JP4134465B2

JP4134465B2 - Branch pipe and heat exchanger

Info

Publication number: JP4134465B2
Application number: JP32600299A
Authority: JP
Inventors: 泰城村上; 悟古藤; 邦彦加賀; 雅弘中山; 晃石橋
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 1999-11-16
Filing date: 1999-11-16
Publication date: 2008-08-20
Anticipated expiration: 2019-11-16
Also published as: JP2001141333A

Description

【０００１】
【発明の属する技術分野】
本発明は、蒸気圧縮式冷凍サイクルの冷媒分流などに使用される分岐管および熱交換器に関するものである。
【０００２】
【従来の技術】
近年、冷凍空調機の熱交換器の多パス化に伴い、分岐管が数多く用いられており、分岐性能の向上が重要視されている。以下に、図面を参照しながら従来の分岐管について説明する。
【０００３】
図１９は、従来の分岐管の熱交換器への取り付け状態を示す斜視図、図２０は従来の分岐管の形状を示す斜視図、図２１は熱交換器を冷凍サイクルに接続して運転した際の従来の分岐管内部における冷媒の流動状態を示す断面図である。図において、１は分岐管、２はＵ字管、３は熱交換器の本体、４は熱交換器を構成し内部を冷媒が流れる伝熱管、特に４ａは分岐管１への入口配管、４ｂおよび４ｃは分岐管１からの出口配管、６は分岐管１を通過する冷媒の流れ方向を示し、１０は重力方向を示す。ここで、Ｕ字管２と伝熱管４および分岐管１と伝熱管４ａ、４ｂ、４ｃはロウ付けによって溶接される。また、１ａは分岐管入口部、１ｂ、１ｃは分岐管出口部、８ａ、８ｂ、８ｃは冷媒の液相部、７ａ、７ｂ、７ｃは冷媒の気相部、９ａ、９ｂ、９ｃは冷媒の液相部と気相部を合わせた冷媒全体を示す。
【０００４】
以上のように構成された分岐管１について、図２１を用いてその動作を説明する。冷媒９ａは、冷媒の気相部７ａが伝熱管の中央部、冷媒の液相部８ａが伝熱管の内壁面周囲に膜状に流れる環状流に近い状態で気液分離して、分岐管入口部１ａから流入し、分岐管出口部１ｂと１ｃに分流されて流出する。
【０００５】
また、異なる従来の分岐管として特開平１−２５４２３９号公報に開示されたものがある。図２２は、従来の別の分岐管を示す外観図であり、図２３は、熱交換器を冷凍サイクルに接して運転した際の分岐管内部における冷媒の流動状態を示す断面図である。図において、１は分岐管、１ａは分岐管入口部、１ｂ、１ｃは分岐管出口部、１６はらせん板を示す。らせん板１６は分岐管入口部１ａの内側に挿入されている。
【０００６】
以上のように構成された分岐管１について、以下図２３を用いてその動作を説明する。冷媒の液相部８ａと冷媒の気相部７ａが分岐管入口部１ａから流入する。このとき、冷媒の液相部８ａと冷媒の気相部７ａは、環状流に近い状態で気液分離しているが、分岐管入口部１ａを流れる時にらせん板１６によって気液が乱流混合し、その後、分岐管出口部１ｂと１ｃに分流されて流出する。
【０００７】
【発明が解決しようとする課題】
しかしながら、図２０、２１で説明した従来の分岐管では、分岐時に冷媒の気相部７ａよりも重い冷媒の液相部８ａが、重力１０の影響をうけるとともに、分岐部の壁面へ付着するため、分岐管出口部１ｃへ多く流れ過ぎてしまい、冷媒９ａを分岐管出口部１ｂと１ｃへ均一に分流できず、熱交換器の冷却性能が低下するという問題があった。また、所望の分流比に分割することが不可能であった。
【０００８】
また、特開平１−２５４２３９号公報に記載された分岐管では、らせん板１６により冷媒８ａと冷媒の気相部７ａを気液混合するが、冷媒の気相部７ａよりも重い冷媒の液相部８ａが重力１０の影響をうけるとともに、混合された冷媒全体９ａが分岐部で壁面に衝突して付着するため、冷媒９ａが分岐管出口部１ｃへ多く流れ、均一に分流できなかった。
【０００９】
本発明は、上記問題点を解決するためになされたものであり、重力の影響をうけず、冷媒の均一分配、さらには所望の冷媒の分配比を実現できる分岐管を得ることを目的とする。
【００１０】
【課題を解決するため手段】
この発明に係る分岐管は、分岐管本体に流体が流入する入口部と、この入口部から流入した流体を複数の流路へ分岐させる分岐部と、この分岐部を介して流れる流体を流出させる複数の出口部と、入口部から分岐部に至る管内に設けられた隔壁とを備えた分岐管において、隔壁は、入口部側の端部が分岐管本体の取り付け状態における重力方向に沿うと共に、入口部側の端部での分岐管の中心軸方向に垂直な断面全体が、管断面の中心を通って管断面を二分する直線に重なるように形成され、入口部側の端部において分流された冷媒が分岐管内で実質的に合流することなく複数の出口部から流出する構造である。また、隔壁は、入口部側の端部が分岐管本体の取り付け状態における重力方向に沿うと共に管中心で切り分けられ、入口部側の端部での分岐管の中心軸方向に垂直な断面全体が、管断面の中心を通って管断面を二分する直線に平行な２本の直線に重なるように形成され、入口部側の端部において分流された冷媒が分岐管内で実質的に合流することなく複数の出口部から流出する構造であり、入口部側の端部の開き角と入口部に接続される伝熱管の内壁に形成されたらせん溝の傾き角とを等しくするものである。
【００１１】
また、隔壁をフィンにより形成するものである。さらに、隔壁を入口部から分岐部へ近づくにつれて捻り、分岐部においては、複数の流路の分岐方向に対して垂直となるように配置するものである。
【００１２】
また、隔壁は、入口部から分岐部に至る直線部分に設けられているものである。
【００１３】
また、隔壁の入口部側の端部を、くさび形状とするものである。
【００１４】
また、上記分岐管を具備する熱交換器である。
【００１５】
【発明の実施の形態】
実施の形態１．
以下、本発明の実施の形態について図面を参照しながら説明する。図１は、本発明の実施の形態１における分岐管を示す斜視図である。図において、１ａは直管からなる分岐管入口部、１ｂ、１ｃは曲がり管からなる分岐管出口部、１ｄは分岐管入口部１ａに垂直な直管の分岐管接続部で分岐管の分岐部を構成している。５は隔壁、１１は分岐管入口部１ａの中心軸を示す。分岐管１はＴ字管として分岐管入口部１ａと分岐管接続部１ｄを形成し、分岐管入口部１ａと分岐管接続部１ｄからなるＴ字管の略中央ではない残りの端部に分岐管出口部１ｂ、１ｃをロウ付けにより溶接した形状である。ここで分岐管入口部１ａ、分岐管出口部１ｂ、１ｃはそれぞれ、上記従来例で示した図１９における入口配管４ａ、出口配管４ｂ、４ｃと接続する。また、隔壁５は分岐管入口部１ａおよび分岐管接続部１ｄの配管内壁にロウ付けにより溶接される。なお、この分岐管は、上記従来例における図１９に示したような熱交換器に用いられる。
【００１６】
ここで、分岐管１の取り付け姿勢について説明をわかりやすくするため図２を用いて座標軸を決定する。図２において、１２はＸ軸、１３はＹ軸、１４はＺ軸、１５は原点を示す。原点１５は分岐出口部１ｂ、１ｃ端部の管断面の中心を結ぶ線分の中点とする。Ｘ軸は分岐管入口部１ａの中心軸１１に平行かつ原点１５を通る直線、Ｙ軸１３は原点１５と分岐管入口部１ａ端部の管断面の中心を結ぶ直線、Ｚ軸１４は分岐管出口部１ｂ、１ｃ端部の管断面の中心を結ぶ直線とする。また、Ｘ軸方向を分岐管入口部１ａの冷媒流入方向にとり、Ｙ軸方向、Ｚ軸方向を右手系となるように決定する。上記図１はＺ軸を鉛直とした場合の分岐管１の取り付け姿勢を一例として示したものである。
