JP3906764B2

JP3906764B2 - Plate heat exchanger

Info

Publication number: JP3906764B2
Application number: JP2002251724A
Authority: JP
Inventors: 光春沼田; 育弘岩田; 達己高瀬
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2002-08-29
Filing date: 2002-08-29
Publication date: 2007-04-18
Anticipated expiration: 2022-08-29
Also published as: JP2004092949A

Description

【０００１】
【発明の属する技術分野】
【０００２】
本願発明は、プレート式熱交換器の構成に関するものである。
【従来の技術】
【０００３】
例えば蒸発器等の熱交換器を液膜流下型のプレート式熱交換器によって形成するようにした場合、例えば複数枚並設された各液膜流下型の伝熱プレートの上部に、それぞれ第１の流体散布溝を設けて、各伝熱プレートの一側面側伝熱面に第１の流体を液膜状態で流下させ、他面側の第２の流体と熱交換させて、蒸発させるように構成されている（例えば特開２０００−２８３６６２号公報参照）。
【０００４】
また、この種のプレート式熱交換器では、一般に伝熱プレート面の濡れ性、拡散性、伝熱特性を向上させるために、その伝熱面には凹凸溝が形成されている（特開平１０−３００３７１号公報参照）。
【０００５】
このような液膜流下型プレート式熱交換器において、冷媒等第１の流体を伝熱面に均一に濡らす場合、流量を非常に多くするか、または少ない流量の場合、別部材を取付け、隙間で広げる方法がある。しかし、流量を多くすると液膜が厚くなり性能が低下するし、別部材の取付けは、構造が複雑になること、部品点数が増えることなどにより、製作が難しくなる問題がある。
【０００６】
そこで、本件出願の発明者等は、このような技術的背景の下で、例えば図１０〜図１２および図１３、図１４に示すような第１，第２の２種類のプレート式熱交換器の伝熱プレートを試作し、上記問題の解決を試みた。
【０００７】
先ず第１の試作例である図１０〜図１２において、符号１は同伝熱プレートである。該伝熱プレート１は、例えば全体として縦に長いステンレス製金属板をプレス成形して形成されており、その伝熱面外周に接合一体化用の鉤形のフレーム部１ａ、同伝熱面中央側の主たる伝熱面部に上方から下方にジグザグに延びる断面Ｖ字状の凹凸溝部３、該凹凸溝部３の両側左右に各々４個の第２の流体の導入、導出用の各分配ヘッダ接続口４ａ，４ａ・・、４ｂ，４ｂ・・、上記凹凸溝部３の上部に第１の流体の散布溝５、上記凹凸溝部３の下部に蒸気抜き口部６等が各々設けられている。
【０００８】
一方、上記第１の流体の冷媒散布溝５のフラットな底部には、第１の流体の散布孔５ａが開孔され、同散布孔５ａと上記凹凸溝部３の上部との間には、全体として略台形形状をなして、上方から下方に順次左右方向の幅が広くなる第１，第２，第３の凸部７ａ，７ｂ，７ｃとそれらの間に形成される第１，第２の凹部７ｅ，７ｆよりなる流体拡散部７が設けられている。
【０００９】
そして、上記第１の流体の散布孔５ａから流出した第１の流体は、例えば図１１および図１２に示すように、先ず伝熱プレート１のフラットな壁面１ｃを伝わって、当該流体拡散部７の第１の凸部７ａに到達し、その後、同第１の凸部７ａ部分で停滞、滞留し、量が増加することによって左右に所定幅拡散される。
【００１０】
