JP3617083B2

JP3617083B2 - Receiver integrated refrigerant condenser

Info

Publication number: JP3617083B2
Application number: JP22543294A
Authority: JP
Inventors: 弘樹松尾; 康司山中; 健一藤原
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 1993-10-12
Filing date: 1994-09-20
Publication date: 2005-02-02
Anticipated expiration: 2020-02-02
Also published as: JPH07180930A

Description

【０００１】
【産業上の利用分野】
この発明は、例えば冷媒循環量が変動可能な車両用空気調和装置に用いられる受液器一体型冷媒凝縮器に関するものである。
【０００２】
【従来の技術】
従来より、車両用空気調和装置の冷凍サイクルの受液器と凝縮器とは別個独立して配置されている。そのため、部品点数の低減即ちコスト低減が困難であり、また受液器と凝縮器とで互いに取付スペースを占めるため、省スペースの要望に応えることができないという不具合があった。そこで、その不具合を解消する目的で、米国特許第４９７２６８３号公報に開示された技術や実開平２−１０３６６７号公報に開示された技術が提案されている。
【０００３】
先ず、米国特許第４９７２６８３号公報に開示された技術は、冷媒凝縮器の片側ヘッダ内の気液分離室の断面積を大きくして冷媒の流速を落とすことにより気相冷媒の浮力を利用して気液分離させるものであった。次に、実開平２−１０３６６７号公報に開示された技術は、冷媒凝縮器の出口側ヘッダの内部を２部屋に区画する仕切り部材に２部屋を連通するための貫通路を設け、出口側ヘッダの片側の部屋を気液分離室として用いるものであった。
【０００４】
【発明が解決しようとする課題】
ところが、米国特許第４９７２６８３号公報に開示された技術においては、凝縮用チューブの流路径が微細で、しかも数多く気液二相状態の冷媒を吹き出す。このために、凝縮用チューブから出る気泡状の気相冷媒が小さいので、浮力の効果が期待できず、容易に気相冷媒を気液分離室より下流へ送り出してしまう。したがって、冷媒凝縮器より下流側に接続された温度作動式膨張弁で流動音が発生する等の問題が発生してしまう。
【０００５】
そこで、温度作動式膨張弁に気相冷媒が送り込まれないようにするために、凝縮部と過冷却部を上下に配した冷媒凝縮器も考えられるが、この冷媒凝縮器の場合でも気液分離室へ冷媒を導く凝縮用チューブのうちの最下部の凝縮用チューブと気液分離室から液相冷媒のみを送り出すための過冷却用チューブのうちの最上部の過冷却用チューブとの距離が接近する。このため、容易に気相冷媒を気液分離室より下流側の過冷却部へ送り出し易く、過冷却部が有効に働かない。
【０００６】
また、実開平２−１０３６６７号公報に開示された技術において、気液分離室内への冷媒流入口が気液分離室の上部にある場合は、特に冷媒圧縮機を高速運転した時のように冷媒循環量が大きい場合は、気液分離室内の断面積がかなり大きくないと、気液分離室内で気液界面ができない。したがって、気液分離室の下流側へ気相冷媒を送り出すことになる。
【０００７】
そして、気液分離室内への冷媒流入口が気液分離室の下部（但し気液分離室内からの冷媒流出口よりも上方）にある場合は、気液分離室の冷媒流入口と冷媒流出口の距離が近く、また気液分離室の冷媒流入口から冷媒流出口への冷媒の流れのベクトル方向が同じである。このため、気液分離室の下流側へ容易に気相冷媒を送り出してしまうため、前述の問題が発生する。
【０００８】
この発明の目的は、仮に凝縮部の最下部と過冷却部の最上部とが接近していても、受液部の気液分離室内での冷媒の気液分離性を維持し、且つ受液部の気液分離室より下流の過冷却部へ簡単に気相冷媒が流出しないようにすることが可能な受液器一体型冷媒凝縮器を提供することにある。
【０００９】
【課題を解決するための手段】
この発明は、内部を流れる冷媒を凝縮する凝縮部、およびこの凝縮部で凝縮された冷媒を過冷却する過冷却部を上下に配設したコアと、このコアの一端部において上下方向に延ばされ、上側部に前記凝縮部の下流端が接続され、下側部に前記過冷却部の上流端が接続され、内部を、前記凝縮部の下流端のみに連通する上流側連通室と前記過冷却部の上流端のみに連通する下流側連通室とに区画する第１仕切り部を有するタンク部と、内部に、流入した冷媒を気液分離する気液分離室を有し、且つこの気液分離室と前記上流側連通室および前記下流側連通室とを仕切る第２仕切り部を有する受液部とを備えた受液器一体型冷媒凝縮器であって、前記第２仕切り部は、前記上流側連通室の下部で開口し、かつ前記受液部の下側で開口し、前記上流側連通室より前記気液分離室内へ冷媒を流入させる冷媒流入口、およびこの冷媒流入口より下方で開口し、かつ前記受液部の下部で開口し、前記気液分離室より前記下流側連通室内へ冷媒を流出させる冷媒流出口を有し、前記冷媒流入口から前記気液分離室を通って前記冷媒流出口までの冷媒流路のみで前記上流側連通室と前記下流側連通室とが連通されている技術手段を採用した。
別の発明では、熱交換を行うコア（１４）、このコア（１４）の水平方向の一端側に配された第１ヘッダ（１５）、および前記コア（１４）の水平方向の他端側に配された第２ヘッダ（１６）とを備え、前記第２ヘッダ（１６）に受液部（９）を一体成形、又は前記第２ヘッダ（１６）の外側に別部品で設けた受液部を接続してなり、前記コア（１４）は凝縮部（８）および過冷却部（１０）よりなり、前記受液部は内部に気液分離室を有し、炉中にて一体ろう付けして製造された受液器一体型冷媒凝縮器（３）であって、前記第２ヘッダ（１６）は、上下方向に延びる筒状を呈し、タンク部を構成するヘッダプレート（３６）を備え、前記タンク部は、前記凝縮部の下流端のみに連通する上流側連通室と、前記過冷却部の上流端のみに連通する下流側連通室とに、第１仕切り部（４２）によって区画されており、前記第２ヘッダ（１６）と前記受液部（９）とは第２仕切り部（４１）によって区画されており、前記第２仕切り部（４１）には、前記上流側連通室の下部で開口し、かつ前記受液部の下側で開口し、前記上流側連通室より前記気液分離室内へ冷媒を流入させる冷媒流入口（４４）、およびこの冷媒流入口より下方で開口し、かつ前記受液部の下部で開口し、前記気液分離室より前記下流側連通室内へ冷媒を流出させる冷媒流出口（４５）を有し、前記冷媒流入口（４４）から前記気液分離室（４８）を通って前記冷媒流出口（４５）までの冷媒流れがＵターン流れとなっており、前記冷媒流入口から前記気液分離室を通って前記冷媒流出口までの冷媒流路のみで前記上流側連通室と前記下流側連通室とが連通されていることを特徴とする受液器一体型冷媒凝縮器を採用した。
【００１０】
なお、前記受液部を、前記タンク部に一体成形しても良い。また、前記受液部を、前記ヘッダに間接的または直接的に接続しても良い。さらに、過冷却部よりも下流に、冷媒の状態を観察するためのサイトグラスを接続しても良い。そして、気液分離室内の上部に、冷媒中の水分を取り除くドライヤを設けても良い。
【００１１】
【作用】
この発明によれば、凝縮部より流出した気液二相状態の冷媒をタンク部の上流側連通室内に一旦集め、その後に受液部の第２仕切り部の冷媒流入口を介して受液部の気液分離室内へ送り出すようにしている。これにより、凝縮部より出る細かい気泡状の気相冷媒がタンク部の上流側連通室で集められて径の大きい気泡状の気相冷媒となって浮力の影響を大きく受けるようになり、受液部の気液分離室内で気液分離し易くなる。
また、タンク部の第１仕切り部により、第２仕切り部の冷媒流入口から気液分離室を通って第２仕切り部の冷媒流出口までの冷媒の流れがＵターン流れとなっているので、気液が遠心力により分離し気泡状の気相冷媒がより集まることで気泡状の気相冷媒の径がより大きくなり、浮力の影響を大きく受けて気液分離がよりし易くなる。
【００１２】
そして、仮に凝縮部の最下部と過冷却部の最上部とが接近していても、タンク部の第１仕切り部により凝縮部の下流端から過冷却部の上流端までの流路長さが長くなり、気液分離室から過冷却部へ分離できていない気泡状の気相冷媒を送り出すことがなくなる。
そして、受液部の気液分離室の下流側に過冷却部が設けられているため、気液分離室での気液分離が完全でなくても、過冷却部にて気泡状の気相冷媒は消滅するので、気液分離室の容積、つまり気液分離室の断面積を小さくすることが可能となり、凝縮部と過冷却部の有効放熱面積が小さくならない。
【００１３】
【実施例】
次に、この発明の受液器一体型冷媒凝縮器を自動車用空気調和装置に適用した実施例に基づいて説明する。
【００１４】
〔第１実施例の構成〕
図１ないし図４はこの発明の第１実施例を示したもので、図１は自動車用空気調和装置の冷凍サイクルを示した図である。この自動車用空気調和装置の冷凍サイクル１は、冷媒圧縮機２、受液器一体型冷媒凝縮器３、サイトグラス４、膨張弁５および冷媒蒸発器６を、金属製パイプまたはゴム製パイプよりなる冷媒配管７によって順次接続されている。
【００１５】
冷媒圧縮機２は、自動車のエンジンルーム（図示せず）内に設置されたエンジンＥにベルト（図示せず）と電磁クラッチ（図示せず）を介して連結されている。この冷媒圧縮機２は、エンジンＥの回転動力が伝達されると、冷媒蒸発器６より内部に吸入した気相冷媒を圧縮して、高温高圧の気相冷媒を受液器一体型冷媒凝縮器３へ吐出する。
【００１６】
受液器一体型冷媒凝縮器３は、凝縮部８、受液部９および過冷却部１０を一体的に設けている。凝縮部８は、冷媒圧縮機２の吐出側に接続され、冷媒圧縮機２より内部に流入した気相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凝縮液化させる凝縮器として働く。
【００１７】
受液部９は、凝縮部８より内部に流入した気液二相状態の冷媒を気相冷媒と液相冷媒とに気液分離して、液相冷媒のみ過冷却部１０に供給する受液器として働く。過冷却部１０は、凝縮部８より下方に隣接して設けられ、受液部９より内部に流入した液相冷媒をクーリングファン等により送られてくる室外空気と熱交換させて液相冷媒を過冷却する過冷却器として働く。
【００１８】
サイトグラス４は、受液器一体型冷媒凝縮器３の過冷却部１０より下流側に接続され、冷凍サイクル１内を循環する冷媒の状態を観察するものである。このサイトグラス４は、自動車のエンジンルーム内において点検者が視認し易い場所、例えば受液器一体型冷媒凝縮器３に隣設した冷媒配管７の途中に単独で架装されている。
【００１９】
そして、サイトグラス４は、図１に示したように、両端部が冷媒配管７に溶接や締結等の手段で接続される管状の金属ボディ１１、およびこの金属ボディ１１の上面に形成された覗き窓１２に嵌め込まれた溶着ガラス１３等より構成されている。一般に覗き窓１２から気泡が見られるときは冷媒不足であり、気泡が見られないときは冷媒量が適正量である。
【００２０】
膨張弁５は、冷媒蒸発器６の冷媒入口部側に接続され、サイトグラス４より流入した高温高圧の液相冷媒を断熱膨張して低温低圧の霧状冷媒にするもので、本例では冷媒蒸発器６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温度作動式膨張弁が用いられている。
【００２１】
冷媒蒸発器６は、冷媒圧縮機２の吸入側と膨張弁５の下流側との間に接続され、膨張弁５より内部に流入した気液二相状態の冷媒をブロワ（図示せず）により吹き付けら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気化させる熱交換器として働く。
【００２２】
次に、この実施例の受液器一体型冷媒凝縮器３を図２ないし図４に基づいて詳細に説明する。この受液器一体型冷媒凝縮器３は、例えば高さが３００ｍｍ〜４００ｍｍ、幅が３００ｍｍ〜６００ｍｍで、自動車のエンジンルーム内の走行風を受け易い場所に取付ブラケット（図示せず）を介して一体的に取り付けられている。そして、受液器一体型冷媒凝縮器３は、熱交換を行うコア１４、このコア１４の水平方向の一端側に配された第１ヘッダ１５、およびコア１４の水平方向の他端側に配された第２ヘッダ１６等から構成され、炉中にて一体ろう付けして製造される。
