage space.
[0009]
The present invention has been made in view of the above points, and can be used as a liquid refrigerant storage space up to the upper space in the receiver even when the periphery of the receiver is in a high-temperature atmosphere, and An object is to achieve both a receiver having a small cross-sectional area and a satisfactory refrigerant / liquid separation function.
[0010]
[Means for Solving the Problems]
  In order to achieve the above object, in the invention according to claim 1,A core (23) for cooling and condensing the refrigerant gas discharged from the compressor (1);
  A liquid receiver (31) that separates the gas-liquid of the refrigerant after condensing in the core part (23) and stores the liquid refrigerant is integrally formed, and the liquid receiver (31) is arranged to extend in the vertical direction. In the receiver-integrated refrigerant condenser,
  It extends vertically in the liquid receiver (31).CylindricalA partition member (317) is disposed;The upper end (317b) of the partition member (317) is open,
  The partition member (317) forms a refrigerant guide passage (318) extending in the circumferential direction and the vertical direction along the inner wall of the liquid receiver (31), and
  A refrigerant gas-liquid separation part (319) is formed inside the partition member (317),
  A refrigerant inlet (32) for allowing the refrigerant condensed in the core part (23) to flow into the refrigerant guide passage (318) is disposed at a lower portion of the refrigerant guide passage (318),
  The refrigerant from the refrigerant inlet (32) rises in the refrigerant guide passage (318) along the entire circumference of the inner wall of the liquid receiver (31),
  Upper end of partition member (317)(317b)And a gap (320) between the upper surface wall (312) of the liquid receiver (31),
  Refrigerant guide passage (318)To reach the upper end (317b)It is characterized in that the refrigerant flows into the gas-liquid separator (319) from the circumferential direction of the upper end (317b) through the gap (320).
[0011]
According to this, since the refrigerant condensed in the core portion (23) passes through the refrigerant guide passage (318) and rises in the entire circumferential direction along the inner wall of the liquid receiver (31), it is received by the low-temperature refrigerant after condensation. The wall surface of the liquid container (31) can be cooled, and a low-temperature refrigerant atmosphere can be interposed between the wall surface of the liquid receiver (31) and the gas-liquid separator (319).
[0012]
Thereby, even if the atmosphere around liquid receiver (31) is high temperature, it can prevent well that the heat of this high temperature atmosphere is conducted to the liquid refrigerant in gas-liquid separation part (319). As a result, the volume of the gas-liquid separation part (319) in the liquid receiver (31) is increased in the upper space even at high temperatures in summer and in a mounting layout in which the cooling air cannot be sufficiently blown to the liquid receiver (31). Can be effectively used as a liquid refrigerant storage space.
[0013]
In addition, when the refrigerant rises in the refrigerant guide passage (318) and reaches the upper end (317b) of the partition member (317), a gap (320) between the upper end (317b) and the upper wall (312) is obtained. ) Allows the refrigerant to flow into the gas-liquid separator 319 from the upper end (317b) through the entire circumference. Therefore, the refrigerant flowing into the gas-liquid separator (319) is dispersed in the circumferential direction.
[0014]
As a result, the refrigerant dynamic pressure acting on the refrigerant liquid level in the gas-liquid separator (319) does not concentrate on the specific part, and is uniformed at a low value over a wide range. Thereby, since the disturbance of the refrigerant liquid level can be reduced, even if the cross-sectional area of the liquid receiver (31) is reduced, the gas-liquid separation action can be exhibited well.
In the invention according to claim 2, the refrigerant gas inlet (26) from the compressor (1) is arranged above the core part (23), and the refrigerant collecting part after being condensed in the core part (23) (22b) is arranged below the core portion (23), and the condensed refrigerant flows from the aggregate portion (22b) into the refrigerant inlet (32).
[0015]
  According to this, the refrigerant can be guided directly from the condensed refrigerant collecting portion (22b) located below the core portion (23) to the lower portion of the refrigerant guide passage (318) through the refrigerant inlet (32) also located below. This can simplify the refrigerant flow path.