その後、同第１の凸部７ａを乗り超えて、同第１の凸部７ａと次の第２の凸部７ｂとの間に形成された第１の凹部７ｅ内に流速を増して流れ落ち、均一に分散される。さらに、その後、第２の凸部７ｂ部分で再び流速が落ちて停滞、滞留し、その量の増大により所定幅左右に拡散する。
【００１１】
その後、同第２の凸部７ｂを乗り超えて、同第２の凸部７ｂと次の第３の凸部７ｃとの間に形成された第２の凹部７ｆに流速を増して流れ落ち、均一に分散される。さらに、その後、第３の凸部７ｃ部分で再び流速が落ちて停滞、滞留し、その量の増大により所定幅左右に拡散する。
【００１２】
そして、このようにして、最終的に最も左右方向に幅が広く、厚さの均一な液膜状の流れを形成した上で、当該伝熱プレート１の伝熱面における熱交換作用の主要部を形成する凹凸溝部３の全体に均一に第１の流体を流し、濡れ性を良くして可能な限り効率の良い熱交換（蒸発）作用を行わせる。
【００１３】
一方、図１３および図１４は、第２の試作例であり、上記流体拡散部７の左右方向への拡散効果を、さらに向上させることを意図して、上記流体拡散部７の第１，第２，第３の各凸部７ａ，７ｂ，７ｃ、第１，第２の凹部７ｅ，７ｆの左右方向の長さを、より長くしたものであり、その他の構成は、上記第１の試作例と全く同一である。
【発明が解決しようとする課題】
【００１４】
以上のように、流体拡散部７の流体拡散作用は、伝熱プレート１の伝熱面全体に均一に第１の流体を流し、濡れ性を向上させる上で、極めて重要な役割を果たす。
【００１５】
したがって、同流体拡散部７は、第１の流体の流れを、できるだけ左右方向に広く拡散させることができる拡散性能の高いものであることが好ましい。
【００１６】
その意味で、本件出願の発明者等は、当初上記第１の試作例（図１０〜図１２）よりも、第２の試作例（図１３および図１４）の方が拡散性能に優れていると考えた。
【００１７】
ところが、実際に流体を流して見ると、少なくとも散布量が同一である限り、図１１と図１４に対比して示すように、両者の間の拡散性能には殆ど差がなく、また第１，第２，第３の凸部７ａ，７ｂ，７ｃの各々で見ても、壁面１ｃから第１の凸部７ａ、第１の凸部７ａから第２の凸部７ｂの凹凸部分では、それぞれ拡散効果が見られるが、第２の凸部７ｂ以降の凹凸部分では、殆ど拡散効果が見られないことが分った。
【００１８】
したがって、第２の試作例のように流体拡散部７の凹凸部の幅を広くしただけでは、その拡散性能を向上させることができない。
【００１９】
このような事情に鑑み、種々の検討分析を行った結果、上記の原因は、上記流体散布孔から滴下される流体が、一旦フラットな壁面側に付着して流下し、その時点で流速を大きく低下させ、速度エネルギーを小さくしてしまった状態で、第１の凸部に到達するので、同第１の凸部部分自体で、すでに左右方向へ広がろうとする速度成分ベクトルが小さくなってしまっていることにあることが分った。
【００２０】
本願発明は、このような知見に基き、流体散布孔から流体拡散部の最初の凸部に流体が直接落下状態で滴下されるようにすることにより、その落下エネルギーを確保せしめ、同落下エネルギーを活用して、有効に拡散性能を向上させるようにしたプレート式熱交換器を提供することを目的とするものである。
【課題を解決するための手段】
【００２１】
本願発明は、同目的を達成するために、次のような課題解決手段を備えている。
【００２２】
（１）第１の課題解決手段