【００２３】
コア１４は、凝縮部８および過冷却部１０よりなり、上端部および下端部に受液器一体型冷媒凝縮器３を自動車に取り付けるための取付用ブラケットを固定するサイドプレート１７、１８がろう付け等の手段により接合されている。凝縮部８は、複数の凝縮用チューブ１９およびコルゲートフィン２０よりなり、これらはろう付け等の手段により接合されている。過冷却部１０は、複数の過冷却用チューブ２１およびコルゲートフィン２２よりなり、これらはろう付け等の手段により接合されている。
【００２４】
なお、サイドプレート１７、１８は、アルミニウムまたはアルミニウム合金でろう材でクラッド処理した金属プレートをプレス加工することによって形状が得られ、水平方向の両端部にそれぞれ第１ヘッダ１５および第２ヘッダ１６に差し込まれる挿入片１７１、１７２、１８１、１８２が形成されている。
【００２５】
複数の凝縮用チューブ１９および過冷却用チューブ２１は耐腐食性、熱伝導性に優れたアルミニウムまたはアルミニウム合金等でろう材をクラッド処理したプレートを押出し加工することによって断面形状が偏平な長円形状に形成され、内部に複数の冷媒流路を有している。また、コルゲートフィン２０、２２は、冷媒の放熱効率を向上させるための放熱フィンで、両側面をろう材でクラッド処理したアルミニウムまたはアルミニウム合金等の金属プレートをコルゲート状にプレス加工したものである。
【００２６】
なお、複数の凝縮用チューブ１９および複数の過冷却用チューブ２１は水平方向に配されている。そして、複数の凝縮用チューブ１９内を流れる冷媒は第１ヘッダ１５から第２ヘッダ１６へ流れ、複数の過冷却用チューブ２１内を流れる冷媒は逆に第２ヘッダ１６から第１ヘッダ１５へ流れる。また、この実施例では、凝縮用チューブ１９の本数を、過冷却用チューブ２１の本数より多くしてあり、実験的経験によれば、過冷却用チューブ２１の本数はコア１４の全体の１５％〜２０％程度が好ましい。
【００２７】
第１ヘッダ１５は、断面形状が略Ｕ字状のヘッダプレート２３および断面形状が半円弧状のタンクプレート２４よりなり、上下方向に延びる円筒形状を呈する。この第１ヘッダ１５は、それぞれ耐腐食性および熱伝導性に優れたアルミニウムまたはアルミニウム合金で両側面をろう材でクラッド処理した金属プレートをプレス加工することによって所定の形状を得ている。
【００２８】
また、第１ヘッダ１５の上側部は凝縮部８を構成する複数の凝縮用チューブ１９の上流端が接続され、下側部は過冷却部１０を構成する複数の過冷却用チューブ２１の下流端が接続されている。そして、第１ヘッダ１５の上下方向（板長さ方向）の上下端部の開口部には、キャップ２５が嵌め込まれている。
【００２９】
なお、キャップ２５は、アルミニウムまたはアルミニウム合金でろう材でクラッド処理した金属プレートをプレス加工することによって形状が得られ、第１ヘッダ１５の上下端部にろう付け等の手段により接合される略円環状の接合片２５１と、この接合片２５１より窪んでおり、上下端部の開口部を塞ぐ略円板状の閉塞部２５２とを有している。
【００３０】
ヘッダプレート２３には、プレス加工によって、長円形状の抜き穴２６が多数形成され、上下端部に貫通穴２７がそれぞれ形成されている。その多数の抜き穴２６には、複数の凝縮用チューブ１９の上流端および複数の過冷却用チューブ２１の下流端が差し込まれた状態でろう付け等の手段により接合されている。また、２個の貫通穴２７には、サイドプレート１７、１８の挿入片１７１、１８１が差し込まれた状態でろう付け等の手段により接合されている。
【００３１】
タンクプレート２４には、プレス加工によって、内部を上下に仕切るセパレータ２８を固定する穴部２９、入口配管３０を固定する円形状の冷媒吸入口３１および出口配管３２を固定する円形状の冷媒吐出口３３が形成されている。そのセパレータ２８は、略円板形状に形成され、第１ヘッダ１５の内部を、凝縮部８の上流端のみに連通する入口側連通室３４と過冷却部１０の下流端のみに連通する出口側連通室３５とに分割するものである。
【００３２】
入口配管３０は、円管形状を呈し、冷媒圧縮機２より吐出された高温高圧の気相冷媒を入口側連通室３４内に流入させるための配管で、ろう付け等の手段により冷媒吸入口３１に接合されている。また、出口配管３２は、円管形状を呈し、出口側連通室３５内の液相冷媒をサイトグラス４へ送り出す配管で、ろう付け等の手段により冷媒吐出口３３に接合されている。
【００３３】
第２ヘッダ１６は、図４にも示したように、断面形状が略Ｕ字状のヘッダプレート３６および断面形状が略Ｒ形状の筒状体３７よりなり、上下方向に延びる二重筒状を呈し、受液部９がタンク部に一体成形されている。この第２ヘッダ１６は、それぞれ耐腐食性および熱伝導性に優れたアルミニウムまたはアルミニウム合金で所定の形状を得ている。なお、本例では、ヘッダプレート３６と筒状体３７の図示左側部分とでタンク部を構成し、筒状体３７の筒部分で受液部９を構成している。
【００３４】
また、第２ヘッダ１６の上側部は凝縮部８を構成する複数の凝縮用チューブ１９の下流端が接続され、下側部は過冷却部１０を構成する複数の過冷却用チューブ２１の上流端が接続されている。そして、第２ヘッダ１６の上下方向（板長さ方向）の上下端部の開口部には、キャップ３８が嵌め込まれている。
【００３５】
なお、キャップ３８は、第２ヘッダ１６の上下端部にろう付け等の手段により接合される略円環状の接合片３８１と、この接合片３８１より窪んでおり、第２ヘッダ１６の上下端部の内側の開口部を塞ぐ略円板状の閉塞部３８２と、第２ヘッダ１６の上下端部の外側の開口部を塞ぐ偏平な楕円形状の閉塞部３８３とを有している。
【００３６】
ヘッダプレート３６には、両側面をろう材でクラッド処理した金属プレートをプレス加工することによって、長円形状の抜き穴３９が多数形成され、上下端部に貫通穴４０がそれぞれ形成されている。その多数の抜き穴３９には、複数の凝縮用チューブ１９の下流端および複数の過冷却用チューブ２１の上流端が差し込まれた状態でろう付け等の手段により接合されている。また、２個の貫通穴４０には、サイドプレート１７、１８の挿入片１７２、１８２が差し込まれた状態でろう付け等の手段により接合されている。
【００３７】
筒状体３７は、押出し加工にて所定の形状に形成され、内側部に第２ヘッダ１６内を第１の部屋と第２の部屋とに２分割（区画）する第１セパレータ４１を有している。この第１セパレータ４１には、プレス加工による追加工によって、第１の部屋の内部を上側の部屋（上流側連通室４６）と下側の部屋（下流側連通室４７）とに２分割（区画）する第２セパレータ４２を固定する穴部４３、第１の部屋と第２の部屋とを連通する円形状の冷媒流入口４４および円形状の冷媒流出口４５が形成されている。
【００３８】
第１セパレータ４１および第２セパレータ４２は、凝縮部８の下流端のみに連通する上流側連通室４６と過冷却部１０の上流端のみに連通する下流側連通室４７と外側に形成される受液部９を構成する気液分離室４８とに、第２ヘッダ１６の内部を３分割する仕切り部である。また、第１セパレータ４１は本発明の第２仕切り部を構成し、第２セパレータ４２は本発明の第１仕切り部を構成する。
【００３９】
なお、冷媒流入口４４は上流側連通室４６の下部（凝縮部８の最下部）で開口し、上流側連通室４６内の冷媒を気液分離室４８内に流入させる連通口で、冷媒流出口４５は冷媒流入口４４より下方で開口し、気液分離室４８内の冷媒を下流側連通室４７内に流出させる連通口である。また、気液分離室４８は、上流側連通室４６より内部に流入した冷媒を気相冷媒と液相冷媒とに分離して液相冷媒のみを下流側連通室４７へ送り出す。
【００４０】
〔第１実施例の作用〕
次に、この実施例の自動車用空気調和装置の冷凍サイクル１の作用を図１および図２に基づいて簡単に説明する。自動車用空気調和装置の運転が開始されると、電磁クラッチが通電され、冷媒圧縮機がベルトと電磁クラッチを介してエンジンＥによって回転駆動される。
【００４１】
このため、冷媒圧縮機２内で圧縮されて吐出された高温高圧の気相冷媒は、入口配管３０を通って第１ヘッダ１５の入口側連通室３４内に流入する。入口側連通室３４内に流入した気相冷媒は、入口側連通室３４内で凝縮部８を構成する複数の凝縮用チューブ１９に分配される。
【００４２】
そして、複数の凝縮用チューブ１９に分配された気相冷媒は、これらの凝縮用チューブ１９を通過する際にコルゲートフィン２０を介して室外空気と熱交換して凝縮液化され、一部の気相冷媒を残してほとんど液相冷媒となる。このような気液二相状態の冷媒は、複数の凝縮用チューブ１９より第２ヘッダ１６の上流側連通室４６内に流入する。上流側連通室４６内に流入した気液二相状態の冷媒は、一旦集められた後に、冷媒流入口４４を通って受液部９（気液分離室４８）内へ流入する。
【００４３】
受液部９（気液分離室４８）では、その断面積をある程度大きく（例えば５００ｍｍ^２）とることで冷媒の速度を低減させ、且つ気泡状の気相冷媒の浮力を利用している。さらに、第２セパレータ４２によって、複数の凝縮用チューブ１９のうちの最下部の凝縮用チューブ１９の下流端から複数の過冷却用チューブ２１のうちの最下部の過冷却用チューブ２１の上流端までの流路長さを長くとっている。
【００４４】
その上、第２セパレータ４２によって、複数の凝縮用チューブ１９から第２ヘッダ１６内に流入した冷媒がＵターンして複数の過冷却用チューブ２１へ流出するようにしているので、気液二相状態の冷媒が遠心力により気液分離し気泡状の気相冷媒がより一箇所（内側）に集められる。
【００４５】
すなわち、冷媒流入口４４が上流側連通室４６の下部で開口しており、冷媒流入口４４と冷媒流出口４５とが比較的に接近しているので、気液二相状態の冷媒が冷媒流入口４４→受液部９→冷媒流出口４５を通過する時に、遠心力を受けて比重の大きい液相冷媒が筒状体３７の外側部に移行し、比重の小さい気泡状の気相冷媒が第２セパレータ４２の受液部９内への突出部分に集まる。
【００４６】
したがって、受液部９内で気液二相状態の冷媒が効率良く気液分離するため、受液部９の上部に気相冷媒が、下部に液相冷媒が溜まることになる。よって、受液部９内において気液界面ができるだけの十分な冷媒が冷凍サイクル１内に充填されているならば、受液部９の下部にある冷媒流出口４５からは過冷却度を持たない液相冷媒のみが下流側連通室４７内に流入する。下流側連通室４７内に流入した液相冷媒は、下流側連通室４７内で過冷却部１０を構成する複数の過冷却用チューブ２１に分配される。
【００４７】
そして、複数の過冷却用チューブ２１に分配された液相冷媒は、これらの過冷却用チューブ２１を通過する際にコルゲートフィン２２を介して室外空気と熱交換して過冷却され、過冷却度を持つ液相冷媒となり、第１ヘッダ１５の出口側連通室３５内に流入する。
【００４８】
出口側連通室３５内に流入した液相冷媒は、出口配管３２、サイトグラス４を通って膨張弁５内へ流入する。なお、膨張弁５内には気相冷媒を含まない単相の液相冷媒が供給されるため、膨張弁５内に流入する液相冷媒の冷媒循環量が低下することはない。これにより、十分な量の霧状冷媒が冷媒蒸発器６内へ供給されるので、自動車用空気調和装置の冷凍能力を低下を防止することができる。
【００４９】
〔第１実施例の効果〕
以上のように、自動車用空気調和装置の冷凍サイクル１は、上流側連通室４６の下部、つまり受液部９の下側で冷媒流入口４４が開口しているので、特に冷媒圧縮機２を高速運転した時のように冷媒循環量が大きい場合でも、受液部９の断面積を異様に大きくしなくても、受液部９内で気液界面ができる。
【００５０】
また、複数の凝縮用チューブ１９の下流端より流出した気液二相状態の冷媒を第２ヘッダ１６の上流側連通室４６内にて一旦集め、その後に上流側連通室４６の下部で開口する冷媒流入口４４を介して受液部９内へ送り出すようにしている。これにより、複数の凝縮用チューブ１９の下流端より出る細かい気泡状の気相冷媒が上流側連通室４６内で集められて径の大きい気泡状の気相冷媒となって浮力の影響を大きく受けるようになる。
【００５１】