【００１７】
次に、図３を用いて隔壁５の取り付けの様子を説明する。図３は、上記図１の分岐管１を−Ｙ軸方向からみた断面図である。図において、隔壁５は、分岐管入口部１ａ付近においては、分岐管１の取り付け状態における重力方向１０に沿って管中心を通るように配置され、分岐部へ近づくにつれて９０度捻られ、分岐部付近においては、分岐接続部１ｄの分岐方向に対して垂直となるようににロウづけされている。
【００１８】
以上のように構成された分岐管１について、以下にその動作を説明する。まず分岐管１に流入する冷媒の様子について、図４、図５を用いて説明する。図４、図５は、上記従来例における図１９に示した入口配管４ａを−Ｘ軸方向からみた断面図である。図４において、７ａは冷媒の気相部、８ａは冷媒の液相部、９ａは冷媒の気相部７ａと冷媒の液相部８ａを合わせた冷媒全体、２０は管中心を通る鉛直軸を示す。
【００１９】
入口配管４ａにおける冷媒９ａの配管断面分布の多くは、図４に示すように、冷媒の気相部７ａが入口配管４ａの中央部を流れ、冷媒の液相部８ａが入口配管４ａの内面にそって環状となるような分布、もしくは図５に示すように、比重の大きな冷媒の液相部８ａが重力の影響を受けて入口配管４ａの下側に多く流れ、比重の小さな冷媒の気相部７ａが入口配管４ａの上側に多く流れるような分布となる。図４、図５の分布からも明らかなように、入口配管４ａの断面内における冷媒の気相部７ａおよび冷媒の液相部８ａの分布は、鉛直軸２０に対してほぼ軸対称となる。
【００２０】
次に、分岐管入口部１ａに流入した直後の冷媒９ａの様子を、図６、図７を用いて説明する。図６、図７は分岐管入口部１ａの端部を−Ｘ軸方向からみた断面図である。図６、図７において、７ｂ、７ｃは冷媒の気相部、８ｂ、８ｃは冷媒の液相部、９ｂ、９ｃは冷媒の気相部７ｂ、７ｃと冷媒の液相部８ｂ、８ｃのそれぞれを合わせた冷媒全体を示す。分岐管入口部１ａに流入した冷媒９ａは隔壁５により、冷媒９ｂと冷媒９ｃに分流される。ここで、分岐管入口部１ａ付近において隔壁５は、分岐管１の取り付け状態における重力方向１０と同等である鉛直軸２０と重なるように配置されているため、隔壁５により分流された後の冷媒の気相部７ｂと８ｂ、冷媒の液相部７ｃと８ｃの流量はおおむね等しくなり、冷媒の気相部７ｂ、７ｃと冷媒の液相部８ｂ、８ｃのそれぞれの和である冷媒全体９ｂと９ｃの流量もおおむね等しくなる。
【００２１】
さらに、分岐管入口部１ａを通過して分岐管出口１ｂ、１ｃへ進む冷媒の流れを図８を用いて説明する。図８は、分岐管１を−Ｙ軸方向からみた断面図である。図８において、斜線の領域は配管内を流れる冷媒９ｃを示し、点部は配管内を流れる冷媒９ｂを示す。ここで、隔壁５が分岐管入口部１ａおよび分岐管接続部１ｄの配管内壁にロウづけされているため、分岐管入口部１ａの入口で隔壁５により分流された冷媒９ｂ、９ｃは、隔壁５の捻れに沿って合流することなくそれぞれ分岐管出口部１ｂおよび１ｃより流出する。
【００２２】
以上のように、本実施の形態によれば、伝熱管４の直管部において鉛直軸２０に対してほぼ軸対称な分布となる冷媒９ａを効果的に均一に分流することが可能となる。また、分岐管１は伝熱管４の直管部終端に取り付けられるとともに、直管部である分岐管入口部１ａにおいて冷媒を分岐するため、曲がり管を通過した後に冷媒を分流する従来の分岐管よりも安定した状態で冷媒を分流することができ、より均一分流性能を向上できるという効果を奏する。さらに、分岐管入口部１ａの直管部で隔壁５をねじるような構造をとるため、曲がり管内で隔壁５を溶接するよりも、隔壁５の加工および溶接が容易となり、製造コストを低減することができる。
【００２３】
なお、上記実施の形態１では、分岐管１のＺ軸１４は鉛直方向上向きに正であり、分岐管１は直管の分岐管入口部１ａと直管の分岐管接続部１ｄをＴ字管により形成し、曲がり管の分岐管出口部１ｂと１ｃを、分岐管入口部１ａと分岐管接続部１ｄからなるＴ字管の略中央でない残りの端部に溶接し、隔壁５は分岐管１の入口で鉛直軸２０と重なるように取り付けた構造を例に挙げた。しかしながら、分岐管１の取り付け姿勢や、分岐管１の構造および加工方法、隔壁の構造および加工方法、取り付け方法、取り付け姿勢は任意であり、少なくとも隔壁５が、入口配管４ａと接続する分岐管入口部１ａにあり、分岐管１の取り付け状態における重力方向１０に沿って設けられ、分流された冷媒９ｂと９ｃが分岐管１内で合流することなく分岐管出口部１ｂと１ｃから流出するような構造であればよい。
【００２４】
以下に図を用いて変形例を列挙する。まず、分岐管１の姿勢と構造についての変形例を示す。図９（ａ）は、Ｙ軸を鉛直下向き方向とした場合の分岐管の斜視図である。この場合、隔壁５のねじれはなくてもよい。図９（ｂ）は、分岐管接続部１ｄ、分岐管出口部１ｂ、１ｃを配管の曲げ加工により形成し、それに分岐管入口部１ａを溶接した場合の分岐管の斜視図である。図９（ｃ）は分岐管入口部１ａに分岐管出口部１ｂ、１ｃを溶接した場合の分岐管の斜視図である。
【００２５】
次に、隔壁５の構造についての変形例を示す。図１０（ａ）は、隔壁５が分岐管入口部１ａ端部よりも長い場合である。図１０（ｂ）は、隔壁５が分岐管入口部１ａ端部よりも短い場合である。図１１（ａ）は隔壁５の端部をＹＺ平面に対して傾けた場合、図１１（ｂ）は隔壁５端部をくさび形状とした場合、図１１（ｃ）は隔壁５をくの字に曲げて取り付けた場合である。ここで、図１１（ｂ）のように隔壁５の先端をくさび形状とした場合、分流時の隔壁の厚みをより薄くすることができるとともに、隔壁５の圧損がより小さくなるため、より冷媒を均一に分流することができる。図１１（ｃ）では所望の分配比を得ることも可能である。
【００２６】
さらに、図１２（ａ）は隔壁５の端部を上側と下側で切り分けた場合であり、図１２（ｂ）は−Ｘ軸方向から見た隔壁５の様子、図１２（ｃ）はＺ軸から見た隔壁５の様子を示す図である。図１２（ｄ）は内壁にらせん溝を持つ伝熱管４ａを示す図である。図１２（ｅ）は内壁にらせん溝を持つ伝熱管４ａに図１２（ａ）に示す分岐管１を取り付け、中心軸１１から伝熱管４ａおよび分岐管入口部１ａの壁内側を見た図である。
【００２７】
図において、１６はらせん溝、１７はらせん溝１６間を通過する冷媒液相部の流れ方向、１８は隔壁５の中心軸１１に対する開き角、１９はらせん溝の中心軸１１に対する傾き角であり、ここで、らせん溝１６の傾き角１９と隔壁５の開き角１８の大きさは等しい。図１２（ｅ）を用いて冷媒の流れを説明する。伝熱管４ａの内側にらせん溝１６がある場合、らせん溝１６の間を流れる冷媒の液相部の流れ方向１７は、らせん溝の傾き角１９と等しくなる。また、隔壁５の開き角１８は、らせん溝の傾き角１９と等しいため、らせん溝内を流れる冷媒の液相部の流れ方向１７と隔壁５は平行となる。よって、冷媒が隔壁５から受ける抵抗は小さくなり、冷媒側の圧力損失の上昇を高めることなく分流できるという効果を奏する。
【００２８】
また図１３は、従来例として説明した上記図１９の分岐管に、本発明における隔壁５を取り付けた場合である。図１３の分岐管１では、曲がり部に隔壁５を取り付けるため、隔壁の製造および取り付け加工が困難となるが、その反面、従来の分岐管１を流用できるため、分岐管１を製造するための金型代を節約できるとともに従来の製造技術を活用でき、製造コストを低減できるという効果を奏する。
【００２９】
実施の形態２．