  Moreover, in invention of Claim 3, a partition member (317)Cylindrical face ofIn addition, a communication hole (321) that directly communicates the refrigerant guide passage (318) with the gas-liquid separator (319) is provided.
[0016]
  According to this, since the refrigerant guide passage (318) can be directly communicated with the gas-liquid separator (319) by the communication hole (321), the gas-liquid separation is performed through the gap (320) at the upper end of the partition member (317). The amount of refrigerant flowing into the section (319) decreases, and the refrigerant dynamic pressure acting on the refrigerant liquid level in the gas-liquid separation section (319) can be further reduced. As a result, the gas-liquid separation action can be further improved.
  Specifically, a plurality of communication holes (321) according to the invention described in claim 3 are provided in the circumferential direction and the vertical direction of the cylindrical surface of the partition member (317) as in the invention described in claim 4. You can do it.
[0021]
Claim5In the described invention, the core portion (23) has a tube (24) arranged in a horizontal direction and through which a refrigerant flows, and the first header tank (21) communicating with one end portion of the tube (24) is connected to the core portion (23). The second header tank (22) which is disposed so as to extend in the vertical direction on one end side of the core portion (23) and communicates with the other end portion of the tube (24) is arranged vertically on the other end side of the core portion (23). It arrange | positions so that it may extend in a direction, and the liquid receiver (31) was integrally joined to either one of the 1st header tank (21) and the 2nd header tank (22).
[0022]
  The present invention can be suitably implemented in a condenser having such a multi-flow type core structure.
  Claims6In the described invention, a supercooling part (35) for supercooling the liquid refrigerant separated by the gas-liquid separation part (319) is provided integrally with the core part (23), and the liquid receiver (31) is placed near the bottom. A refrigerant outlet (33) for guiding the refrigerant to the supercooling section (35) is arranged.
[0023]
The present invention can be suitably implemented also in such a supercooling part rejection integrated condenser.
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.
[0024]
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. The refrigeration apparatus (refrigeration cycle) of this automotive air conditioner includes a refrigerant compressor 1, a receiver-integrated refrigerant condenser 2, a sight glass (refrigerant amount checking means) 3, a temperature-operated expansion valve (decompression means) 4, The refrigerant evaporator 5 as a cooling means for cooling the conditioned air is constituted by a closed circuit in which the refrigerant evaporator 5 is sequentially connected by a refrigerant pipe made of a metal pipe or a rubber pipe.
[0025]
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.
[0026]
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.
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.
[0027]
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.
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.
[0028]
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.
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.
[0029]
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.
The first embodiment features a communication structure between the interior of the liquid receiver 31 and the second header tank 22 and a refrigerant inflow passage configuration to the gas-liquid separation section inside the liquid receiver 31, which will be described in detail below. Then, the second header tank 22 has a first plate 221 having a substantially semicircular cross section that is supported by being joined to an end of the flat tube 24, and the second plate having a substantially semicircular cross section is formed on the first plate 221. By joining the plates 222, a substantially cylindrical shape is formed. The upper and lower ends of the second header tank 22 are closed by cap members 223 and 224.
[0030]
On the other hand, the liquid receiver 31 has a body portion 311 configured in a substantially cylindrical shape, and an upper end portion of the body portion 311 is closed by a cap member 312. The second header tank 22 and the liquid receiver 31 are joined together by forming a flat portion on a part of the second plate 222 and the body portion 311 and bringing the flat portions into contact with each other. Yes.
[0031]
A substantially cylindrical mounting base 313 is joined to the lower end of the body part 311, and the mounting base 313 is closed by a cap member 314. The cap member 314 is screwed and fixed to the mounting base 313 in an airtight and detachable manner via a seal material (not shown).
An upper part of the mounting base 313 is integrally provided with a desiccant 315 for adsorbing moisture and a filter 316 for removing foreign matter. The filter 316 is formed of a cylindrical net.
[0032]
In addition, a substantially cylindrical partition member 317 extending in the vertical direction is disposed on the mounting base 313. This partition member 317 forms a predetermined gap between the inner wall of the body part 311 of the liquid receiver 31 and thereby extends in the circumferential direction and the vertical direction between the partition member 317 and the inner wall of the body part 311. 318 is formed. A refrigerant gas-liquid separator 319 is formed on the inner peripheral side of the partition member 317 (installation site of the desiccant 315), and the gas-liquid separator 319 and the refrigerant guide passage 318 are partitioned by the partition member 317.