そして、凝縮部８の下流端と過冷却部１０の上流端との境界の位置に設置した第２セパレータ４２の存在により、冷媒流入口４４から受液部９を通って冷媒流出口４５までの冷媒の流れがＵターン流れ（逆方向のベクトル）となっている。このため、気液が遠心力により分離し気泡状の気相冷媒がより集まることで気泡状の気相冷媒の径がより大きくなり、浮力の影響をより大きく受けて気液分離がよりし易くなる。したがって、冷媒流入口４４より受液部９内へ流入した際に気液分離し易くなり、受液部９内において気相冷媒が上方に液相冷媒が下方に滞留するようになる。
【００５２】
そして、仮に複数の凝縮用チューブ１９のうちの最下部の凝縮用チューブ１９と複数の過冷却用チューブ２１のうちの最上部の過冷却用チューブ２１とが接近していても、凝縮部８の下流端と過冷却部１０の上流端との境界の位置に設置した第２セパレータ４２の存在により複数の凝縮用チューブ１９の下流端から複数の過冷却用チューブ２１の上流端までの流路長さが長くなっている。これにより、受液部９から複数の過冷却用チューブ２１、サイトグラス４および膨張弁５へ分離できていない気泡状の気相冷媒を流出させることがなくなり、過冷却部１０を有効に働かせることができ、且つ膨張弁５での流動音の発生を防止することができる。
【００５３】
そして、受液部９の下流側に過冷却部１０が設けられているため、受液部９での気液分離が完全でなくても、過冷却部１０にて気泡状の気相冷媒は完全に消滅するので、受液部９の容積、つまり受液部９の断面積を小さくすることができ、コア１４の凝縮部８と過冷却部１０の有効放熱面積が縮小化することを防止することができる。
【００５４】
また、この実施例では、受液器一体型冷媒凝縮器３を冷媒圧縮機２とサイトグラス４との間に接続しているので、部品点数の低減即ちコスト低減が図られるため、生産性を向上することができる。また、自動車のエンジンルーム内にコンパクトに収めることができるため、省スペースとなる。
【００５５】
なお、この実施例では、サイトグラス４を過冷却部１０より下流側に接続しているため、受液部９での気液分離性を確実にする必要はなく、受液部９の容積、つまり受液部９の断面積は冷凍サイクル１の負荷変動による冷媒変動量と冷媒漏れに対する余裕量の分だけ見込んでおけば良い。
【００５６】
〔第２実施例〕
図５はこの発明の第２実施例を示したもので、受液器一体型冷媒凝縮器を示した図である。この実施例では、第１ヘッダ１５および第２ヘッダ１６内に、凝縮部８を構成する複数の凝縮用チューブ１９と連通している部屋を第２セパレータ５１、５２により２分割して中間連通室５３および上流側連通室５４を追加し、凝縮部８内での冷媒の流し方をＳターンとしている。
なお、凝縮部８内での冷媒の流し方はセパレータをさらに増やすことでターン数を増やしても良い。但し、凝縮部８内への冷媒吸入口３１と受液部９内への冷媒流入口４４とは相反する位置に設ける必要がある。
【００５７】
〔第３実施例の構成〕
図６および図７はこの発明の第３実施例を示したもので、図６は受液器一体型冷媒凝縮器を示した図で、図７は受液器一体型冷媒凝縮器の受液部を示した図である。この実施例の受液部９（気液分離室４８）内の上部には、冷媒中の水分を取り除くドライヤ６１が組み込まれている。ドライヤ６１は、キャップ３８の楕円形状の閉塞部３８３と楕円形状のホルダ（押さえ）６２に保持されたフィルタ６３との間に設けられている。また、ドライヤ６１は、合成ゼオライト、アルミナゲル、シリカゲル等のシリカアルミナ吸着剤などの多数のフロン系冷媒用乾燥剤（以下乾燥剤と略す）６１１が用いられている。
【００５８】
ホルダ６２は、多数の小穴６４が開けられたパンチングメタルよりなる。なお、フィルタ６３の材質として剛性のあるものを用いた場合にはホルダ６２を設けなくても良い。
フィルタ６３は、例えば耐高温性に優れるセラミックスや金属等よりなり、ドライヤ６１を構成する多数の乾燥剤６１１が長期間使用している間に崩壊したり、磨耗して微粉化して冷凍サイクル内に流出するのを防止するものである。
【００５９】
ここで、ドライヤ６１の組み付け方法を簡単に説明する。先ず、第２ヘッダ１６の筒状体３７内にホルダ６２を圧入して所定の位置に止める。そして、フィルタ６３を第２ヘッダ１６の筒状体３７の上部側開口よりホルダ６２に当接するまで挿入した後に、多数の乾燥剤６１１よりなるドライヤ６１を入れる。そして、第２ヘッダ１６の筒状体３７の上部側開口にキャップ３８の閉塞部３８３を嵌め込んで一体ろう付けすることにより、ドライヤ６１の組み付けがなされる。
【００６０】
〔第３実施例の作用〕
次に、この実施例の受液器一体型冷媒凝縮器３の作用を図６および図７に基づいて簡単に説明する。複数の凝縮用チューブ１９より第２ヘッダ１６の上流側連通室４６内に流入した気液二相状態の冷媒は、一旦集められた後に、冷媒流入口４４を通って受液部９（気液分離室４８）内へ流入する。そして、受液部９内に流入した気液二相状態の冷媒は、第１実施例で説明したように効率良く気液分離して、液相冷媒のみが冷媒流出口４５から下流側連通室４７内に流入する。そして、下流側連通室４７内に流入した液相冷媒は、下流側連通室４７内で過冷却部１０を構成する複数の過冷却用チューブ２１に分配される。
【００６１】
なお、この実施例においては、ドライヤ６１を冷媒の主流流れを受けない場所に設置している。そして、液相冷媒が溜まる部分は受液部９の下部にあるが、気液分離方法は受液部９の下方から気泡が浮力で上昇し、代わりに液相冷媒を受液部９の下方に補う方式のため、受液部９内の気泡の一部は外部（大気）との熱交換により凝縮液化して受液部９の下方に流れる。このため、気液分離した気泡がホルダ６２の多数の小穴６４、フィルタ６３を通って受液部９の上部に設けたドライヤ６１内に一旦入り、凝縮液化して下方に流れ出る際に冷媒中の水分が取り除かれる。
【００６２】
したがって、冷媒の主流の一部ではあるが、常に冷媒中の水分を除去することができる。また、フィルタ６３を冷媒の主流に配置しないことにより、長期間使用してもフィルタ６３の上流と下流との間に上下圧力差が生じることはなく、冷凍サイクルに悪影響を及ぼさない。さらに、フィルタ６３のホルダ６２も冷媒の主流に配置されないので、冷媒の流れの主流と共にホルダ６２が流出することはなく、これによりドライヤ６１の流出を防止できる。よって、膨張弁５や冷媒圧縮機２の弁機構に引っ掛かってその作動を妨げたり、冷媒圧縮機２のピストン、軸受等の摺動部の焼き付きを防ぐことができる。
【００６３】
〔第４実施例〕
図８はこの発明の第４実施例を示したもので、受液器一体型冷媒凝縮器の受液部を示した図である。この実施例のキャップ３８の閉塞部３８３には、ドライヤ６１を挿入するためのドライヤ挿入口６５が開口している。そして、閉塞部３８３の内周には、シール材としての閉塞栓６６の小径部分（下端部）が嵌め合わされている。
【００６４】
そして、この実施例のドライヤ６１の組み付け方法は、第２ヘッダ１６の筒状体３７内にホルダ６２を圧入しておいて受液器一体型冷媒凝縮器３を炉中で一体ろう付けした後に、キャップ３８の閉塞部３８３に形成したドライヤ挿入口６５から受液部９内にフィルタ６３、ドライヤ６１を挿入するようにしている。そして、ドライヤ６１を挿入した後にドライヤ挿入口６５を閉塞栓６６で塞ぐようにしている。
【００６５】
なお、閉塞栓６６は、トーチろう付け法、アルゴンガス溶接法等のドライヤ６１やフィルタ６３にあまり熱が伝わらないような溶接法を用いてキャップ３８に接合すると良い。
また、閉塞栓６６の接合位置とフィルタ６３とはある程度の距離が保たれているので、フィルタ６３の材質として一般的な樹脂材料を用いることができる。
【００６６】
〔第５実施例〕
図９はこの発明の第５実施例を示したもので、受液器一体型冷媒凝縮器の受液部を示した図である。この実施例のキャップ３８の閉塞部３８３には、ドライヤ６１を挿入するためのドライヤ挿入口６５が開口している。そして、閉塞部３８３の内周にはシール材としての閉塞栓６７の小径部分（下端部）が嵌め合わされている。
【００６７】
また、閉塞部３８３は、他の実施例より板厚が厚く形成されており、その上部側の内周に閉塞栓６７の小径部分の上部外周に形成されたおねじ部（外周ねじ部）６７１に螺合するめねじ部（内周ねじ部）６５１が形成されている。閉塞栓６７の外周とキャップ３８の閉塞部３８３の内周との間には、ドライヤ６１の外部への流出を防止するシール材としてのＯリング６８が装着されている。
【００６８】
そして、この実施例のドライヤ６１の組み付け方法は、第２ヘッダ１６の筒状体３７内にホルダ６２を圧入し、受液器一体型冷媒凝縮器３を炉中で一体ろう付けした後に、キャップ３８の閉塞部３８３のドライヤ挿入口６５から受液部９内にフィルタ６３、ドライヤ６１を挿入し、閉塞栓６７をドライヤ挿入口６５にねじ込むようにしている。この実施例の場合には、冷凍サイクルを長期間使用した後に閉塞栓６７を開けてドライヤ６１およびフィルタ６３の取替え（交換）を行うことができる。
【００６９】
〔第６実施例〕
図１０はこの発明の第６実施例を示したもので、受液器一体型冷媒凝縮器の受液部を示した図である。この実施例のキャップ３８の閉塞部３８３には、ドライヤ６１を挿入するためのドライヤ挿入口６５が形成されており、しかもこのドライヤ挿入口６５を閉じる突起片６９が一体成形されている。なお、突起片６９は弾性変形可能に設けられている。
【００７０】
この実施例の場合も、受液器一体型冷媒凝縮器３を炉中で一体ろう付けし、ドライヤ挿入口６５から受液部９内にフィルタ６３、ドライヤ６１を挿入した後に、キャップ３８の突起片６９を閉塞部３８３と同一平面上に位置するように倒してから、ドライヤ６１の流出を防止するためにドライヤ挿入口６５を塞ぐ。そして、第４実施例と同様にして、突起片６９の外周と閉塞部３８３の内周との隙間をろう付けや溶接により塞ぐ。
【００７１】
〔第７実施例〕
図１１はこの発明の第７実施例を示したもので、受液器一体型冷媒凝縮器の受液部を示した図である。この実施例のキャップ３８の閉塞部３８３には、上方に向かって内径が漸減する円錐状部分と円筒部分よりなる筒部７０が形成されている。この筒部７０内には、ドライヤ６１を挿入するためのドライヤ挿入口７１が開口している。そして、筒部７０内にはシール材としての閉塞栓７２の小径部分（下端部）が嵌め合わされている。
【００７２】
また、筒部７０の上部側の内周には、閉塞栓７２の小径部分の上部外周に形成されたおねじ部（外周ねじ部）７２１に螺合するめねじ部（内周ねじ部）７０１が形成されている。閉塞栓７２の小径部分の外周と筒部７０の内周との間には、ドライヤ６１の外部への流出を防止するシール材としてのＯリング７３が装着されている。
【００７３】
この実施例の場合には、ドライヤ挿入口７１からドライヤ６１を受液部（気液分離室４８）内に挿入した後に、閉塞栓７２でドライヤ挿入口７１を塞いだ場合でも、閉塞栓７２の小径部分の下端部がドライヤ６１を構成する多数の乾燥剤６１１の上面に届かず、多数の乾燥剤６１１の上面を平に保つことができる。
【００７４】
さらに、多数の乾燥剤６１１の上面と閉塞栓７２の小径部分の下端部との間を、シール材としてのフェルト（耐水性の重質紙）７４で塞ぐようにしているので、ドライヤ６１を構成する多数の乾燥剤６１１同士に隙間が発生することを防止できる。なお、多数の乾燥剤６１１同士に隙間があると、車両の振動等により乾燥剤６１１が移動することにより乾燥剤６１１同士が磨耗して微粉化し易くなる。
【００７５】
〔変形例〕
この実施例では、本発明を自動車用空気調和装置に適用したが、本発明を鉄道車両、船舶や航空機等のように冷媒循環量が変動するあらゆる空気調和装置に適用しても良い。また、受液器一体型冷媒凝縮器３の放熱を有効利用するヒートポンプ式冷凍サイクルに適用しても良い。
【００７６】
この実施例では、第２ヘッダ１６をヘッダプレート３６と筒状体３７で構成したが、第２ヘッダ１６を押出し成形により一部品で一体成形しても良い。同様に、第１ヘッダ１５も押出し成形により一部品で一体成形しても良い。
また、第２ヘッダ１６を複数の筒状体を上下方向に張り合わせて構成しても良く、さらに第２ヘッダ１６を１個の筒状体で形成して、その筒状体内に別途設けた第１セパレータ４１を嵌め込んでも良い。
この実施例では、第２ヘッダ１６に受液部９を一体成形したが、第２ヘッダ１６の外側に、第２ヘッダ１６と別部品で設けた受液部を接続しても良い。