以下、本発明の実施の形態２について図面を参照しながら説明する。図１４（ａ）は、本発明の実施の形態２における分岐管１を示す斜視図である。分岐管１の説明は実施の形態１と共通するために省略する。また、図１４（ｂ）は分岐管入口部１ａの端部を−Ｘ軸方向からみた断面図である。ここで、隔壁５は一枚の板を溶接して構成するのではなく、フィンを分岐管入口部１ａの内部に加工することで構成する。図１４（ｂ）において、上下の隔壁５は、分岐管入口部１ａの端部において、分岐管本体の取り付け状態における重力方向に沿って配置され、図１４（ａ）のように、分岐管入口部１ａ内で冷媒の流れ方向６に進みながら９０度ねじれ、分岐管接続部１ｄ内側で、分岐管接続部１ｄの分岐方向に対して垂直な状態となる。
【００３０】
以上のように構成された分岐管１について、以下にその動作を説明する。伝熱管４内を流れる冷媒は、上記実施の形態１の図４で示したように冷媒の気相部７ａが伝熱管４ａの中央部を流れ、冷媒の液相部８ａが伝熱管４ａの内壁面周囲にそって環状となるような分布か、もしくは図５に示すように、比重の大きな冷媒の液相部８ａが重力の影響を受けて伝熱管４ａの下側に多く流れ、比重の小さな冷媒の気相部７ａが伝熱管４ａの上側に多く流れるような分布となる。
【００３１】
次に、分岐管入口部１ａを通過した直後の冷媒の様子を図１５および図１６を用いて説明する。図１５および図１６に示すように、分岐管入口部１ａに流入した冷媒の液相部８ａは隔壁５により、冷媒８ｂと冷媒８ｃに分流される。一方、冷媒の気相部７ａは隔壁５により完全に分岐されない。その後、冷媒の液相部８ｂおよび８ｃは分岐管入口部１ａを進むが、図１５および図１６のように冷媒の気相部７ａが配管中央を通過する分布となるため、冷媒の液相部８ｂと８ｃはわずかに合流するのみで分岐管接続部１ｄに到達し、その後、各々が分岐管出口１ｂおよび１ｃより流出する。これにより冷媒の液相部９ｂと９ｃの流量がほぼ等しくなる。一方、冷媒の気相部７ａは重力の影響を強く受けないとともに、冷媒の液相部９ｂと９ｃがほぼ均一に分流されて、冷媒の気相部が流れる分岐管出口１ｂ、１ｃの流路断面積がほぼ等しくなるため、冷媒の気相部もほぼ均一に分流される。
【００３２】
以上のように、本実施の形態２によれば、上記実施の形態１と同様に、伝熱管４の直管部において鉛直軸２０に対してほぼ軸対称な分布となる冷媒９ａを効果的に均一に分流することが可能となる。また、分岐管１は伝熱管４の直管部終端に取り付けられるとともに、直管部である分岐管入口部１ａにおいて冷媒を分岐するため、曲がり管を通過した後に冷媒を分流する従来の分岐管よりも安定した状態で冷媒を分配、より等分配を実現できるという効果を奏する。さらに、分岐管入口部１ａの直管部で隔壁５をねじるような構造をとるため、曲がり管内で隔壁５を溶接するよりも、明らかに隔壁５の加工および溶接が容易となる。さらに、隔壁５をフィンとして加工することにより、隔壁５の製造方法の自由度が増すとともに、製造コストの低減も期待できるという効果を奏する。
【００３３】
なお、本実施の形態では、分岐管１のＺ軸１４は鉛直方向上向きに正であり、分岐管１は直管の分岐管入口部１ａと直管の分岐管接続部１ｄをＴ字管により形成し、曲がり管の分岐管出口部１ｂと１ｃを略中央でない残りの端部に溶接し、分岐管入口部１ａの壁面にフィンを加工することで隔壁５を構成する構造を例に挙げたが、分岐管１の取り付け姿勢や、分岐管１の構造および加工方法、隔壁の構造および加工方法、取り付け方法、取り付け姿勢は任意である。
【００３４】
以下に図を用いて隔壁５の変形例を列挙する。図１７、図１８（ａ）、図１８（ｂ）は−Ｘ軸方向から隔壁５を見た断面図である。図１７は、ほぼ直管内径に等しい高さのフィンを隔壁５とした場合、図１８（ａ）は鈍い先端形状の隔壁５とした場合、図１８（ｂ）は背の低いフィンを隔壁５とした場合である。図１７の分岐管１では、冷媒の液相部８ｂ、８ｃが分岐管入口部１ａ内の底部に多く分布するような場合、図１８（ａ）、（ｂ）の分岐管１では、冷媒の液相部８ｂ、８ｃが分岐管入口部１ａの内壁面周囲に沿って薄い膜状に分布するような場合に、上記各実施の形態で示した内容と同様の効果を奏することは言及するまでもない。ここで、図１７の分岐管１では、隔壁５がひとつで済むため、部品点数を削減できるという効果を奏する。一方、図１８（ａ）の分岐管１では、管外からプレス加工を施すことにより分岐管入口部１ａ内に隔壁５を製造することができる。さらに、図１８（ｂ）の分岐管１では、銅板に隔壁５をプレス加工した後に管状とする電縫管方式を用いて、分岐管入口部１ａ内に隔壁５を製造することができるため、隔壁５の加工が容易となり、より製造コストを低減できるという効果を奏する。
【００３５】
【発明の効果】
以上のように、請求項１記載の発明によれば、入口部側の端部が分岐管本体の取り付け状態における重力方向に沿うと共に、入口部側の端部での分岐管の中心軸方向に垂直な断面全体が、管断面の中心を通って管断面を二分する直線に重なるように形成され、入口部側の端部において分流された冷媒が分岐管内で実質的に合流することなく複数の出口部から流出する構造の隔壁を入口部から分岐部に至る管内に備えたので、冷媒を均一に分流できる効果が得られる。また、請求項２記載の発明によれば、隔壁の入口部側の端部を管中心で切り分け、端部の開き角と入口部に接続される伝熱管の内壁に形成されたらせん溝の傾き角とを等しくしたので、冷媒側の圧力損失上昇を高めることなく分流できる効果が得られる。
【００３６】
また、請求項３記載の発明によれば、隔壁をフィンにより形成するので、製造コストを低減できる効果が得られる。さらに、請求項４記載の発明によれば、隔壁を入口部から分岐部へ近づくにつれて捻り、分岐部においては、複数の流路の分岐方向に対して垂直となるように配置するので、冷媒を均一に分流できる効果が得られる。
【００３７】
また、請求項５記載の発明によれば、隔壁は、入口部から分岐部に至る直線部分にのみ設けられているので、製造コストを低減できる効果が得られる。
【００３８】
また、請求項６記載の発明によれば、隔壁の入口部側の先端部を、くさび形状とするので、冷媒側の圧力損失上昇を高めることなく冷媒を均一に分流できる効果が得られる。
【００３９】
また、請求項７記載の発明によれば、上記各効果が得られる。
【図面の簡単な説明】
【図１】この発明の実施の形態１による分岐管を示す斜視図である。
【図２】この発明の実施の形態１による分岐管の座標軸を示す図である。
【図３】この発明の実施の形態１による分岐管を示す断面図である。
【図４】この発明の実施の形態１による分岐管を接続する伝熱管内を流れる冷媒の配管断面分布を示す図である。
【図５】この発明の実施の形態１による分岐管を接続する伝熱管内を流れる冷媒の別の配管断面分布を示す図である。
【図６】この発明の実施の形態１による分岐管の分岐管入口部における冷媒の配管断面分布を示す図である。
【図７】この発明の実施の形態１によるおける分岐管の分岐管入口部における冷媒の別の配管断面分布を示す図である。
【図８】この発明の実施の形態１による分岐管内の冷媒分布を示す図である。
【図９】この発明の実施の形態１による別の分岐管を示す斜視図である。
【図１０】この発明の実施の形態１による別の分岐管を示す斜視図である。
【図１１】この発明の実施の形態１による別の分岐管を示す斜視図である。
【図１２】この発明の実施の形態１による別の分岐管を示す斜視図及び断面図である。
【図１３】この発明の実施の形態１による別の分岐管を示す斜視図である。
【図１４】この発明の実施の形態２による分岐管を示す斜視図及び断面図である。