先ず本願発明の第１の課題解決手段は、複数枚の伝熱プレート１１Ａ，１１Ｂ、１１Ａ，１１Ｂ・・・よりなり、それら各伝熱プレート１１Ａ，１１Ｂ、１１Ａ，１１Ｂ・・・の伝熱面の主たる伝熱面部に凹凸溝部１３、該凹凸溝部１３の両側に第２の流体Ｙの導入、導出用の各分配ヘッダ接続口１４ａ，１４ａ・・、１４ｂ，１４ｂ・・、上記凹凸溝部１３の上部に第１の流体Ｘの散布溝１５がそれぞれ設けられているとともに、上記複数枚の伝熱プレート１１Ａ，１１Ｂ、１１Ａ，１１Ｂ・・・の相互に隣合う伝熱プレート１１Ａ，１１Ｂの何れか一側面側に上記第１の流体Ｘを上記流体散布溝１５より滴下して液膜状に拡散流下させ、他側面側を流れる上記第２の流体Ｙと熱交換させる液膜流下型のプレート式熱交換器であって、上記流体散布溝１５の底部に設けられた第１の流体Ｘの散布孔１５ａと上記伝熱プレート１１Ａ，１１Ｂの主たる伝熱面との間に、上記第１の流体Ｘを伝熱面全体に拡散させる上方から下方に順次左右方向の幅が広くなる複数の凸部１７ａ，１７ｂ，１７ｃとそれら各凸部１７ａ，１７ｂ，１７ｃの間の凹部７ｅ，７ｆとよりなる凹凸構造の流体拡散部１７を有するとともに、該流体拡散部１７は、上記第１の流体Ｘの散布孔１５ａよりも所定寸法Ｌ以上下方に位置し、当該第１の流体Ｘの散布孔１５ａから滴下される第１の流体Ｘが上記伝熱プレート１１Ａ，１１Ｂの壁面１１ｃ，１１ｃを伝わることなく、所定の重力加速度をもって直接落下状態で衝突し、同衝突時のエネルギーで左右に広がるように構成されている。
【００２３】
したがって、このような構成では、上記第１の流体Ｘの散布孔１５ａから滴下された第１の流体Ｘが、上記上方から下方に順次左右方向の幅が広くなる複数の凸部１７ａ，１７ｂ，１７ｃとそれら各凸部１７ａ，１７ｂ，１７ｃの間の複数の凹部１７ｅ，１７ｆとよりなる凹凸構造の流体拡散部１７の最初の凸部１７ａに所定の重力加速度をもって衝突し、同衝突時の拡散エネルギーで、従来よりも遥かに大きく左右に広がる。
【００２４】
そして、該大きく広がった第１の流体Ｘが、さらに次の凹凸部１７ｅ，１７ｂ，１７ｆ，１７ｃで、従来同様に拡散均一化される。
【００２５】
しかも、同流体拡散部１７は、上記第１の流体Ｘの散布孔１５ａよりも所定寸法Ｌ以上下方に位置し、当該第１の流体Ｘの散布孔１５ａから滴下される第１の流体Ｘが上記伝熱プレート１１Ａ，１１Ｂの壁面１１ｃ，１１ｃを伝わることなく、所定の重力加速度をもって直接落下状態で衝突し、同衝突時のエネルギーで左右に大きく広がるように構成されていることから、拡散効果が高い。
【００２６】
したがって、最終的に伝熱プレート１１Ａ，１１Ｂ、１１Ａ，１１Ｂ・・・の上記凹凸溝部１３よりなる伝熱面積の大きい主たる伝熱面に供給される第１の流体Ｘは、同凹凸面よりなり伝熱面積の大きい主たる伝熱面の全体を時間をかけながら一層均一に覆う有効な液膜状の流れとなる。
【００２７】
その結果、上記第２の流体Ｙとの熱交換効率も大きく向上する。
【００２８】
（２）第２の課題解決手段
次に本願発明の第２の課題解決手段は、伝熱プレート１１Ａ，１１Ｂの何れか一側面側に第１の流体Ｘを所定の構造の流体散布溝１５より滴下して液膜状に拡散流下させ、他側面側を流れる第２の流体Ｙと熱交換させる液膜流下型のプレート式熱交換器であって、上記流体散布溝１５の第１の流体Ｘの散布孔１５ａと上記伝熱プレート１１Ａ，１１Ｂの主たる伝熱面との間に、第１の流体Ｘを伝熱面全体に拡散させる凹凸構造の流体拡散部１７を有するとともに、該流体拡散部１７は、上記第１の流体Ｘの散布孔１５ａよりも所定寸法Ｌ以上下方に位置し、かつ当該第１の流体Ｘの散布孔１５ａから滴下される第１の流体Ｘが上記伝熱プレート１１Ａ，１１Ｂの壁面１１ｃ，１１ｃを伝わることなく、直接落下状態で衝突するように構成されてなるプレート式熱交換器であって、上記流体散布溝１５の第１の流体Ｘの散布孔１５ａは、相互に隣合う伝熱プレート１１Ａ，１１Ｂ各々の当該流体散布溝１５，１５底部の相対向する傾斜面に形成して、互いに相手側伝熱プレート１１Ａ，１１Ｂの流体拡散部１７，１７の最初の凸部１７ａ，１７ａ面に向けて吐出状態で滴下させるように構成している。
【００２９】