【００７７】
第３〜第７実施例では、受液部９内にドライヤ６１を構成する多数の乾燥剤６１１を直接挿入したが、フェルト（耐水性の重質紙）製の袋内に多数の乾燥剤６１１を入れたものを受液部９内に挿入しても良い。
第４〜第７実施例では、フィルタ６３の材質として一般的な樹脂材料を用いて一体ろう付け後に受液部９内に挿入したが、フィルタ６３の材質として耐熱材料を用いることにより一体ろう付け前に受液部９内に挿入しておいても良い。
【００７８】
第３〜第７実施例では、第２ヘッダ１６の筒状体３７の上端面、つまり上端側のキャップ３８にドライヤ挿入口６５、７１を形成したが、第２ヘッダ１６の筒状体３７の下端面（下端側のキャップ３８）または筒状体３７の側面等、受液部９の周囲であればどこにドライヤ挿入口を形成しても良い。
【００７９】
【発明の効果】
この発明は、仮に凝縮部の最下部と過冷却部の最上部とが接近していても、タンク部の第１仕切り部により凝縮部の下流端から過冷却部の上流端までの流路長さが長くなるので、受液部の気液分離室内での冷媒の気液分離性を向上させることができる。また、受液部の気液分離室より下流の過冷却部へ気相冷媒が流出し難くなるので、過冷却部を有効に働かせることができ、さらに膨張弁での作動音の発生を防止できる。
【図面の簡単な説明】
【図１】この発明の第１実施例に用いた自動車用空気調和装置の冷凍サイクルを示した構成図である。
【図２】この発明の第１実施例に用いた受液器一体型冷媒凝縮器を示した断面図である。
【図３】図２の受液器一体型冷媒凝縮器の分解図である。
【図４】図２の受液器一体型冷媒凝縮器のタンク部と受液部を一体成形した第２ヘッダを示した断面図である。
【図５】この発明の第２実施例に用いた受液器一体型冷媒凝縮器を示した断面図である。
【図６】この発明の第３実施例に用いた受液器一体型冷媒凝縮器を示した断面図である。
【図７】図６の受液器一体型冷媒凝縮器の受液部を示した断面図である。
【図８】この発明の第４実施例に用いた受液器一体型冷媒凝縮器の受液部を示した断面図である。
【図９】この発明の第５実施例に用いた受液器一体型冷媒凝縮器の受液部を示した断面図である。
【図１０】この発明の第６実施例に用いた受液器一体型冷媒凝縮器の受液部を示した断面図である。
【図１１】この発明の第７実施例に用いた受液器一体型冷媒凝縮器の受液部を示した断面図である。
【符号の説明】
１冷凍サイクル
３受液器一体型冷媒凝縮器
４サイトグラス
８凝縮部
９受液部
１０過冷却部
１４コア
１５第１ヘッダ
１６第２ヘッダ
１９凝縮用チューブ
２１過冷却用チューブ
２５キャップ
３８キャップ
４１第１セパレータ（第２仕切り部）
４２第２セパレータ（第１仕切り部）
４４冷媒流入口
４５冷媒流出口
４６上流側連通室
４７下流側連通室
４８気液分離室
６１ドライヤ
６２ホルダ（押さえ）
６３フィルタ[0001]
[Industrial application fields]
The present invention relates to a receiver-integrated refrigerant condenser used in, for example, a vehicle air conditioner in which the amount of refrigerant circulation is variable.
[0002]
[Prior art]
Conventionally, the liquid receiver and the condenser of the refrigeration cycle of the vehicle air conditioner are arranged separately and independently. For this reason, it is difficult to reduce the number of parts, that is, to reduce the cost, and the receiver and the condenser occupy the mounting space with each other. Therefore, in order to solve the problem, a technique disclosed in US Pat. No. 4,972,683 and a technique disclosed in Japanese Utility Model Laid-Open No. 2-103667 have been proposed.
[0003]
First, the technology disclosed in US Pat. No. 4,972,683 utilizes the buoyancy of a gas-phase refrigerant by increasing the cross-sectional area of the gas-liquid separation chamber in the header on one side of the refrigerant condenser and reducing the flow rate of the refrigerant. Gas-liquid separation was performed. Next, the technology disclosed in Japanese Utility Model Laid-Open No. 2-103667 provides a partition member that divides the interior of the outlet side header of the refrigerant condenser into two chambers, and provides a through passage for communicating the two chambers. The room on one side of was used as a gas-liquid separation chamber.
[0004]
[Problems to be solved by the invention]
However, in the technology disclosed in US Pat. No. 4,972,683, the flow path diameter of the condensing tube is fine, and many refrigerants in a gas-liquid two-phase state are blown out. For this reason, since the gaseous gaseous refrigerant | coolant which exits from the tube for condensation is small, the effect of a buoyancy cannot be anticipated and a gaseous-phase refrigerant | coolant will be easily sent downstream from a gas-liquid separation chamber. Therefore, problems such as the generation of flow noise occur at the temperature-actuated expansion valve connected downstream from the refrigerant condenser.
[0005]
Therefore, in order to prevent the gas-phase refrigerant from being sent to the temperature-actuated expansion valve, a refrigerant condenser in which the condensing unit and the supercooling unit are arranged up and down is conceivable, but even in the case of this refrigerant condenser, gas-liquid separation is also possible. The distance between the lowermost condensing tube of the condensing tube that guides the refrigerant to the chamber and the uppermost subcooling tube of the supercooling tube for sending only the liquid refrigerant from the gas-liquid separation chamber are close to each other To do. For this reason, it is easy to send the vapor-phase refrigerant to the supercooling part downstream from the gas-liquid separation chamber, and the supercooling part does not work effectively.
[0006]
Further, in the technique disclosed in Japanese Utility Model Laid-Open No. 2-103667, when the refrigerant inlet into the gas-liquid separation chamber is at the upper part of the gas-liquid separation chamber, the refrigerant particularly when the refrigerant compressor is operated at high speed. When the circulation amount is large, the gas-liquid interface cannot be formed in the gas-liquid separation chamber unless the cross-sectional area in the gas-liquid separation chamber is very large. Therefore, the gas-phase refrigerant is sent out to the downstream side of the gas-liquid separation chamber.
[0007]
When the refrigerant inlet to the gas-liquid separation chamber is below the gas-liquid separation chamber (but above the refrigerant outlet from the gas-liquid separation chamber), the refrigerant inlet and the refrigerant outlet of the gas-liquid separation chamber And the vector directions of the refrigerant flow from the refrigerant inlet to the refrigerant outlet of the gas-liquid separation chamber are the same. For this reason, since the vapor-phase refrigerant is easily sent out to the downstream side of the gas-liquid separation chamber, the above-described problem occurs.