【図１５】この発明の実施の形態２による分岐管の分岐管入口部における冷媒の別の配管断面分布を示す図である。
【図１６】この発明の実施の形態２による分岐管の分岐管入口部における冷媒の別の配管断面分布を示す図である。
【図１７】この発明の実施の形態２による別の分岐管を示す断面図である。
【図１８】この発明の実施の形態２による別の分岐管を示す断面図である。
【図１９】従来の分岐管が接続されている熱交換器を示す斜視図である。
【図２０】従来の分岐管を示す斜視図である。
【図２１】従来の分岐管の管内を流れる冷媒の様子を示す図である。
【図２２】従来の別の分岐管を示す斜視図である。
【図２３】従来の別の分岐管の管内を流れる冷媒の様子を示す図である。
【符号の説明】
１分岐管、１ａ分岐管入口部、１ｂ、１ｃ分岐管出口部、１ｄ分岐管接続部、２Ｕ字管、３熱交換器、４伝熱管、４ａ入口配管、４ｂ、４ｃ出口配管、５隔壁、６冷媒の流れ方向、７ａ、７ｂ、７ｃ冷媒の気相部、８ａ、８ｂ、８ｃ冷媒の液相部、９ａ、９ｂ、９ｃ冷媒、１０重力方向、１１分岐管入口部中心軸、１２Ｘ軸、１３Ｙ軸、１４Ｚ軸、１５原点、１６らせん板、２０管中心を通る鉛直軸[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a branch pipe and a heat exchanger used for refrigerant branching in a vapor compression refrigeration cycle.
[0002]
[Prior art]
In recent years, with the increase in the number of passes in the heat exchanger of the refrigeration air conditioner, many branch pipes are used, and improvement of branching performance is regarded as important. A conventional branch pipe will be described below with reference to the drawings.
[0003]
FIG. 19 is a perspective view showing the state of attachment of a conventional branch pipe to a heat exchanger, FIG. 20 is a perspective view showing the shape of the conventional branch pipe, and FIG. 21 is operated by connecting the heat exchanger to a refrigeration cycle. It is sectional drawing which shows the flow state of the refrigerant | coolant inside the conventional branch pipe at the time. In the figure, 1 is a branch pipe, 2 is a U-shaped pipe, 3 is a main body of the heat exchanger, 4 is a heat transfer pipe constituting the heat exchanger and through which the refrigerant flows, particularly 4a is an inlet pipe to the branch pipe 1, 4b Reference numerals 4c and 4c denote outlet pipes from the branch pipe 1, 6 denotes the flow direction of the refrigerant passing through the branch pipe 1, and 10 denotes the direction of gravity. Here, the U-shaped tube 2 and the heat transfer tube 4 and the branch tube 1 and the heat transfer tubes 4a, 4b and 4c are welded by brazing. Also, 1a is the branch pipe inlet, 1b, 1c are branched pipe outlet, 8a, 8b, 8c liquid phase portion of the refrigerant, 7 a, 7b, 7c is the gas phase of the refrigerant, 9a, 9b, 9c refrigerant The whole refrigerant | coolant which combined the liquid phase part and the gaseous-phase part is shown.
[0004]
About the branch pipe 1 comprised as mentioned above, the operation | movement is demonstrated using FIG. The refrigerant 9a is gas-liquid separated in a state where the refrigerant gas phase portion 7a is close to the central portion of the heat transfer tube and the liquid phase portion 8a of the refrigerant is close to an annular flow around the inner wall surface of the heat transfer tube. It flows in from the section 1a, is divided into the branch pipe outlet sections 1b and 1c, and flows out.
[0005]
Another conventional branch pipe is disclosed in JP-A-1-254239. FIG. 22 is an external view showing another conventional branch pipe, and FIG. 23 is a cross-sectional view showing the flow state of the refrigerant in the branch pipe when the heat exchanger is operated in contact with the refrigeration cycle. In the figure, 1 is a branch pipe, 1a is a branch pipe inlet, 1b and 1c are branch pipe outlets, and 16 is a spiral plate. The spiral plate 16 is inserted inside the branch pipe inlet 1a.