[0033]
The lower end portion of the partition member 317 is enlarged in the radial direction to form an enlarged lower end portion 317a, and the enlarged lower end portion 317a is joined to both the upper surface of the mounting base 313 and the inner wall of the body portion 311. Note that the partition member 317 is made of aluminum in this example, and can be joined by brazing.
On the other hand, the upper end portion 317b of the partition member 317 forms a gap 320 with the cap member (upper surface wall portion) 312 on the upper side of the liquid receiver 31, and the refrigerant in the refrigerant guide passage 318 is moved to the upper end portion 317b of the partition member 317. And then flows into the gas-liquid separator 319 as indicated by the arrow B from the entire circumference in the circumferential direction of the upper end 317b through the gap 320.
[0034]
On the other hand, in the vicinity of the lower end portion of the intermediate space 22 b of the second header tank 22, a refrigerant inlet 32 penetrating the second plate 222 of the second header tank 22 and the wall surface of the body portion 311 of the liquid receiver 31 is opened. . Through the refrigerant inlet 32, the condensed refrigerant in the intermediate space 22b flows into the lower end portion of the refrigerant guide passage 318. Accordingly, in the present example, the intermediate space 22b is a refrigerant collecting portion after condensation.
[0035]
Then, in the vicinity of the middle portion in the vertical direction of the lower part space 22 c of the second header tank 22, a refrigerant outlet 33 that penetrates the wall surface of the second plate 222 of the second header tank 22 and the mounting base 313 of the liquid receiver 31 is provided. Provided. The refrigerant outlet 33 allows the liquid refrigerant in the gas-liquid separator 319 to flow out to the lower part space 22c through the filter 316.
[0036]
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 34 is configured to cool and condense the refrigerant.
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. 35.
[0037]
Therefore, the refrigerant condenser 2 of this example is configured such that the condensing unit 34, the liquid receiver 31 and the supercooling unit 35 are sequentially formed from the upstream side of the refrigerant flow, and these are integrally provided. In addition, since the gas-liquid interface of the refrigerant in the liquid receiver 31, that is, the liquid level A is at a height near the third separator 29 a when the refrigerant filling amount is normal, the refrigerant inlet 32 is arranged at the refrigerant liquid level A. It is in a lower position.
[0038]
Further, the refrigerant condenser 2 is usually 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.
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.
[0039]
As a result, the superheated gas refrigerant discharged from the compressor 1 passes through the upper tube 24 of the condensing unit 34 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 34, 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 34, and then flows into the intermediate space 22 b of the second header tank 22.
[0040]
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 refrigerant guide passage 318 in the liquid receiver 31 from the intermediate space 22b through the refrigerant inlet 32. The refrigerant in the refrigerant guide passage 318 rises along the entire circumference of the inner wall surface of the body portion 311 in the circumferential direction.
[0041]
When the refrigerant reaches the upper end portion 317b of the cylindrical partition member 317 forming the refrigerant guide passage 318, the gap 320 between the upper end portion 317b and the cap member 312 causes the entire circumference in the circumferential direction from the upper end portion 317b. Then, it flows into the gas-liquid separator 319 inside the partition member 317, where the gas-liquid of the refrigerant is separated due to the specific gravity difference, and the liquid refrigerant is stored in the lower part.
[0042]
The liquid refrigerant below the gas-liquid separator 319 passes through the filter 316 and then flows out from the refrigerant outlet 33 to the lower space 22 c of the second header tank 22. Furthermore, since the liquid refrigerant in the lower part space 22c passes through the supercooling part 35 and is cooled again in the supercooling part 35, the liquid refrigerant enters a supercooled state. 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.
[0043]
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.