[0008]
The object of the present invention is to maintain the gas-liquid separation of the refrigerant in the gas-liquid separation chamber of the liquid receiving unit even if the lowermost part of the condensing unit and the uppermost part of the supercooling unit are close to each other, and the liquid receiving unit Another object of the present invention is to provide a receiver-integrated refrigerant condenser capable of easily preventing a gas-phase refrigerant from flowing out to a supercooling section downstream from the gas-liquid separation chamber of the section.
[0009]
[Means for Solving the Problems]
The present invention extends in the vertical direction at a condensing part for condensing the refrigerant flowing in the interior, a core in which a supercooling part for supercooling the refrigerant condensed in the condensing part is arranged up and down, and one end of the core. The upper end is connected to the downstream end of the condensing unit, the lower side is connected to the upstream end of the supercooling unit, and the inside communicates only with the downstream end of the condensing unit and the upstream communication chamber. A tank portion having a first partition section that is divided into a downstream communication chamber that communicates only with the upstream end of the cooling section; and a gas-liquid separation chamber that gas-liquid separates the refrigerant that has flowed therein. A liquid receiver-integrated refrigerant condenser comprising a liquid receiving portion having a second partition portion that partitions the separation chamber from the upstream communication chamber and the downstream communication chamber, wherein the second partition portion includes: Open at the lower part of the upstream communication chamber, and open at the lower side of the liquid receiving part. A refrigerant inlet through which a refrigerant flows from the communication chamber into the gas-liquid separation chamber, and a lower opening than the refrigerant inlet, and an opening at a lower portion of the liquid receiving portion, the downstream communication chamber from the gas-liquid separation chamber Has a refrigerant outlet to let the refrigerant flow out to The upstream communication chamber and the downstream communication chamber communicate with each other only through the refrigerant flow path from the refrigerant inlet to the refrigerant outlet through the gas-liquid separation chamber. Adopted technical means.
In another invention, the core (14) for heat exchange, the first header (15) disposed on one end side in the horizontal direction of the core (14), and the other end side in the horizontal direction of the core (14) And a second header (16) disposed, and a liquid receiving portion (9) is integrally formed with the second header (16), or a liquid receiving portion provided as a separate part outside the second header (16). The core (14) comprises a condensing part (8) and a supercooling part (10), and the liquid receiving part has a gas-liquid separation chamber inside, and is brazed integrally in a furnace. The receiver-integrated refrigerant condenser (3) manufactured in the above-described manner, wherein the second header (16) has a cylindrical shape extending in the vertical direction and includes a header plate (36) constituting a tank portion, The tank part communicates only with an upstream communication chamber that communicates only with the downstream end of the condensing part, and with an upstream end of the supercooling part. And the downstream communication chamber is partitioned by the first partition portion (42), and the second header (16) and the liquid receiving portion (9) are partitioned by the second partition portion (41). The second partition portion (41) opens at a lower portion of the upstream communication chamber and opens below the liquid receiving portion, and the refrigerant flows into the gas-liquid separation chamber from the upstream communication chamber. A refrigerant inlet (44) to be opened, and a refrigerant outlet (opening below the refrigerant inlet and opening at a lower portion of the liquid receiving part, and for allowing the refrigerant to flow out of the gas-liquid separation chamber into the downstream communication chamber ( 45), and the refrigerant flow from the refrigerant inlet (44) through the gas-liquid separation chamber (48) to the refrigerant outlet (45) becomes a U-turn flow. The upstream communication chamber and the downstream communication chamber are communicated only with the refrigerant flow path from the refrigerant inlet to the refrigerant outlet through the gas-liquid separation chamber. The receiver-integrated refrigerant condenser is used.
[0010]
The liquid receiving part may be integrally formed with the tank part. Moreover, you may connect the said liquid receiving part indirectly or directly to the said header. Furthermore, you may connect the sight glass for observing the state of a refrigerant | coolant downstream from a supercooling part. And you may provide the dryer which removes the water | moisture content in a refrigerant | coolant in the upper part in a gas-liquid separation chamber.
[0011]
[Action]
According to this invention, the refrigerant in the gas-liquid two-phase state that has flowed out of the condensing part is once collected in the upstream communication chamber of the tank part, and then the liquid receiving part via the refrigerant inlet of the second partition part of the liquid receiving part. Is sent out into the gas-liquid separation chamber. As a result, the fine bubble-like gas-phase refrigerant coming out of the condensing part is collected in the upstream communication chamber of the tank part to become a bubble-like gas-phase refrigerant having a large diameter, and is greatly affected by buoyancy. Gas-liquid separation is facilitated in the gas-liquid separation chamber of the part.
In addition, because the first partition portion of the tank portion makes the U-turn flow of the refrigerant from the refrigerant inlet port of the second partition portion to the refrigerant outlet port of the second partition portion through the gas-liquid separation chamber, The gas-liquid is separated by the centrifugal force and the gas-phase gas-phase refrigerant is more concentrated, so that the diameter of the gas-phase gas-phase refrigerant is increased, and the gas-liquid separation is more easily affected by the influence of buoyancy.
[0012]
Even if the lowermost part of the condensing part and the uppermost part of the supercooling part are close to each other, the first partition part of the tank part causes the flow path length from the downstream end of the condensing part to the upstream end of the supercooling part. It becomes long, and the gaseous gaseous refrigerant which has not been separated from the gas-liquid separation chamber to the supercooling section is not sent out.
And since the supercooling part is provided in the downstream of the gas-liquid separation chamber of a liquid receiving part, even if the gas-liquid separation in a gas-liquid separation chamber is not perfect, a bubble-like gaseous phase in a supercooling part Since the refrigerant disappears, the volume of the gas-liquid separation chamber, that is, the cross-sectional area of the gas-liquid separation chamber can be reduced, and the effective heat radiation area of the condensing unit and the supercooling unit is not reduced.
[0013]
【Example】
Next, the receiver integrated refrigerant condenser of the present invention will be described based on an embodiment in which it is applied to an automotive air conditioner.
[0014]
[Configuration of the first embodiment]
1 to 4 show a first embodiment of the present invention, and FIG. 1 shows a refrigeration cycle of an automobile air conditioner. The refrigeration cycle 1 of this automotive air conditioner comprises a refrigerant compressor 2, a receiver-integrated refrigerant condenser 3, a sight glass 4, an expansion valve 5, and a refrigerant evaporator 6 made of metal pipes or rubber pipes. The refrigerant pipes 7 are sequentially connected.
[0015]
The refrigerant compressor 2 is connected to an engine E installed in an automobile engine room (not shown) via a belt (not shown) and an electromagnetic clutch (not shown). When the rotational power of the engine E is transmitted to the refrigerant compressor 2, the refrigerant compressor 2 compresses the gas-phase refrigerant sucked in from the refrigerant evaporator 6, and converts the high-temperature and high-pressure gas-phase refrigerant into a receiver-integrated refrigerant condenser. 3 is discharged.
[0016]
The liquid receiver-integrated refrigerant condenser 3 is integrally provided with a condensing unit 8, a liquid receiving unit 9, and a supercooling unit 10. The condensing unit 8 is connected to the discharge side of the refrigerant compressor 2 and exchanges heat between the gas-phase refrigerant flowing into the inside from the refrigerant compressor 2 and outdoor air sent by a cooling fan (not shown) or the like. Works as a condenser to condense and liquefy.
[0017]
The liquid receiving unit 9 gas-liquid separates the gas-liquid two-phase refrigerant flowing into the interior from the condensing unit 8 into a gas phase refrigerant and a liquid phase refrigerant, and supplies only the liquid phase refrigerant to the subcooling unit 10. Work as a vessel. The supercooling unit 10 is provided adjacent to the lower part of the condensing unit 8, and exchanges heat between the liquid-phase refrigerant that has flowed into the interior of the liquid-receiving unit 9 with outdoor air that is sent by a cooling fan or the like. It works as a subcooler that subcools.
[0018]
The sight glass 4 is connected to the downstream side of the supercooling unit 10 of the receiver-integrated refrigerant condenser 3 and observes the state of the refrigerant circulating in the refrigeration cycle 1. The sight glass 4 is singly mounted in a place where the inspector can easily see in the engine room of the automobile, for example, in the middle of the refrigerant pipe 7 provided adjacent to the receiver-integrated refrigerant condenser 3.
[0019]
As shown in FIG. 1, the sight glass 4 has a tubular metal body 11 whose both ends are connected to the refrigerant pipe 7 by means such as welding or fastening, and a peep formed on the upper surface of the metal body 11. It is comprised from the welding glass 13 etc. which were inserted by the window 12. FIG. Generally, when bubbles are seen from the viewing window 12, the refrigerant is insufficient, and when no bubbles are seen, the amount of refrigerant is an appropriate amount.
[0020]
The expansion valve 5 is connected to the refrigerant inlet side of the refrigerant evaporator 6 and adiabatically expands the high-temperature and high-pressure liquid-phase refrigerant flowing from the sight glass 4 to form a low-temperature and low-pressure mist refrigerant. In this example, the refrigerant A temperature-actuated expansion valve is used that automatically adjusts the valve opening so as to maintain the refrigerant superheat degree at the refrigerant outlet of the evaporator 6 at a predetermined value.
[0021]
The refrigerant evaporator 6 is connected between the suction side of the refrigerant compressor 2 and the downstream side of the expansion valve 5, and the gas-liquid two-phase refrigerant flowing into the inside from the expansion valve 5 is blown by a blower (not shown). It functions as a heat exchanger that evaporates the refrigerant by exchanging heat with the outdoor air or the indoor air that is blown.
[0022]
Next, the receiver integrated refrigerant condenser 3 of this embodiment will be described in detail with reference to FIGS. The receiver-integrated refrigerant condenser 3 has, for example, a height of 300 mm to 400 mm and a width of 300 mm to 600 mm, and is attached to a place where it is easy to receive traveling wind in an engine room of an automobile via a mounting bracket (not shown). It is attached integrally. The liquid receiver-integrated refrigerant condenser 3 is disposed on the core 14 for heat exchange, the first header 15 disposed on one end side in the horizontal direction of the core 14, and the other end side in the horizontal direction of the core 14. The second header 16 and the like are manufactured, and are manufactured by integrally brazing in a furnace.
[0023]
The core 14 includes a condensing part 8 and a supercooling part 10, and side plates 17 and 18 for fixing mounting brackets for attaching the receiver-integrated refrigerant condenser 3 to an automobile at the upper end and lower end are brazed. It is joined by such means. The condensing unit 8 is composed of a plurality of condensing tubes 19 and corrugated fins 20, which are joined by means such as brazing. The supercooling unit 10 includes a plurality of supercooling tubes 21 and corrugated fins 22, which are joined by means such as brazing.
[0024]
The side plates 17 and 18 are shaped by pressing a metal plate clad with aluminum or an aluminum alloy with a brazing material, and are formed on the first header 15 and the second header 16 at both ends in the horizontal direction, respectively. Insert pieces 171, 172, 181, and 182 to be inserted are formed.