[0006]
The operation of the branch pipe 1 configured as described above will be described below with reference to FIG. The liquid phase portion 8a of the refrigerant and the gas phase portion 7a of the refrigerant flow from the branch pipe inlet 1a. At this time, the liquid phase portion 8a of the refrigerant and the gas phase portion 7a of the refrigerant are separated from each other in a state close to an annular flow, but the gas and liquid are mixed by turbulent flow by the spiral plate 16 when flowing through the branch pipe inlet 1a. Then, it is diverted to the branch pipe outlets 1b and 1c and flows out.
[0007]
[Problems to be solved by the invention]
However, in the conventional branch pipe described with reference to FIGS. 20 and 21, the liquid phase portion 8a of the refrigerant heavier than the gas phase portion 7a of the refrigerant is affected by the gravity 10 at the time of branching and adheres to the wall surface of the branch portion. However, the refrigerant 9a flows too much to the branch pipe outlet 1c, so that the refrigerant 9a cannot be evenly divided into the branch pipe outlets 1b and 1c, and the cooling performance of the heat exchanger is lowered. Moreover, it was impossible to divide into a desired diversion ratio.
[0008]
Further, in the branch pipe described in JP-A-1-254239, the refrigerant 8a and the gas phase portion 7a of the refrigerant are gas-liquid mixed by the spiral plate 16, but the refrigerant liquid phase is heavier than the gas phase portion 7a of the refrigerant. Since the part 8a is affected by the gravity 10 and the mixed refrigerant 9a collides with and adheres to the wall surface at the branch part, a large amount of the refrigerant 9a flows to the branch pipe outlet part 1c and cannot be evenly divided.
[0009]
The present invention has been made to solve the above-described problems, and an object of the present invention is to obtain a branch pipe that is not affected by gravity and that can achieve uniform distribution of a refrigerant and further a desired distribution ratio of the refrigerant. .
[0010]
[Means for solving the problems]
The branch pipe according to the present invention includes an inlet portion into which a fluid flows into the branch pipe body, a branch portion that branches the fluid that flows in from the inlet portion into a plurality of flow paths, and a fluid that flows through the branch portion. a plurality of outlets, the branch pipes and a partition wall provided in the tube leading to the branching portion from the inlet portion, the partition wall, along Utotomoni end of the inlet portion side in the gravity direction in the mounting state of the branch pipe body The entire cross section perpendicular to the central axis direction of the branch pipe at the end on the inlet side is formed so as to overlap a straight line that bisects the cross section of the pipe through the center of the pipe cross section . It is a structure in which the made refrigerant flows out from the plurality of outlet portions without substantially joining in the branch pipe . In addition, the partition wall has an end on the inlet side along the direction of gravity in the attached state of the branch pipe body and is cut at the center of the pipe, and the entire cross section perpendicular to the central axis direction of the branch pipe at the end on the inlet side is The refrigerant is formed so as to overlap two straight lines parallel to a straight line that bisects the cross section of the pipe through the center of the cross section of the pipe, and the refrigerant divided at the end on the inlet side is not substantially merged in the branch pipe. It is a structure that flows out from a plurality of outlets, and makes the opening angle of the end on the inlet side equal to the inclination angle of the spiral groove formed on the inner wall of the heat transfer tube connected to the inlet.
[0011]
Moreover, a partition is formed with a fin. Moreover, twisting as the septal wall approaching from the inlet part to the branching unit, in the bifurcation, in which arranged to be perpendicular to the branch direction of the plurality of flow paths.
[0012]
Further, the partition wall is provided in a straight line portion from the inlet portion to the branch portion.
[0013]
Moreover, the edge part by the side of the entrance part of a partition is made into a wedge shape.
[0014]
Moreover, it is a heat exchanger provided with the said branch pipe .
[0015]
DETAILED DESCRIPTION OF THE INVENTION
Embodiment 1 FIG.
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a perspective view showing a branch pipe according to Embodiment 1 of the present invention. In the figure, 1a is a branch pipe inlet part made of a straight pipe, 1b and 1c are branch pipe outlet parts made of a bent pipe, and 1d is a branch pipe connection part of a straight pipe perpendicular to the branch pipe inlet part 1a. Is configured. Reference numeral 5 denotes a partition wall, and 11 denotes a central axis of the branch pipe inlet 1a. The branch pipe 1 forms a branch pipe inlet 1a and a branch pipe connection 1d as a T-shaped pipe, and branches to the remaining end portion that is not substantially the center of the T-shaped pipe composed of the branch pipe inlet 1a and the branch pipe connection 1d. It is the shape which welded the pipe | tube exit parts 1b and 1c by brazing. Here, the branch pipe inlet 1a and the branch pipe outlets 1b and 1c are respectively connected to the inlet pipe 4a and the outlet pipes 4b and 4c shown in FIG. The partition wall 5 is welded to the inner wall of the branch pipe inlet 1a and the branch pipe connection 1d by brazing. This branch pipe is used in a heat exchanger as shown in FIG.
[0016]
Here, in order to make the explanation of the mounting posture of the branch pipe 1 easy to understand, the coordinate axes are determined using FIG. In FIG. 2, 12 indicates an X axis, 13 indicates a Y axis, 14 indicates a Z axis, and 15 indicates an origin. The origin 15 is the midpoint of the line segment connecting the centers of the pipe cross sections at the ends of the branch outlets 1b and 1c. The X axis is a straight line parallel to the central axis 11 of the branch pipe inlet 1a and passing through the origin 15. The Y axis 13 is a straight line connecting the origin 15 and the center of the pipe cross section at the end of the branch pipe inlet 1a. The Z axis 14 is the branch pipe. Let it be a straight line connecting the centers of the pipe cross sections of the outlet portions 1b and 1c. Further, the X-axis direction is taken as the refrigerant inflow direction of the branch pipe inlet 1a, and the Y-axis direction and the Z-axis direction are determined to be a right-handed system. FIG. 1 shows an example of the attachment posture of the branch pipe 1 when the Z axis is vertical.
[0017]
Next, how the partition wall 5 is attached will be described with reference to FIG. FIG. 3 is a cross-sectional view of the branch pipe 1 of FIG. 1 as viewed from the −Y axis direction. In the drawing, the partition wall 5 is disposed in the vicinity of the branch pipe inlet 1a so as to pass through the pipe center along the gravity direction 10 in the attached state of the branch pipe 1, and is twisted by 90 degrees as it approaches the branch section. In the vicinity, it is brazed so as to be perpendicular to the branching direction of the branch connecting portion 1d.
[0018]
The operation of the branch pipe 1 configured as described above will be described below. First, the state of the refrigerant flowing into the branch pipe 1 will be described with reference to FIGS. 4 and 5 are cross-sectional views of the inlet pipe 4a shown in FIG. 19 in the conventional example as seen from the −X-axis direction. In FIG. 4, 7a is a gas phase part of the refrigerant, 8a is a liquid phase part of the refrigerant, 9a is an entire refrigerant combining the gas phase part 7a of the refrigerant and the liquid phase part 8a of the refrigerant, and 20 is a vertical axis passing through the center of the pipe. Show.