[0044]
By the way, the required internal volume of the liquid receiver 31 is the refrigerant leakage amount expected to leak to the outside from the piping joint portion of the refrigeration cycle within a certain period (for example, the warranty period of the air conditioner), and the operation of the refrigeration cycle. It is determined so that the sum total of the amount of refrigerant amount fluctuation (the amount of refrigerant in the heat exchanger + the amount of fluctuation in the refrigerant amount in the pipe) generated by the fluctuation of the condition can be stored in the liquid receiver 31.
[0045]
However, when the receiver 31 is arranged at a position where the receiver 31 is densely packed with peripheral devices in a vehicle-mounted state, and the wind around the receiver 31 is poor, the receiver 31 is considered to be at a high outdoor temperature in summer. A situation occurs in which the ambient temperature is higher than the liquid refrigerant temperature in the liquid receiver 31. In such a case, a phenomenon occurs in which liquid refrigerant that should be stored as liquid refrigerant in the liquid receiver 31 is evaporated by heat absorption from the surroundings, and the entire tank capacity of the liquid receiver 31 is used as a liquid storage space. become unable.
[0046]
Therefore, in the present embodiment, the above problem is eliminated by improving the refrigerant inflow mode to the gas-liquid separator 319 in the liquid receiver 31.
That is, the refrigerant condensed in the condensing part 34 of the core part 23 flows from the intermediate part space 22b of the second header tank 22 through the refrigerant inlet 32 to the bottom part of the refrigerant guide passage 318, and then on the inner wall surface of the body part 311. It rises along the entire circumference. In this way, the low-temperature condensed refrigerant that has been cooled and condensed by the condensing unit 34 rises along the entire circumference of the inner wall surface of the body portion 311, so that the entire circumference of the inner wall surface of the body portion 311 can be improved by the low-temperature condensed refrigerant. Can be cooled. At the same time, the refrigerant guide passage 318 is positioned between the body part 311 and the gas-liquid separation part 319 of the liquid receiver 31 to form a low-temperature refrigerant atmosphere, so that the heat of the body part 311 is transferred to the gas-liquid separation part. It is possible to satisfactorily prevent conduction to the liquid refrigerant inside 319.
[0047]
As a result, it is possible to satisfactorily prevent the liquid refrigerant in the gas-liquid separator 319 from absorbing heat and evaporating from the high-temperature atmosphere around the receiver 31, so that the volume in the gas-liquid separator 319 can be increased to the upper part. Can be used effectively.
Further, when the refrigerant rises in the refrigerant guide passage 318 and reaches the upper end portion 317b of the cylindrical partition member 317, the gap 320 between the upper end portion 317b and the cap member 312 causes the arrow B to extend from the upper end portion 317b. In this way, the gas flows through the entire circumference in the circumferential direction and flows into the gas-liquid separator 319 inside the partition member 317. Therefore, the refrigerant flowing into the gas-liquid separator 319 is dispersed in the circumferential direction.
[0048]
As a result, the dynamic pressure of the incoming refrigerant does not concentrate on a specific part with respect to the refrigerant liquid level A in the gas-liquid separator 319, and the dynamic pressure of the incoming refrigerant is made uniform at a low value over a wide range. Thereby, since the disturbance of the refrigerant liquid level A can be reduced, even if the cross-sectional area of the body portion 311 of the liquid receiver 31 is reduced, the gas-liquid separation action can be satisfactorily exhibited.
(Second Embodiment)
FIG. 2 shows a second embodiment, in which a plurality of communication holes 321 that allow the refrigerant guide passage 318 to communicate with the gas-liquid separator 319 are provided in the cylindrical partition member 317 in the first embodiment.
[0049]
A plurality of the communication holes 321 are provided in the circumferential direction and the vertical direction, and a part of the refrigerant in the refrigerant guide passage 318 is directly separated from the communication holes 321 before reaching the upper end portion 317b of the cylindrical partition member 317. It is made to flow into the part 319.
According to this, since a part of the refrigerant in the refrigerant guide passage 318 flows directly from the communication hole 321 to the gas-liquid separation part 319 side, the upper end part 317b of the partition member 317 enters the refrigerant liquid surface A of the gas-liquid separation part 319. The refrigerant that heads is reduced. Therefore, the dynamic pressure of the refrigerant flow acting on the refrigerant liquid level A is further reduced and the refrigerant liquid level A is stabilized, so that the gas-liquid separation action can be further improved.