[0025]
A plurality of condensing tubes 19 and supercooling tubes 21 are oblong shapes having a flat cross-section by extruding a plate clad with brazing material of aluminum or aluminum alloy having excellent corrosion resistance and thermal conductivity. And has a plurality of refrigerant channels therein. The corrugated fins 20 and 22 are heat radiating fins for improving the heat radiating efficiency of the refrigerant, and are obtained by pressing a metal plate such as aluminum or aluminum alloy whose both side surfaces are clad with a brazing material into a corrugated shape.
[0026]
The plurality of condensing tubes 19 and the plurality of subcooling tubes 21 are arranged in the horizontal direction. The refrigerant flowing in the plurality of condensing tubes 19 flows from the first header 15 to the second header 16, and the refrigerant flowing in the plurality of subcooling tubes 21 conversely flows from the second header 16 to the first header 15. . In this embodiment, the number of condensing tubes 19 is larger than the number of supercooling tubes 21, and according to experimental experience, the number of supercooling tubes 21 is 15% of the entire core 14. About 20% is preferable.
[0027]
The first header 15 includes a header plate 23 having a substantially U-shaped cross section and a tank plate 24 having a semicircular cross section, and has a cylindrical shape extending in the vertical direction. The first header 15 has a predetermined shape obtained by pressing a metal plate clad on both sides with a brazing material made of aluminum or aluminum alloy having excellent corrosion resistance and thermal conductivity.
[0028]
The upper side of the first header 15 is connected to the upstream ends of a plurality of condensing tubes 19 constituting the condensing unit 8, and the lower side is the downstream end of a plurality of subcooling tubes 21 constituting the supercooling unit 10. Is connected. And the cap 25 is engage | inserted by the opening part of the up-down direction of the 1st header 15 (plate length direction).
[0029]
The cap 25 has a shape obtained by pressing a metal plate clad with aluminum or an aluminum alloy with a brazing material, and is joined to the upper and lower ends of the first header 15 by means such as brazing. It has an annular joining piece 251 and a substantially disc-shaped closing portion 252 that is recessed from the joining piece 251 and closes the opening at the upper and lower ends.
[0030]
The header plate 23 is formed with a number of oblong holes 26 by press working, and through holes 27 are formed in the upper and lower ends, respectively. The numerous holes 26 are joined by means such as brazing in a state in which the upstream ends of the plurality of condensing tubes 19 and the downstream ends of the plurality of subcooling tubes 21 are inserted. Further, the two through holes 27 are joined by means such as brazing in a state where the insertion pieces 171 and 181 of the side plates 17 and 18 are inserted.
[0031]
The tank plate 24 has a hole 29 for fixing the separator 28 that partitions the inside vertically by pressing, a circular refrigerant inlet 31 for fixing the inlet pipe 30 and a circular refrigerant outlet for fixing the outlet pipe 32. 33 is formed. The separator 28 is formed in a substantially disk shape, and the inside of the first header 15 communicates only with the inlet side communication chamber 34 that communicates only with the upstream end of the condensing unit 8 and the outlet side that communicates only with the downstream end of the supercooling unit 10. The communication room 35 is divided.
[0032]
The inlet pipe 30 has a circular pipe shape, and is a pipe for allowing the high-temperature and high-pressure gas-phase refrigerant discharged from the refrigerant compressor 2 to flow into the inlet-side communication chamber 34. The refrigerant inlet 31 by means of brazing or the like. It is joined to. The outlet pipe 32 has a circular pipe shape and is a pipe for sending the liquid-phase refrigerant in the outlet-side communication chamber 35 to the sight glass 4 and is joined to the refrigerant discharge port 33 by means such as brazing.
[0033]
As shown in FIG. 4, the second header 16 is composed of a header plate 36 having a substantially U-shaped cross section and a cylindrical body 37 having a substantially R-shaped cross section, and has a double cylindrical shape extending in the vertical direction. The liquid receiving part 9 is integrally formed with the tank part. The second header 16 has a predetermined shape made of aluminum or aluminum alloy each having excellent corrosion resistance and thermal conductivity. In this example, the header plate 36 and the illustrated left side portion of the cylindrical body 37 constitute a tank portion, and the cylindrical portion of the cylindrical body 37 constitutes the liquid receiving portion 9.
[0034]
The upper side of the second header 16 is connected to the downstream ends of a plurality of condensing tubes 19 constituting the condensing unit 8, and the lower side is the upstream end of a plurality of subcooling tubes 21 constituting the supercooling unit 10. Is connected. A cap 38 is fitted into the openings in the upper and lower ends of the second header 16 in the vertical direction (plate length direction).
[0035]
The cap 38 is joined to the upper and lower end portions of the second header 16 by means of brazing or the like, and has a substantially annular joining piece 381 that is recessed from the joining piece 381, and the upper and lower end portions of the second header 16. A substantially disc-shaped blocking portion 382 that closes the inner opening portion, and a flat oval blocking portion 383 that closes the outer opening portions of the upper and lower ends of the second header 16.
[0036]
The header plate 36 is formed by pressing a metal plate clad with brazing material on both sides, thereby forming a large number of oval-shaped holes 39 and through holes 40 at the upper and lower ends. The numerous holes 39 are joined by means such as brazing in a state where the downstream ends of the plurality of condensing tubes 19 and the upstream ends of the plurality of subcooling tubes 21 are inserted. Further, the two through holes 40 are joined by means such as brazing in a state where the insertion pieces 172 and 182 of the side plates 17 and 18 are inserted.
[0037]
The cylindrical body 37 is formed into a predetermined shape by extrusion processing, and has a first separator 41 that divides (divides) the inside of the second header 16 into a first chamber and a second chamber inside. ing. The first separator 41 is divided into a first chamber (upstream communication chamber 46) and a lower chamber (downstream communication chamber 47) by an additional process by press working (partition). The hole 43 for fixing the second separator 42, the circular refrigerant inlet 44 and the circular refrigerant outlet 45 communicating the first chamber and the second chamber are formed.
[0038]
The first separator 41 and the second separator 42 are formed outside the upstream communication chamber 46 that communicates only with the downstream end of the condensing unit 8 and the downstream communication chamber 47 that communicates only with the upstream end of the supercooling unit 10. It is a partition part which divides the inside of the 2nd header 16 into 3 in the gas-liquid separation chamber 48 which comprises the liquid part 9. FIG. Moreover, the 1st separator 41 comprises the 2nd partition part of this invention, and the 2nd separator 42 comprises the 1st partition part of this invention.
[0039]
The refrigerant inlet 44 opens at the lower part of the upstream communication chamber 46 (the lowermost part of the condensing unit 8), and is a communication port through which the refrigerant in the upstream communication chamber 46 flows into the gas-liquid separation chamber 48. The outlet 45 is a communication port that opens below the refrigerant inlet 44 and allows the refrigerant in the gas-liquid separation chamber 48 to flow into the downstream communication chamber 47. Further, the gas-liquid separation chamber 48 separates the refrigerant flowing into the inside from the upstream communication chamber 46 into a gas phase refrigerant and a liquid phase refrigerant, and sends out only the liquid phase refrigerant to the downstream communication chamber 47.
[0040]
[Operation of the first embodiment]
Next, the operation of the refrigeration cycle 1 of the automobile air conditioner of this embodiment will be briefly described with reference to FIGS. 1 and 2. When the operation of the automobile air conditioner is started, the electromagnetic clutch is energized, and the refrigerant compressor is rotationally driven by the engine E via the belt and the electromagnetic clutch.
[0041]
Therefore, the high-temperature and high-pressure gas-phase refrigerant compressed and discharged in the refrigerant compressor 2 flows into the inlet side communication chamber 34 of the first header 15 through the inlet pipe 30. The gas-phase refrigerant that has flowed into the inlet side communication chamber 34 is distributed to the plurality of condensing tubes 19 constituting the condensing unit 8 in the inlet side communication chamber 34.
[0042]
The gas-phase refrigerant distributed to the plurality of condensation tubes 19 is condensed and liquefied by exchanging heat with outdoor air via the corrugated fins 20 when passing through these condensation tubes 19. Almost all liquid refrigerant is left behind. Such a gas-liquid two-phase refrigerant flows into the upstream communication chamber 46 of the second header 16 from the plurality of condensing tubes 19. The gas-liquid two-phase refrigerant that has flowed into the upstream communication chamber 46 is once collected and then flows into the liquid receiving part 9 (gas-liquid separation chamber 48) through the refrigerant inlet 44.
[0043]
In the liquid receiving part 9 (gas-liquid separation chamber 48), the cross-sectional area is increased to some extent (for example, 500 mm). ² ), The speed of the refrigerant is reduced, and the buoyancy of the gas-phase gas-phase refrigerant is utilized. Further, by the second separator 42, from the downstream end of the lowermost condensing tube 19 among the plural condensing tubes 19 to the upstream end of the lowermost subcooling tube 21 among the plural subcooling tubes 21. The flow path length is long.
[0044]
In addition, the second separator 42 causes the refrigerant flowing into the second header 16 from the plurality of condensing tubes 19 to make a U-turn and flow out to the plurality of supercooling tubes 21. The refrigerant in the state is gas-liquid separated by centrifugal force, and the gas-phase gas-phase refrigerant is collected in one place (inside).
[0045]
That is, since the refrigerant inlet 44 opens at the lower part of the upstream communication chamber 46 and the refrigerant inlet 44 and the refrigerant outlet 45 are relatively close to each other, the gas-liquid two-phase refrigerant flows into the refrigerant flow. When passing through the inlet 44 → the liquid receiving part 9 → the refrigerant outlet 45, the liquid phase refrigerant having a large specific gravity is transferred to the outer side of the cylindrical body 37 due to the centrifugal force, and the gas phase refrigerant having a small specific gravity is transferred to the outside. The second separator 42 collects at the protruding portion into the liquid receiving part 9.
[0046]
Accordingly, since the gas-liquid two-phase refrigerant is efficiently gas-liquid separated in the liquid receiving unit 9, the gas phase refrigerant is accumulated in the upper part of the liquid receiving part 9, and the liquid phase refrigerant is accumulated in the lower part. Therefore, if the refrigerant is filled in the refrigeration cycle 1 with a sufficient gas-liquid interface in the liquid receiving unit 9, the refrigerant outlet 45 at the lower part of the liquid receiving unit 9 does not have a degree of supercooling. Only the liquid phase refrigerant flows into the downstream communication chamber 47. The liquid-phase refrigerant that has flowed into the downstream communication chamber 47 is distributed to the plurality of supercooling tubes 21 constituting the supercooling unit 10 in the downstream communication chamber 47.
[0047]
Then, the liquid-phase refrigerant distributed to the plurality of supercooling tubes 21 is supercooled by exchanging heat with outdoor air via the corrugated fins 22 when passing through these supercooling tubes 21. The liquid-phase refrigerant having the flow rate of the refrigerant flows into the outlet side communication chamber 35 of the first header 15.
[0048]
The liquid-phase refrigerant that has flowed into the outlet side communication chamber 35 flows into the expansion valve 5 through the outlet pipe 32 and the sight glass 4. In addition, since the single-phase liquid-phase refrigerant not including the gas-phase refrigerant is supplied into the expansion valve 5, the refrigerant circulation amount of the liquid-phase refrigerant flowing into the expansion valve 5 does not decrease. As a result, a sufficient amount of mist refrigerant is supplied into the refrigerant evaporator 6, so that the refrigeration capacity of the automobile air conditioner can be prevented from being lowered.