[0019]
As shown in FIG. 4, most of the cross-sectional distribution of the refrigerant 9a in the inlet pipe 4a is such that the refrigerant gas phase portion 7a flows through the center of the inlet pipe 4a and the refrigerant liquid phase portion 8a is on the inner surface of the inlet pipe 4a. Accordingly, as shown in FIG. 5, the liquid phase portion 8a of the refrigerant having a large specific gravity flows largely below the inlet pipe 4a due to the influence of gravity, and the gas phase of the refrigerant having a small specific gravity is obtained. The distribution is such that the portion 7a flows more to the upper side of the inlet pipe 4a. As is apparent from the distributions of FIGS. 4 and 5, the distribution of the refrigerant gas phase portion 7 a and the refrigerant liquid phase portion 8 a in the cross section of the inlet pipe 4 a is substantially axisymmetric with respect to the vertical axis 20.
[0020]
Next, the state of the refrigerant 9a immediately after flowing into the branch pipe inlet 1a will be described with reference to FIGS. 6 and 7 are cross-sectional views of the end of the branch pipe inlet 1a as seen from the -X-axis direction. 6 and 7, 7b and 7c are refrigerant gas phase portions, 8b and 8c are refrigerant liquid phase portions, 9b and 9c are refrigerant gas phase portions 7b and 7c, and refrigerant liquid phase portions 8b and 8c, respectively. The entire refrigerant is shown. The refrigerant 9a flowing into the branch pipe inlet 1a is divided into the refrigerant 9b and the refrigerant 9c by the partition wall 5. Here, in the vicinity of the branch pipe inlet 1a, the partition wall 5 is disposed so as to overlap with the vertical axis 20 that is equivalent to the gravity direction 10 in the attached state of the branch pipe 1, so that the refrigerant after being divided by the partition wall 5 The flow rates of the gas phase portions 7b and 8b and the liquid phase portions 7c and 8c of the refrigerant are substantially equal, and the total refrigerant 9b, which is the sum of the gas phase portions 7b and 7c of the refrigerant and the liquid phase portions 8b and 8c of the refrigerant, The flow rate of 9c is almost equal.
[0021]
Further, the flow of the refrigerant passing through the branch pipe inlet 1a and proceeding to the branch pipe outlets 1b and 1c will be described with reference to FIG. FIG. 8 is a cross-sectional view of the branch pipe 1 as viewed from the −Y axis direction. In FIG. 8, the hatched area indicates the refrigerant 9c flowing in the pipe, and the dotted portion indicates the refrigerant 9b flowing in the pipe. Here, since the partition wall 5 is brazed to the pipe inner walls of the branch pipe inlet 1a and the branch pipe connection 1d, the refrigerants 9b and 9c diverted by the partition 5 at the inlet of the branch pipe inlet 1a Outflow from the branch pipe outlets 1b and 1c, respectively, without joining along the twist.
[0022]
As described above, according to the present embodiment, it is possible to effectively and evenly divide the refrigerant 9a having a substantially axisymmetric distribution with respect to the vertical axis 20 in the straight tube portion of the heat transfer tube 4. In addition, the branch pipe 1 is attached to the end of the straight pipe portion of the heat transfer pipe 4 and branches the refrigerant at the branch pipe inlet 1a, which is a straight pipe portion, so that the conventional branch pipe that branches the refrigerant after passing through the bent pipe The refrigerant can be diverted in a more stable state, and the effect of improving the uniform diversion performance is achieved. Further, since the partition wall 5 is twisted at the straight pipe portion of the branch pipe inlet 1a, it is easier to process and weld the partition wall 5 than to weld the partition wall 5 in the bent pipe, and to reduce the manufacturing cost. Can do.
[0023]
In the first embodiment, the Z-axis 14 of the branch pipe 1 is positive in the vertical direction, and the branch pipe 1 connects the straight pipe branch pipe inlet 1a and the straight pipe branch pipe connecting portion 1d to the T-shaped pipe. The branch pipe outlet portions 1b and 1c of the bent pipe are welded to the remaining end portion of the T-shaped pipe composed of the branch pipe inlet portion 1a and the branch pipe connecting portion 1d, and the partition wall 5 is connected to the branch pipe 1 As an example, the structure is attached so as to overlap with the vertical shaft 20 at the entrance of. However, the attachment posture of the branch pipe 1, the structure and processing method of the branch pipe 1, the structure and processing method of the partition wall, the attachment method, and the attachment posture are arbitrary, and at least the partition wall 5 is connected to the inlet pipe 4a. In the portion 1a, provided along the direction of gravity 10 in the attached state of the branch pipe 1, the divided refrigerants 9b and 9c flow out from the branch pipe outlets 1b and 1c without joining in the branch pipe 1. Any structure can be used.
[0024]
The modification examples are listed below with reference to the drawings. First, the modification about the attitude | position and structure of the branch pipe 1 is shown. 9 (a) is a perspective view of a branch pipe in the case of a vertically downward direction direction Y axis. In this case, the partition wall 5 may not be twisted. FIG. 9B is a perspective view of the branch pipe when the branch pipe connecting portion 1d and the branch pipe outlet portions 1b and 1c are formed by bending the pipe, and the branch pipe inlet portion 1a is welded thereto. FIG. 9C is a perspective view of the branch pipe when the branch pipe outlet portions 1b and 1c are welded to the branch pipe inlet portion 1a.
[0025]
Next, the modification about the structure of the partition 5 is shown. FIG. 10A shows a case where the partition wall 5 is longer than the end of the branch pipe inlet 1a. FIG. 10B shows a case where the partition wall 5 is shorter than the end of the branch pipe inlet 1a. 11A shows a case where the end of the partition wall 5 is inclined with respect to the YZ plane, FIG. 11B shows a case where the end of the partition wall 5 has a wedge shape, and FIG. It is the case where it is bent and attached. Here, when the tip of the partition wall 5 has a wedge shape as shown in FIG. 11B, the thickness of the partition wall at the time of branching can be made thinner, and the pressure loss of the partition wall 5 becomes smaller. A uniform flow can be split. In FIG. 11C, a desired distribution ratio can be obtained.
[0026]
Further, FIG. 12 (a) is a case where cut end portion of the partition wall 5 at the upper and lower side, and FIG. 12 (b) state of the partition wall 5 as viewed from the -X-axis direction, FIG. 12 (c) Z It is a figure which shows the mode of the partition 5 seen from the axis | shaft. FIG. 12D is a view showing a heat transfer tube 4a having a spiral groove on the inner wall. FIG. 12 (e) is a view in which the branch pipe 1 shown in FIG. 12 (a) is attached to the heat transfer tube 4a having a spiral groove on the inner wall, and the inside of the wall of the heat transfer tube 4a and the branch pipe inlet 1a is viewed from the central axis 11. is there.