したがって、このような構成では、上記請求項１の発明の場合と同様に第１の流体Ｘの散布孔１５ａから滴下された第１の流体Ｘが、上記流体拡散部１７の最初の凸部１７ａに所定の重力加速度をもって衝突し、同衝突時の拡散エネルギーで、従来よりも遥かに大きく左右に広がる。
【００３０】
しかも、この発明の構成では、その場合において、上記相互に隣合う各伝熱プレート１１Ａ，１１Ｂの流体散布溝１５底部の第１の流体Ｘの流体散布孔１５ａから吐出された第１の流体Ｘが、互いに相対向する流体拡散部１７，１７の最初の凸部１７ａ，１７ａ面に、所定の重力加速度をもって衝突し、同衝突時の拡散エネルギーで、従来よりも遥かに大きく左右に広がるようになっている。
【００３１】
そして、該特に大きく広がった第１の流体Ｘが、さらに次の凹凸部１７ｂ，１７ｃ、１７ｅ，１７ｆで、従来同様に拡散均一化される。
【００３２】
したがって、最終的に伝熱プレート１１Ａ，１１Ｂの主たる伝熱面に供給される第１の流体Ｘは、同主たる伝熱面の全体を、より均一に覆うより有効な液膜状の流れとなる。
【００３３】
その結果、第２の流体Ｙとの熱交換効率もさらに向上する。
【００３４】
（３）第３の課題解決手段
本願発明の第３の課題解決手段は、上記第１の課題解決手段の構成における流体散布溝１５の散布孔１５ａを、当該流体散布溝１５底部のフラット面に形成して、鉛直方向下方に滴下させるようにしている。
【００３５】
したがって、このような構成では、当該流体散布溝１５底部のフラット面に形成された流体散布孔１５ａから、鉛直方向下方に滴下する流体Ｘが、上記流体拡散部１７の最初の凸部１７ａに所定の重力加速度をもって衝突し、同衝突時の拡散エネルギーで、従来よりも遥かに大きく左右に広がる。
【００３６】
そして、該大きく広がった第１の流体Ｘが、さらに次の凹凸部１７ｂ，１７ｃ、１７ｅ，１７ｆで、従来同様に拡散均一化される。
【００３７】
（４）第４の課題解決手段
本願発明の第４の課題解決手段は、上記第１の課題解決手段の構成における流体散布溝１５の散布孔１５ａを、当該流体散布溝１５底部の傾斜面に形成して、鉛直方向下方に滴下させるようにしている。
【００３８】
したがって、このような構成では、当該流体散布溝１５底部の傾斜面に形成された流体散布孔１５ａから、伝熱プレート１１Ａ，１１Ｂの壁面に近寄らせることなく、鉛直方向下方に滴下させやすくなり、同滴下する流体が、上記流体拡散部１７の最初の凸部１７ａに所定の重力加速度をもって衝突し、同衝突時の拡散エネルギーで、従来よりも遥かに大きく左右に広がる。
【００３９】
そして、該大きく広がった第１の流体Ｘが、さらに次の凹凸部１７ｂ，１７ｃ、１７ｅ，１７ｆで、従来同様に拡散均一化される。
【００４０】
（５）第５の課題解決手段
本願発明の第５の課題解決手段は、上記第１，第２，３又は第４の課題解決手段の構成における、上記流体拡散部１７の最初の凸部１７ａは、それよりも下方側の凸部１７ｂ，１７ｃよりも高さが高く構成されている。
【００４１】
したがって、このような構成では、上記第１の流体の散布孔１５ａから滴下する第１の流体Ｘが確実に最初の凸部１７ａに衝突し、より有効に上述の作用を果たすようになる。
【発明の効果】
【００４２】
以上の結果、本願発明によると、滴下流体の散布量を増やしたり、隙間形成のための別部材を設けることなく、伝熱面に均一で適度な厚さの液膜を形成することができる。
【００４３】
したがって、構造が簡単で、製作も容易となり、低コストで、高性能のプレート式熱交換器を提供することができる。
【発明の実施の形態】
【００４４】
以下、添付の図面を参照して、本願発明のいくつかの実施の形態について説明する。
【００４５】
（実施の形態１）
先ず図１ないし図５には、本願発明の実施の形態に係るプレート式熱交換器の全体および要部の構造と作用が示されている。
【００４６】