[0049]
[Effects of the first embodiment]
As described above, in the refrigeration cycle 1 of the automobile air conditioner, the refrigerant inlet 44 is opened at the lower part of the upstream communication chamber 46, that is, below the liquid receiving part 9. Even when the refrigerant circulation amount is large as in the case of high-speed operation, a gas-liquid interface can be formed in the liquid receiving unit 9 even if the cross-sectional area of the liquid receiving unit 9 is not increased abnormally.
[0050]
Further, the gas-liquid two-phase refrigerant flowing out from the downstream ends of the plurality of condensing tubes 19 is once collected in the upstream communication chamber 46 of the second header 16, and then opened at the lower portion of the upstream communication chamber 46. The liquid is fed into the liquid receiving unit 9 through the refrigerant inlet 44. As a result, fine bubble-like gas-phase refrigerants coming out from the downstream ends of the plurality of condensing tubes 19 are collected in the upstream communication chamber 46 to become bubble-like gas-phase refrigerants having a large diameter, which are greatly affected by buoyancy. It becomes like this.
[0051]
Then, due to the presence of the second separator 42 installed at the boundary between the downstream end of the condensing unit 8 and the upstream end of the supercooling unit 10, from the refrigerant inlet 44 through the liquid receiver 9 to the refrigerant outlet 45. The flow of the refrigerant is a U-turn flow (vector in the reverse direction). For this reason, the gas-liquid is separated by centrifugal force and the gas-phase gas-phase refrigerant is more concentrated, so that the gas-phase gas-phase refrigerant has a larger diameter and is more easily affected by the buoyancy to facilitate gas-liquid separation. Become. Therefore, gas-liquid separation is facilitated when it flows into the liquid receiving unit 9 from the refrigerant inlet 44, and the gas phase refrigerant stays in the liquid receiving unit 9 and the liquid phase refrigerant stays downward in the liquid receiving unit 9.
[0052]
Even if the lowermost condensing tube 19 among the plural condensing tubes 19 and the uppermost subcooling tube 21 among the plural subcooling tubes 21 are close to each other, the condensing unit 8 The flow path length from the downstream end of the plurality of condensing tubes 19 to the upstream end of the plurality of supercooling tubes 21 due to the presence of the second separator 42 installed at the boundary between the downstream end and the upstream end of the supercooling unit 10. Is getting longer. Thereby, the gaseous gaseous refrigerant which cannot be separated from the liquid receiving unit 9 to the plurality of supercooling tubes 21, the sight glass 4 and the expansion valve 5 is prevented from flowing out, and the supercooling unit 10 is effectively operated. And generation of flow noise at the expansion valve 5 can be prevented.
[0053]
And since the supercooling part 10 is provided in the downstream of the liquid receiving part 9, even if the gas-liquid separation in the liquid receiving part 9 is not perfect, a bubble-like gaseous-phase refrigerant | coolant is in the supercooling part 10. Since it disappears completely, the volume of the liquid receiving part 9, that is, the cross-sectional area of the liquid receiving part 9 can be reduced, and the effective heat radiation area of the condensing part 8 and the supercooling part 10 of the core 14 is prevented from being reduced. can do.
[0054]
In this embodiment, since the receiver-integrated refrigerant condenser 3 is connected between the refrigerant compressor 2 and the sight glass 4, the number of parts can be reduced, that is, the cost can be reduced. Can be improved. Moreover, since it can be stored compactly in the engine room of an automobile, space is saved.
[0055]
In this embodiment, since the sight glass 4 is connected to the downstream side of the supercooling unit 10, it is not necessary to ensure the gas-liquid separation in the liquid receiving unit 9, and the volume of the liquid receiving unit 9, That is, the cross-sectional area of the liquid receiving unit 9 may be estimated by the amount of refrigerant fluctuation due to load fluctuation of the refrigeration cycle 1 and the margin for refrigerant leakage.
[0056]
[Second Embodiment]
FIG. 5 shows a second embodiment of the present invention and is a view showing a receiver-integrated refrigerant condenser. In this embodiment, in the first header 15 and the second header 16, a room communicating with the plurality of condensing tubes 19 constituting the condensing unit 8 is divided into two by the second separators 51 and 52, and the intermediate communication chamber. 53 and the upstream communication chamber 54 are added, and the flow of the refrigerant in the condensing unit 8 is an S turn.
Note that the number of turns may be increased by increasing the number of separators in the manner of flowing the refrigerant in the condensing unit 8. However, the refrigerant inlet 31 into the condenser 8 and the refrigerant inlet 44 into the liquid receiver 9 need to be provided at opposite positions.
[0057]
[Configuration of Third Embodiment]
6 and 7 show a third embodiment of the present invention. FIG. 6 shows a receiver-integrated refrigerant condenser. FIG. 7 shows a liquid receiver of the receiver-integrated refrigerant condenser. It is the figure which showed the part. A dryer 61 for removing moisture in the refrigerant is incorporated in the upper part of the liquid receiving part 9 (gas-liquid separation chamber 48) of this embodiment. The dryer 61 is provided between the elliptical blocking portion 383 of the cap 38 and the filter 63 held by the elliptical holder (presser) 62. The dryer 61 uses a large number of Freon refrigerant desiccants (hereinafter abbreviated as desiccants) 611 such as silica alumina adsorbents such as synthetic zeolite, alumina gel, and silica gel.
[0058]
The holder 62 is made of a punching metal having a large number of small holes 64 formed therein. Note that the holder 62 does not have to be provided when a rigid material is used for the filter 63.
The filter 63 is made of, for example, ceramics or metal having excellent high temperature resistance, and collapses during use for a long period of time, or is worn and pulverized into the refrigeration cycle. It is intended to prevent leakage.
[0059]
Here, a method for assembling the dryer 61 will be briefly described. First, the holder 62 is press-fitted into the cylindrical body 37 of the second header 16 and stopped at a predetermined position. And after inserting the filter 63 from the upper side opening of the cylindrical body 37 of the 2nd header 16 until it contact | abuts to the holder 62, the dryer 61 which consists of many desiccants 611 is put. The dryer 61 is assembled by fitting the closing portion 383 of the cap 38 into the upper opening of the tubular body 37 of the second header 16 and integrally brazing.
[0060]
[Operation of the third embodiment]
Next, the operation of the receiver-integrated refrigerant condenser 3 of this embodiment will be briefly described with reference to FIGS. The gas-liquid two-phase refrigerant that has flowed into the upstream communication chamber 46 of the second header 16 from the plurality of condensing tubes 19 is once collected and then passed through the refrigerant inlet 44 (gas / liquid). It flows into the separation chamber 48). The gas-liquid two-phase refrigerant that has flowed into the liquid receiver 9 is efficiently gas-liquid separated as described in the first embodiment, and only the liquid-phase refrigerant flows from the refrigerant outlet 45 to the downstream communication chamber. 47 flows in. The liquid-phase refrigerant that has flowed into the downstream communication chamber 47 is distributed to the plurality of supercooling tubes 21 that constitute the supercooling unit 10 in the downstream communication chamber 47.
[0061]
In this embodiment, the dryer 61 is installed in a place where it does not receive the main flow of the refrigerant. The portion where the liquid-phase refrigerant is accumulated is located below the liquid-receiving unit 9, but the gas-liquid separation method causes the bubbles to rise from below the liquid-receiving unit 9 by buoyancy. Therefore, a part of the bubbles in the liquid receiving part 9 is condensed and liquefied by heat exchange with the outside (atmosphere) and flows below the liquid receiving part 9. For this reason, when the gas-liquid separated bubbles pass through the numerous small holes 64 of the holder 62 and the filter 63 and once enter the dryer 61 provided at the upper portion of the liquid receiving part 9, and then condense into liquid and flow downward, Moisture is removed.
[0062]
Therefore, although it is a part of the main stream of the refrigerant, moisture in the refrigerant can always be removed. Further, since the filter 63 is not disposed in the main flow of the refrigerant, there is no difference in the vertical pressure between the upstream and downstream of the filter 63 even when used for a long time, and the refrigeration cycle is not adversely affected. Furthermore, since the holder 62 of the filter 63 is not arranged in the main flow of the refrigerant, the holder 62 does not flow out together with the main flow of the refrigerant, and thus the outflow of the dryer 61 can be prevented. Therefore, the valve mechanism of the expansion valve 5 or the refrigerant compressor 2 can be caught to hinder its operation, or seizure of sliding parts such as pistons and bearings of the refrigerant compressor 2 can be prevented.
[0063]
[Fourth embodiment]
FIG. 8 shows a fourth embodiment of the present invention and is a view showing a liquid receiving portion of a liquid receiver-integrated refrigerant condenser. In the closing portion 383 of the cap 38 of this embodiment, a dryer insertion opening 65 for inserting the dryer 61 is opened. And the small diameter part (lower end part) of the obstruction | occlusion stopper 66 as a sealing material is fitted by the inner periphery of the obstruction | occlusion part 383. FIG.
[0064]
The method of assembling the dryer 61 of this embodiment is as follows. After the holder 62 is press-fitted into the cylindrical body 37 of the second header 16, the receiver-integrated refrigerant condenser 3 is integrally brazed in the furnace. The filter 63 and the dryer 61 are inserted into the liquid receiving portion 9 from the dryer insertion port 65 formed in the closing portion 383 of the cap 38. Then, after the dryer 61 is inserted, the dryer insertion port 65 is closed with a closing plug 66.
[0065]
The closing plug 66 may be joined to the cap 38 by using a welding method such as a torch brazing method or an argon gas welding method that does not transfer much heat to the dryer 61 or the filter 63.
In addition, since a certain distance is maintained between the joining position of the blocking plug 66 and the filter 63, a general resin material can be used as the material of the filter 63.
[0066]
[Fifth embodiment]
FIG. 9 shows a fifth embodiment of the present invention, and is a view showing a liquid receiving portion of a liquid receiver-integrated refrigerant condenser. In the closing portion 383 of the cap 38 of this embodiment, a dryer insertion opening 65 for inserting the dryer 61 is opened. And the small diameter part (lower end part) of the obstruction | occlusion stopper 67 as a sealing material is fitted by the inner periphery of the obstruction | occlusion part 383. As shown in FIG.
[0067]
Further, the closing portion 383 is formed thicker than the other embodiments, and an external thread portion (outer peripheral thread portion) 671 formed on the upper outer periphery of the small diameter portion of the closing plug 67 on the inner periphery on the upper side thereof. A female screw portion (inner peripheral screw portion) 651 is formed to be screwed with the screw. An O-ring 68 as a sealing material that prevents the dryer 61 from flowing out is mounted between the outer periphery of the closing plug 67 and the inner periphery of the closing portion 383 of the cap 38.
[0068]
Then, in the method of assembling the dryer 61 of this embodiment, the holder 62 is press-fitted into the tubular body 37 of the second header 16 and the receiver-integrated refrigerant condenser 3 is brazed integrally in the furnace, and then the cap The filter 63 and the dryer 61 are inserted into the liquid receiving portion 9 from the dryer insertion port 65 of the closing portion 383 of 38, and the closing plug 67 is screwed into the dryer insertion port 65. In the case of this embodiment, after the refrigeration cycle has been used for a long period of time, the obturator plug 67 is opened and the dryer 61 and the filter 63 can be replaced (replaced).
[0069]
[Sixth embodiment]
FIG. 10 shows a sixth embodiment of the present invention and is a view showing a liquid receiving portion of a liquid receiver-integrated refrigerant condenser. In the closing portion 383 of the cap 38 of this embodiment, a dryer insertion port 65 for inserting the dryer 61 is formed, and a projection piece 69 for closing the dryer insertion port 65 is integrally formed. In addition, the protrusion piece 69 is provided so that elastic deformation is possible.