[0027]
In the figure, 16 is a spiral groove, 17 is a flow direction of the liquid phase portion of the refrigerant passing between the spiral grooves 16, 18 is an opening angle with respect to the central axis 11 of the partition wall 5, and 19 is an inclination angle with respect to the central axis 11 of the spiral groove. Here, the inclination angle 19 of the spiral groove 16 and the opening angle 18 of the partition wall 5 are equal. The flow of the refrigerant will be described with reference to FIG. When the spiral groove 16 is present inside the heat transfer tube 4a, the flow direction 17 of the liquid phase portion of the refrigerant flowing between the spiral grooves 16 is equal to the inclination angle 19 of the spiral groove. Further, since the opening angle 18 of the partition wall 5 is equal to the inclination angle 19 of the spiral groove, the flow direction 17 of the liquid phase portion of the refrigerant flowing in the spiral groove and the partition wall 5 are parallel. Therefore, the resistance that the refrigerant receives from the partition wall 5 is reduced, and there is an effect that the flow can be diverted without increasing the increase in pressure loss on the refrigerant side.
[0028]
FIG. 13 shows a case where the partition wall 5 according to the present invention is attached to the branch pipe of FIG. 19 described as a conventional example. In the branch pipe 1 of FIG. 13, since the partition wall 5 is attached to the bent portion, it is difficult to manufacture and attach the partition wall. However, since the conventional branch pipe 1 can be used, the branch pipe 1 is manufactured. There is an effect that the cost of the mold can be saved and the conventional manufacturing technology can be utilized, and the manufacturing cost can be reduced.
[0029]
Embodiment 2. FIG.
Embodiment 2 of the present invention will be described below with reference to the drawings. Fig.14 (a) is a perspective view which shows the branch pipe 1 in Embodiment 2 of this invention. Since the description of the branch pipe 1 is the same as that of the first embodiment, it is omitted. FIG. 14B is a cross-sectional view of the end of the branch pipe inlet 1a as seen from the −X axis direction. Here, the partition wall 5 is not formed by welding a single plate, but by forming fins inside the branch pipe inlet 1a. In FIG. 14 (b), the upper and lower partition walls 5 are arranged at the end of the branch pipe inlet 1a along the direction of gravity in the attached state of the branch pipe main body, and as shown in FIG. 14 (a), Twist 90 degrees while proceeding in the flow direction 6 of the refrigerant in the part 1a, and is in a state perpendicular to the branch direction of the branch pipe connecting part 1d inside the branch pipe connecting part 1d.
[0030]
The operation of the branch pipe 1 configured as described above will be described below. As shown in FIG. 4 of the first embodiment, the refrigerant flowing in the heat transfer tube 4 has the gas phase portion 7a of the refrigerant flowing in the center of the heat transfer tube 4a and the liquid phase portion 8a of the refrigerant in the heat transfer tube 4a. As shown in FIG. 5, the liquid phase portion 8a of the refrigerant having a large specific gravity flows under the heat transfer tube 4a due to the influence of gravity and has a small specific gravity. The distribution is such that a large amount of the refrigerant gas phase portion 7a flows to the upper side of the heat transfer tube 4a.
[0031]
Next, the state of the refrigerant immediately after passing through the branch pipe inlet 1a will be described with reference to FIGS. As shown in FIGS. 15 and 16, the liquid phase portion 8 a of the refrigerant that has flowed into the branch pipe inlet 1 a is divided into the refrigerant 8 b and the refrigerant 8 c by the partition wall 5. On the other hand, the refrigerant gas phase portion 7 a is not completely branched by the partition wall 5. Thereafter, the liquid phase portions 8b and 8c of the refrigerant proceed through the branch pipe inlet 1a. However, since the refrigerant gas phase portion 7a has a distribution passing through the center of the pipe as shown in FIGS. 8b and 8c only merge slightly and reach the branch pipe connection 1d, and then each flow out from the branch pipe outlets 1b and 1c. As a result, the flow rates of the liquid phase portions 9b and 9c of the refrigerant become substantially equal. On the other hand, the refrigerant gas phase portion 7a is not strongly affected by gravity, and the liquid phase portions 9b and 9c of the refrigerant are almost uniformly divided to flow through the branch pipe outlets 1b and 1c through which the refrigerant gas phase portion flows. Since the cross-sectional areas are substantially equal, the gas phase portion of the refrigerant is also divided substantially uniformly.
[0032]
As described above, according to the second embodiment, similarly to the first embodiment, the refrigerant 9a having a substantially axisymmetric distribution with respect to the vertical axis 20 in the straight pipe portion of the heat transfer tube 4 is effectively provided. It is possible to uniformly divert. In addition, the branch pipe 1 is attached to the end of the straight pipe portion of the heat transfer pipe 4 and branches the refrigerant at the branch pipe inlet 1a, which is a straight pipe portion, so that the conventional branch pipe that branches the refrigerant after passing through the bent pipe The refrigerant can be distributed and more evenly distributed in a more stable state. Furthermore, since the partition wall 5 is twisted at the straight pipe portion of the branch pipe inlet 1a, it is apparently easier to process and weld the partition wall 5 than to weld the partition wall 5 in the bent pipe. Furthermore, by processing the partition walls 5 as fins, the degree of freedom of the manufacturing method of the partition walls 5 is increased, and the manufacturing cost can be expected to be reduced.
[0033]
In the present embodiment, the Z-axis 14 of the branch pipe 1 is positive upward in the vertical direction, and the branch pipe 1 has a straight pipe branch pipe inlet 1a and a straight pipe branch pipe connecting portion 1d formed by a T-shaped pipe. An example of a structure in which the partition wall 5 is formed by forming and welding the branch pipe outlet portions 1b and 1c of the bent pipe to the remaining end portions that are not substantially in the center, and processing fins on the wall surface of the branch pipe inlet portion 1a is given as an example. However, the mounting posture of the branch pipe 1, the structure and processing method of the branch pipe 1, the structure and processing method of the partition wall, the mounting method, and the mounting posture are arbitrary.
[0034]
Below, the modification of the partition 5 is enumerated using a figure. 17, FIG. 18A and FIG. 18B are cross-sectional views of the partition wall 5 as viewed from the −X axis direction. FIG. 17 shows a case where fins having a height substantially equal to the straight pipe inner diameter are used as the partition walls 5, FIG. 18A shows a case where blunt tip-shaped partition walls 5 are used, and FIG. This is the case. In the branch pipe 1 of FIG. 17, when the liquid phase parts 8b and 8c of the refrigerant are distributed in the bottom part in the branch pipe inlet 1a, the branch pipe 1 of FIGS. 18 (a) and 18 (b) When the liquid phase portions 8b and 8c are distributed in the form of a thin film along the inner wall surface of the branch pipe inlet portion 1a, the same effects as those described in the above embodiments can be obtained. Nor. Here, in the branch pipe 1 of FIG. 17, since only one partition wall 5 is required, there is an effect that the number of parts can be reduced. On the other hand, in the branch pipe 1 of FIG. 18A, the partition wall 5 can be manufactured in the branch pipe inlet 1a by performing press working from the outside of the pipe. Furthermore, in the branch pipe 1 of FIG. 18B, the partition wall 5 can be manufactured in the branch pipe inlet 1a by using an electric sewing tube method in which the partition wall 5 is pressed into a copper plate and then tubular. The partition wall 5 can be easily processed, and the manufacturing cost can be further reduced.