このプレート式熱交換器１０は、例えば図１〜図３に示すように、前後プレート２６，２７間に、第１，第２の複数枚の伝熱プレート１１Ａ，１１Ａ・・および１１Ｂ，１１Ｂ・・を交互に重ね合わせて第１の流体通路２２と第２の流体通路２３とを順次隣接配置してなり、上記第１の流体通路２２を上方から下方に向かって流れる第１の流体Ｘと上記第２の流体通路２３を流れる第２の流体Ｙ（図示省略）とを熱交換させるように構成されている。
【００４７】
上記第１の流体通路２２は、上記第１，第２の各伝熱プレート１１Ａ，１１Ｂにそれぞれ形成され、かつ鉛直方向に対して所定の傾斜角で互いに反対向きに傾斜し、その下端において当該傾斜方向が反転を繰り返す複数段の傾斜通路となっている。これらの傾斜通路は、必要に応じて、１段のみとすることもできる。
【００４８】
そして、これらの各傾斜通路は、例えば上記第１，第２の伝熱プレート１１Ａ，１１Ｂの前後両面に相対関係を有して設けられた断面Ｖ字状の凹凸溝部１３で構成されるとともに、上記第１の伝熱プレート１１Ａ側の傾斜通路と第２の伝熱プレート１１Ｂ側の傾斜通路とを相互に連通させるように構成している。
【００４９】
このように構成したことにより、それぞれ第１の流体通路２２を構成する第１の伝熱プレート１１Ａ側の傾斜通路と第２の伝熱プレート１１Ｂ側の傾斜通路とが相互に交差状態で連通されることになり、上記第１の伝熱プレート１１Ａ側の傾斜通路あるいは第２の伝熱プレート１１Ｂ側の傾斜通路を流れる第１の流体Ｘは、下方に流下する過程において上記第２の伝熱プレート１１Ｂ側の傾斜通路あるいは第１の伝熱プレート１１Ａ側の傾斜通路に流れ込むことができるようになり、第１，第２の各伝熱プレート１１Ａ，１１Ｂの伝熱面全体が第１の流体Ｘによって均一に濡らされることになる。その結果、熱交換が行われない領域がなくなり、熱伝達性能が大幅に向上する。
【００５０】
ところで、上記第１，第２の伝熱プレート１１Ａ，１１Ｂは、例えば図１に示されるように、それぞれ全体として縦に長いステンレス製金属板をプレス成形して形成されており、その伝熱面外周側に設けられた重合接合用の鉤形に曲げたフレーム部１１ａ，１１ａ、同伝熱面中央部に上方から下方にジグザグに延び、上述した傾斜通路を形成する断面Ｖ字状の凹凸溝部１３、該凹凸溝部１３の両側左右に各々４個設けられた第２の流体Ｙを導入、導出するための分配ヘッダ接続口１４ａ，１４ａ・・、１４ｂ，１４ｂ・・、上記凹凸溝部１３の上部に設けられた第１の流体散布溝１５、上記凹凸溝部１３の下部に設けられた蒸気抜き口部１６等が、各々配設されている。
【００５１】
一方、上記第１の流体散布溝１５のフラットな底部には、例えば図４、図５に示すように、流体散布孔１５ａが開孔され、同流体散布孔１５ａと上記凹凸溝部１３の上部との間には、全体として略台形形状をなして、上方から下方に順次左右方向の幅が広くなる第１，第２，第３の凸部１７ａ，１７ｂ，１７ｃと第１，第２の凹部７ｅ，７ｆよりなる流体拡散部１７が設けられている。この流体拡散部１７の第１の凸部１７ａは、それよりも下方側の凸部１７ｂ，１７ｃよりも高さが高く構成されている。
【００５２】
そして、この流体拡散部１７は、上記第１の流体Ｘの散布孔１５ａよりも所定寸法（第１，第２の試作例に比べて、遥かに大きい寸法）Ｌ以上下方に位置し、かつ当該第１の流体Ｘの散布孔１５ａから滴下させる第１の流体Ｘが、上記第１，第２の伝熱プレート１１Ａ，１１Ｂのフラットな壁面１１ｃを伝わることなく、直接落下状態で衝突するように構成されている。なお、このようにした結果、広くなったフラットな壁面部１１ｃには、第１の流体Ｘの滴下を妨げない範囲で、左右両側に所定の間隔を置いて補強リブ１８，１８を設けて補強する。
【００５３】