[0050]
(Third embodiment)
FIG. 3 shows a third embodiment. In the first and second embodiments, the inlet-side piping joint 26 is disposed above the core portion 23 and the refrigerant collecting portion (second header) after condensing in the core portion 23 is shown. The intermediate space 22b) of the tank 22 is disposed below and the refrigerant inlet 32 is disposed below the core 23. In the third embodiment, on the contrary, the inlet side pipe joint 26 is disposed on the core. The refrigerant collecting part (the upper space 22a of the second header tank 22) after being condensed at the core part 23 is arranged above the part 23, and the refrigerant inlet 32 is also arranged above the core part 23. is doing.
[0051]
Along with this, a refrigerant guide member 322 is arranged at the upper part inside the liquid receiver 31. That is, the refrigerant guide member 322 is disposed at a position above the refrigerant liquid surface of the gas-liquid separator 319 formed in the liquid receiver 31 and below the refrigerant inlet 32. The refrigerant guide member 322 has a convex portion 322a that protrudes upward at the center thereof, and a refrigerant receiving surface 322b that extends in the circumferential direction around the bottom of the convex portion 322a. A plurality of communication holes (communication passages) 322c are formed along the inner wall of the body portion 311 of the liquid receiver 31 to allow the refrigerant to flow into the gas-liquid separation portion 319 from the circumferential direction.
[0052]
The refrigerant guide member 322 may be made of aluminum, for example, and may be joined to the body portion 311 of the liquid receiver 31 by soldering.
According to the third embodiment, the gas refrigerant from the inlet side pipe joint 26 flows in a meandering manner from the lower part to the upper part in the core part 23, and the refrigerant condenses during this time, and the condensed refrigerant is the second header. The refrigerant gathers in the upper space 22 a of the tank 22, from which the refrigerant flows into the upper space of the liquid receiver 31 through the refrigerant inlet 32. The inflowing refrigerant gathers on the refrigerant receiving surface 322b that forms a concave portion on the outer peripheral side by the convex portion 322a upward of the central portion of the refrigerant guide member 322, and a plurality of communication holes 322c provided in the circumferential direction of the refrigerant receiving surface 322b. Thus, the refrigerant is caused to flow into the gas-liquid separator 319 from the entire circumference in the circumferential direction along the inner wall of the body portion 311.
[0053]
In this way, by causing the refrigerant to flow into the gas-liquid separation part 319 from the entire circumference in the circumferential direction along the inner wall of the body part 311, the dynamic pressure acting on the refrigerant liquid level A in the gas-liquid separation part 319 is uniform. To a low value. Thereby, disorder of the refrigerant | coolant liquid level A can be reduced and a gas-liquid separation effect | action can be exhibited favorably.
Further, the flow of the low-temperature condensed refrigerant that flows down from the entire circumference in the circumferential direction along the inner wall of the body portion 311 can maintain the liquid refrigerant in the gas-liquid separation unit 319 at a lower temperature than the surrounding high-temperature atmosphere. The volume inside the liquid receiver 31 can be effectively used as a liquid storage space up to the top.
[0054]
(Other embodiments)
The present invention is not limited to the above-described embodiment and can be variously modified as follows.
(1) In the above-described embodiment, the case where the partition member 317 or the refrigerant guide member 322 is made of aluminum and joined to the body portion 311 of the liquid receiver 31 by brazing has been described, but for example, the partition member 317 or The refrigerant guide member 322 may be made of resin and may be incorporated into the liquid receiver 31 after the heat exchanger is brazed.
[0055]
(2) In the above-described embodiment, the liquid receiver 31 is integrated with the second header tank 22 not provided with the refrigerant inlet / outlet joints 26 and 27, but the refrigerant inlet / outlet joints 26 and 27 are provided. The liquid receiver 31 may be integrated with the first header tank 21.
(3) The present invention may be applied to a liquid receiver-integrated refrigerant condenser in which the core portion 23 of the condenser 2 is only the condensing portion 34 and the supercooling portion 35 is separated from the core portion 23 and configured independently. it can.