[0070]
Also in this embodiment, after the receiver-integrated refrigerant condenser 3 is integrally brazed in the furnace and the filter 63 and the dryer 61 are inserted into the receiver 9 from the dryer insertion port 65, After the piece 69 is tilted so as to be positioned on the same plane as the closing portion 383, the dryer insertion port 65 is closed in order to prevent the dryer 61 from flowing out. In the same manner as in the fourth embodiment, the gap between the outer periphery of the protruding piece 69 and the inner periphery of the closing portion 383 is closed by brazing or welding.
[0071]
[Seventh embodiment]
FIG. 11 shows a seventh embodiment of the present invention, and is a view showing a liquid receiving portion of a liquid receiver-integrated refrigerant condenser. In the closing portion 383 of the cap 38 of this embodiment, a cylindrical portion 70 is formed which is composed of a conical portion whose inner diameter gradually decreases upward and a cylindrical portion. A dryer insertion opening 71 for inserting the dryer 61 is opened in the cylindrical portion 70. And in the cylinder part 70, the small diameter part (lower end part) of the obstruction | occlusion stopper 72 as a sealing material is fitted.
[0072]
A female screw portion (inner peripheral screw portion) 701 that is screwed into a male screw portion (outer peripheral screw portion) 721 formed on the outer periphery of the upper portion of the small diameter portion of the blocking plug 72 is provided on the inner periphery on the upper side of the cylindrical portion 70. Is formed. Between the outer periphery of the small diameter portion of the blocking plug 72 and the inner periphery of the cylindrical portion 70, an O-ring 73 is mounted as a seal material that prevents the dryer 61 from flowing out.
[0073]
In the case of this embodiment, even when the dryer 61 is inserted into the liquid receiving part (gas-liquid separation chamber 48) from the dryer insertion port 71 and then the dryer insertion port 71 is closed with the plug 72, The lower end portion of the small diameter portion does not reach the upper surfaces of the many desiccants 611 constituting the dryer 61, and the upper surfaces of the many desiccants 611 can be kept flat.
[0074]
Furthermore, since the space between the upper surface of a large number of desiccants 611 and the lower end portion of the small-diameter portion of the closing plug 72 is sealed with felt (water resistant heavy paper) 74 as a sealing material, the dryer 61 is configured. It is possible to prevent the generation of gaps between the many desiccants 611. Note that if there are gaps between a large number of desiccants 611, the desiccants 611 are worn by the vibration of the vehicle and the like, so that the desiccants 611 are worn and easily pulverized.
[0075]
[Modification]
In this embodiment, the present invention is applied to an automobile air conditioner. However, the present invention may be applied to any air conditioner in which the refrigerant circulation amount varies, such as a railway vehicle, a ship, and an aircraft. Further, the present invention may be applied to a heat pump refrigeration cycle that effectively uses the heat radiation of the receiver-integrated refrigerant condenser 3.
[0076]
In this embodiment, the second header 16 is composed of the header plate 36 and the cylindrical body 37, but the second header 16 may be integrally formed as a single part by extrusion molding. Similarly, the first header 15 may be integrally formed as a single part by extrusion molding.
Further, the second header 16 may be constituted by sticking a plurality of cylindrical bodies in the vertical direction, and the second header 16 is formed by a single cylindrical body and is provided separately in the cylindrical body. One separator 41 may be fitted.
In this embodiment, the liquid receiver 9 is integrally formed with the second header 16, but a liquid receiver provided as a separate part from the second header 16 may be connected to the outside of the second header 16.
[0077]
In the third to seventh embodiments, a large number of desiccants 611 constituting the dryer 61 are directly inserted into the liquid receiver 9. However, a large number of desiccants 611 are contained in a felt (waterproof heavy paper) bag. You may insert what put in in the liquid receiving part 9. FIG.
In the fourth to seventh embodiments, a general resin material is used as the material of the filter 63 and the brazing is inserted into the liquid receiving part 9 after integral brazing. However, the integral brazing is achieved by using a heat resistant material as the material of the filter 63. It may be inserted in the liquid receiving part 9 before.
[0078]
In the third to seventh embodiments, the dryer insertion ports 65 and 71 are formed in the upper end surface of the cylindrical body 37 of the second header 16, that is, the cap 38 on the upper end side. The dryer insertion port may be formed anywhere around the liquid receiving portion 9 such as the lower end surface (cap 38 on the lower end side) or the side surface of the cylindrical body 37.
[0079]
【The invention's effect】
Even if the lowermost part of the condensing part and the uppermost part of the supercooling part are close to each other, the present invention provides a flow path length from the downstream end of the condensing part to the upstream end of the supercooling part by the first partition part of the tank part. Therefore, the gas-liquid separation property of the refrigerant in the gas-liquid separation chamber of the liquid receiving unit can be improved. In addition, since it is difficult for the gas-phase refrigerant to flow out to the supercooling section downstream from the gas-liquid separation chamber of the liquid receiving section, the supercooling section can be effectively operated, and further, generation of operating noise in the expansion valve can be prevented. .
[Brief description of the drawings]
FIG. 1 is a configuration diagram showing a refrigeration cycle of an automotive air conditioner used in a first embodiment of the present invention.
FIG. 2 is a cross-sectional view showing a receiver-integrated refrigerant condenser used in the first embodiment of the present invention.
3 is an exploded view of the receiver-integrated refrigerant condenser of FIG. 2. FIG.
4 is a cross-sectional view showing a second header in which a tank part and a liquid receiving part of the liquid receiver integrated refrigerant condenser of FIG. 2 are integrally formed. FIG.
FIG. 5 is a cross-sectional view showing a receiver-integrated refrigerant condenser used in a second embodiment of the present invention.
FIG. 6 is a cross-sectional view showing a receiver-integrated refrigerant condenser used in a third embodiment of the present invention.
7 is a cross-sectional view showing a liquid receiving portion of the liquid receiver-integrated refrigerant condenser of FIG. 6. FIG.
FIG. 8 is a cross-sectional view showing a liquid receiving portion of a liquid receiver integrated refrigerant condenser used in a fourth embodiment of the present invention.
FIG. 9 is a cross-sectional view showing a liquid receiving part of a liquid receiver integrated refrigerant condenser used in a fifth embodiment of the present invention.
FIG. 10 is a sectional view showing a liquid receiving part of a liquid receiver integrated refrigerant condenser used in a sixth embodiment of the present invention.
FIG. 11 is a cross-sectional view showing a liquid receiving portion of a liquid receiver integrated refrigerant condenser used in a seventh embodiment of the present invention.
[Explanation of symbols]
1 Refrigeration cycle
3. Receiver integrated refrigerant condenser
4 Sight Glass
8 Condensing section
9 Liquid receiver
10 Supercooling section
14 core
15 First header
16 Second header
19 Condensation tube
21 Tube for supercooling
25 cap
38 cap
41 First separator (second partition)
42 Second separator (first partition)
44 Refrigerant inlet
45 Refrigerant outlet
46 Upstream communication room
47 Downstream communication room
48 Gas-liquid separation chamber
61 Dryer
62 Holder (presser)
63 Filter

Claims

(A) a core provided with a condensing part for condensing the refrigerant flowing inside, and a supercooling part for supercooling the refrigerant condensed in the condensing part, up and down;
(B) It is extended in the up-down direction at one end of the core, the downstream end of the condensing unit is connected to the upper side, the upstream end of the supercooling unit is connected to the lower side, and the inside is connected to the condensing unit A tank section having a first partition section that is divided into an upstream communication chamber that communicates only with the downstream end of the subcooling section and a downstream communication chamber that communicates only with the upstream end of the supercooling section;
(C) A receiver having a gas-liquid separation chamber for gas-liquid separation of the refrigerant flowing therein, and a second partition for partitioning the gas-liquid separation chamber from the upstream communication chamber and the downstream communication chamber. A receiver-integrated refrigerant condenser comprising a liquid part,
(D) The second partition portion is
A refrigerant inlet that opens at a lower portion of the upstream communication chamber and opens at a lower side of the liquid receiving portion, and allows the refrigerant to flow into the gas-liquid separation chamber from the upstream communication chamber, and below the refrigerant inlet in open and open at the bottom of the liquid receiving part, have a coolant outlet port for flowing out the refrigerant from the gas-liquid separation chamber to said downstream side communicating chamber,
The liquid receiver is characterized in that the upstream communication chamber and the downstream communication chamber communicate with each other only through the refrigerant flow path from the refrigerant inlet to the refrigerant outlet through the gas-liquid separation chamber. Body refrigerant condenser.

The receiver-integrated refrigerant condenser according to claim 1,
A liquid receiver-integrated refrigerant condenser, wherein the liquid receiver is integrally formed with the tank.

The receiver-integrated refrigerant condenser according to claim 1,
A liquid receiver-integrated refrigerant condenser, wherein the liquid receiver provided as a separate part from the tank is connected to the outside of the tank.

The receiver-integrated refrigerant condenser according to any one of claims 1 to 3,
A liquid receiver-integrated refrigerant condenser, wherein a sight glass for observing the state of the refrigerant is connected downstream of the supercooling section.

The receiver-integrated refrigerant condenser according to any one of claims 1 to 4,
A receiver-integrated refrigerant condenser, wherein a dryer for removing moisture in the refrigerant is provided in an upper part of the gas-liquid separation chamber.

In the receiver integrated refrigerant condenser in any one of Claims 1-5,
The receiver-integrated refrigerant condenser, wherein the refrigerant flow from the refrigerant inlet to the refrigerant outlet through the gas-liquid separation chamber is a U-turn flow.

A core (14) that performs heat exchange, a first header (15) that is disposed on one end side in the horizontal direction of the core (14), and a second that is disposed on the other end side in the horizontal direction of the core (14). A header (16), and a liquid receiving part (9) is formed integrally with the second header (16), or a liquid receiving part provided as a separate part on the outside of the second header (16). The core (14) is composed of a condensing part (8) and a supercooling part (10), and the liquid receiving part has a gas-liquid separation chamber therein and is manufactured by integrally brazing in a furnace. A liquid condenser-integrated refrigerant condenser (3),
The second header (16) has a cylindrical shape extending in the vertical direction, and includes a header plate (36) constituting a tank portion. The tank portion communicates only with the downstream end of the condensing portion. And a downstream communication chamber that communicates only with the upstream end of the supercooling section, and is partitioned by the first partition (42),
The second header (16) and the liquid receiver (9) are partitioned by a second partition (41),
In the second partition (41),
A refrigerant inlet (44) that opens at a lower portion of the upstream communication chamber and opens at a lower side of the liquid receiving portion and allows the refrigerant to flow into the gas-liquid separation chamber from the upstream communication chamber, and the refrigerant flow A refrigerant outlet (45) that opens below the inlet and opens at a lower portion of the liquid receiver, and allows the refrigerant to flow out of the gas-liquid separation chamber into the downstream communication chamber;
The refrigerant flow from the refrigerant inlet (44) through the gas-liquid separation chamber (48) to the refrigerant outlet (45) is a U-turn flow ,
The liquid receiver is characterized in that the upstream communication chamber and the downstream communication chamber communicate with each other only through the refrigerant flow path from the refrigerant inlet to the refrigerant outlet through the gas-liquid separation chamber. Body refrigerant condenser.