[0035]
【The invention's effect】
As described above, according to according to the invention of claim 1, wherein, along Utotomoni gravity direction end portion of the inlet portion side in the mounting state of the branch pipe main body, the center axis of the branch pipe at the end of the inlet side Are formed so as to overlap a straight line that bisects the cross section of the pipe through the center of the cross section of the pipe, and a plurality of refrigerants divided at the end on the inlet side are not substantially merged in the branch pipe. Since the partition wall having a structure that flows out from the outlet portion is provided in the pipe from the inlet portion to the branch portion, an effect that the refrigerant can be evenly divided can be obtained. According to the second aspect of the present invention, the end of the partition wall on the inlet side is cut at the tube center, and the opening angle of the end and the inclination of the spiral groove formed on the inner wall of the heat transfer tube connected to the inlet. Since the angle is made equal, the effect of diverting can be obtained without increasing the increase in pressure loss on the refrigerant side .
[0036]
Further, according to the invention described in claim 3, since the partition walls are formed by the fins, an effect of reducing the manufacturing cost can be obtained. Furthermore, according to the invention of claim 4, the partition wall is twisted as it approaches the branch portion from the inlet portion, and the branch portion is arranged so as to be perpendicular to the branch direction of the plurality of flow paths. The effect of evenly diverting is obtained.
[0037]
In addition, according to the invention described in claim 5, since the partition wall is provided only in the straight line portion from the inlet portion to the branch portion, an effect of reducing the manufacturing cost can be obtained.
[0038]
According to the invention of claim 6, wherein the tip end of the inlet side of the partition wall, since the wedge shape, the effect can be uniformly diverts coolant without increasing the pressure loss increase of the refrigerant is obtained.
[0039]
Further, according to the invention of claim 7 , the above-mentioned effects can be obtained.
[Brief description of the drawings]
FIG. 1 is a perspective view showing a branch pipe according to Embodiment 1 of the present invention.
FIG. 2 is a diagram showing coordinate axes of a branch pipe according to Embodiment 1 of the present invention.
FIG. 3 is a cross-sectional view showing a branch pipe according to Embodiment 1 of the present invention.
FIG. 4 is a diagram showing a pipe cross-sectional distribution of refrigerant flowing in a heat transfer pipe connecting branch pipes according to Embodiment 1 of the present invention.
FIG. 5 is a diagram showing another pipe cross-sectional distribution of the refrigerant flowing in the heat transfer pipes connecting the branch pipes according to Embodiment 1 of the present invention.
FIG. 6 is a diagram showing a refrigerant pipe cross-sectional distribution at a branch pipe inlet of a branch pipe according to Embodiment 1 of the present invention.
FIG. 7 is a diagram showing another pipe cross-sectional distribution of the refrigerant at the branch pipe inlet of the branch pipe according to Embodiment 1 of the present invention.
FIG. 8 is a diagram showing a refrigerant distribution in a branch pipe according to Embodiment 1 of the present invention.
FIG. 9 is a perspective view showing another branch pipe according to Embodiment 1 of the present invention.
FIG. 10 is a perspective view showing another branch pipe according to Embodiment 1 of the present invention.
FIG. 11 is a perspective view showing another branch pipe according to Embodiment 1 of the present invention.
FIGS. 12A and 12B are a perspective view and a sectional view showing another branch pipe according to Embodiment 1 of the invention. FIGS.
FIG. 13 is a perspective view showing another branch pipe according to Embodiment 1 of the present invention.
FIG. 14 is a perspective view and a sectional view showing a branch pipe according to Embodiment 2 of the present invention.
FIG. 15 is a diagram showing another pipe cross-sectional distribution of the refrigerant at the branch pipe inlet of the branch pipe according to Embodiment 2 of the present invention.
FIG. 16 is a diagram showing another pipe cross-sectional distribution of the refrigerant at the branch pipe inlet of the branch pipe according to the second embodiment of the present invention.
FIG. 17 is a cross-sectional view showing another branch pipe according to Embodiment 2 of the present invention.
FIG. 18 is a sectional view showing another branch pipe according to Embodiment 2 of the present invention.
FIG. 19 is a perspective view showing a heat exchanger to which a conventional branch pipe is connected.
FIG. 20 is a perspective view showing a conventional branch pipe.
FIG. 21 is a view showing a state of a refrigerant flowing in a pipe of a conventional branch pipe.
FIG. 22 is a perspective view showing another conventional branch pipe.
FIG. 23 is a diagram illustrating a state of a refrigerant flowing in a pipe of another conventional branch pipe.
[Explanation of symbols]
1 branch pipe, 1a branch pipe inlet part, 1b, 1c branch pipe outlet part, 1d branch pipe connection part, 2 U-shaped pipe, 3 heat exchanger, 4 heat transfer pipe, 4a inlet pipe, 4b, 4c outlet pipe, 5 partition , 6 Flow direction of refrigerant, 7a, 7b, 7c Gas phase part of refrigerant, 8a, 8b, 8c Liquid phase part of refrigerant, 9a, 9b, 9c Refrigerant, 10 Gravity direction, 11 Branch pipe inlet central axis, 12 X Axis, 13 Y-axis, 14 Z-axis, 15 origin, 16 spiral plate, 20 Vertical axis passing through tube center

Claims

An inlet part through which a fluid flows into the branch pipe body, a branch part for branching the fluid flowing in from the inlet part into a plurality of flow paths, a plurality of outlet parts for letting out the fluid flowing through the branch part, and the inlet In a branch pipe provided with a partition wall provided in the pipe from the section to the branch section ,
The partition is
Along the ends of the inlet side in the gravity direction in the mounting state of the branch pipe body Utotomoni,
The entire cross section perpendicular to the central axis direction of the branch pipe at the end on the inlet side is formed to overlap a straight line that bisects the pipe cross section through the center of the pipe cross section,
Branch pipe, characterized in that the refrigerant diverted at the end of the inlet portion has a structure which flows out from the plurality of outlets without substantially meet at the branch pipe.

An inlet part through which a fluid flows into the branch pipe body, a branch part for branching the fluid flowing in from the inlet part into a plurality of flow paths, a plurality of outlet parts for letting out the fluid flowing through the branch part, and the inlet In a branch pipe provided with a partition wall provided in the pipe from the section to the branch section,
The partition is
The end on the inlet side is cut along the center of the pipe along the direction of gravity in the attached state of the branch pipe body,
The entire cross section perpendicular to the central axis direction of the branch pipe at the end on the inlet side is formed to overlap two straight lines that pass through the center of the pipe cross section and are parallel to a straight line that bisects the pipe cross section. ,
The refrigerant diverted at the end on the inlet side flows out from the plurality of outlets without substantially joining in the branch pipe,
A branch pipe characterized in that an opening angle of an end portion on the inlet portion side is equal to an inclination angle of a spiral groove formed on an inner wall of a heat transfer tube connected to the inlet portion .

The branch pipe according to claim 1 or 2 , wherein the partition wall is formed by a fin.

The partition wall is twisted as it approaches the branch portion from the inlet portion, and the branch portion is disposed so as to be perpendicular to the branch direction of the plurality of flow paths. The branch pipe according to item 1.

The branch pipe according to any one of claims 1 to 4, wherein the partition wall is provided only in a straight line portion extending from the inlet portion to the branch portion.

The previous end of the inlet side of the partition wall, the branch pipe according to any one of claims 1 to 5, characterized in that the wedge-shaped.

A heat exchanger comprising the branch pipe according to any one of claims 1 to 6.