[0056]
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.
Further, the present invention can be similarly implemented in a refrigeration apparatus that does not have the supercooling unit 35.
[Brief description of the drawings]
FIG. 1 is a front view showing a refrigerant condenser according to a first embodiment of the present invention, in which a liquid receiver side portion is shown in a sectional view.
FIG. 2 is a front view showing a refrigerant condenser according to a second embodiment of the present invention, in which a liquid receiver side portion is shown in a cross-sectional view.
FIG. 3 is a front view showing a refrigerant condenser according to a third embodiment of the present invention, in which a liquid receiver side portion is shown in a cross-sectional view.
[Explanation of symbols]
21 ... 1st header tank, 21a, 21b, 21c ... space,
22 ... 2nd header tank, 22a, 22b, 22c ... space, 23 ... core part,
24 ... Tube, 26 ... Inlet side piping joint (inlet), 31 ... Liquid receiver,
32 ... Refrigerant inlet, 33 ... Refrigerant outlet, 34 ... Condensing part, 35 ... Supercooling part,
317 ... Partition member, 318 ... Refrigerant guide passage, 319 ... Gas-liquid separation part,
320: gap, 322: refrigerant guide member.

Claims

A core (23) for cooling and condensing the refrigerant gas discharged from the compressor (1);
A liquid receiver (31) that separates the gas-liquid of the refrigerant after condensing in the core portion (23) and stores the liquid refrigerant is integrally configured so that the liquid receiver (31) extends vertically. In the receiver-integrated refrigerant condenser to be arranged ,
A cylindrical partition member (317) extending in the vertical direction is disposed in the liquid receiver (31),
The upper end (317b) of the partition member (317) is open,
The partition member (317) forms a refrigerant guide passage (318) extending in the circumferential direction and the vertical direction along the inner wall of the liquid receiver (31), and
Forming a refrigerant gas-liquid separator (319) inside the partition member (317);
A refrigerant inlet (32) through which the refrigerant condensed in the core portion (23) flows into the refrigerant guide passage (318) is disposed at a lower portion of the refrigerant guide passage (318);
The refrigerant from the refrigerant inlet (32) rises in the refrigerant guide passage (318) along the entire circumference of the inner wall of the liquid receiver (31),
Forming a gap (320) between the upper end (317b ) of the partition member (317) and the upper wall (312) of the receiver (31);
Flowing the refrigerant reaches the upper end rises the refrigerant guide passage (318) (317b) in said gas-liquid separator from the circumferential direction of the upper end portion (317b) (319) in through the gap (320) A receiver-integrated refrigerant condenser characterized by that.

The core portion (23) has an inlet (26) for the refrigerant gas from the compressor (1) disposed above,
The refrigerant collecting part (22b) after being condensed in the core part (23) is disposed below,
The receiver-integrated refrigerant condenser according to claim 1, wherein the condensed refrigerant flows into the refrigerant inlet (32) from the collecting portion (22b).

The cylindrical surface of the partition member (317) is provided with a communication hole (321) that allows the refrigerant guide passage (318) to directly communicate with the gas-liquid separator (319). Item 3. The receiver-integrated refrigerant condenser according to Item 1 or 2.

The receiver-integrated refrigerant condensation according to claim 3, wherein a plurality of the communication holes (321) are provided in a circumferential direction and a vertical direction of a cylindrical surface of the partition member (317). vessel.

The core part (23) has a tube (24) arranged in a horizontal direction and through which a refrigerant flows,
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 integrally joined to any one of the first header tank (21) and the second header tank (22), according to any one of claims 1 to 4. The liquid receiver integrated refrigerant condenser as described.

A supercooling part (35) for supercooling the liquid refrigerant separated by the gas-liquid separation part (319) is provided integrally with the core part (23),
Any one of claims 1 to 5, characterized in that a refrigerant outlet (33) for guiding the liquid coolant in the vicinity of the bottom of the liquid receiver (31) wherein the supercooling part retirement (35) The receiver-integrated refrigerant condenser described in 1.