したがって、上記第１の流体の散布孔１５ａから流出した第１の流体Ｘは、例えば図４に示すように、先ず第１，第２の伝熱プレート１１Ａ，１１Ｂのフラットな壁面１１ｃを全く伝わらずに、直接上記流体拡散部１７の最初の第１の凸部１７ａ上面に所定の重力加速度をもって衝突し、同衝突時の拡散エネルギーで、従来よりも遥かに大きく左右に広がる。
【００５４】
そして、該大きく広がった第１の流体Ｘが、その後、さらに同第１の凸部７ａを乗り超えて、同第１の凸部７ａと次の第２の凸部７ｂとの間に形成された凹部７ｅ内に流速を増して流れ落ち、均一に分散される。その後、さらに第２の凸部７ｂ部分で再び流速が落ちて停滞、滞留し、その量の増大により所定幅左右に拡散する。
【００５５】
その後、同第２の凸部７ｂを乗り超えて、同第２の凸部７ｂと次の第３の凸部７ｃとの間に形成された凹部７ｆ内に流速を増して流れ落ち、再び均一に分散される。そして、その後、さらに第３の凸部７ｃ部分で再び流速が落ちて停滞、滞留し、その量の増大により最終的に所定幅左右に拡散する。
【００５６】
したがって、最終的に第１，第２の伝熱プレート１１Ａ，１１Ｂに供給される第１の流体Ｘは、その凹凸溝部１３を有する主たる伝熱面の全体を均一に覆い、かつジグザグに流れる有効な液膜状の流れとなる。
【００５７】
その結果、第２の流体Ｙとの熱交換効率も一層大きく向上する。
【００５８】
以上の結果、従来のように、滴下流体の散布量を増やしたり、隙間形成のための別部材を設けることなく、伝熱面に均一で適度な厚さの液膜を形成することができるようになる。
【００５９】
したがって、構造が簡単で、製作も容易となり、低コストで、高性能のプレート式熱交換器を提供することができる。
【００６０】
（実施の形態２）
次に図６は、本願発明の実施の形態２に係るプレート式熱交換器の伝熱プレートの要部の構造と作用が示されている。
【００６１】
このプレート式熱交換器は、その伝熱プレート１１Ａ，１１Ｂ部の第１の流体Ｘの散布溝１５の底部面を、例えば図６に示すように、傾斜面とし、同傾斜面部分に第１の流体Ｘの散布孔１５ａを設けて、下方側流体拡散部１７の最も高い第１の凸部１７ａの上面に衝突させるようにしたことを特徴とするものである。
【００６２】
このような構成にすると、より確実に伝熱プレート１のフラットな壁面部１１ｃから離して、第１の凸部１７ａに衝突させることができる。
【００６３】
その他の構成と作用は、上記実施の形態１のものと同様である。
【００６４】
（実施の形態３）
次に図７は、本願発明の実施の形態３に係るプレート式熱交換器の伝熱プレートの要部の構造と作用が示されている。
【００６５】
このプレート式熱交換器は、上記実施の形態２のように、その伝熱プレート１１Ａ，１１Ｂ部の第１の流体Ｘの散布溝１５の底部面を、例えば図７に示すように、傾斜面としているが、他方同傾斜面部分に相互に隣接する相手側伝熱プレート１１Ａ，１１Ｂの第１の凸部１７ａ，１７ａ方向に向けて、それぞれ第１の流体Ｘの散布孔１５ａ，１５ａを開口し、同相手側の流体拡散部１７の最も高い第１の凸部１７ａ，１７ａの上面に対して各々第１の流体Ｘ，Ｘを衝突させるようにしたことを特徴とするものである。
【００６６】
このような構成にすると、より確実に伝熱プレート１のフラットな壁面部１１ｃから離して、より衝撃の大きい状態で、相手側第１の凸部１７ａ，１７ａに衝突させることができる。その結果、より拡散効果が高くなる。
【００６７】
その他の構成と作用は、上記実施の形態１のものと同様である。
【００６８】
（実施の形態４）
さらに、図８および図９は、本願発明の実施の形態４に係るプレート式熱交換器の構造が示されている。
【００６９】
上述の実施の形態１に係るプレート式熱交換器１０では、第１，第２の各伝熱プレート１１Ａ，１１Ａ・・・、１１Ｂ，１１Ｂ・・・の各々が、それぞれその外周縁に相互に重合して一体に接合されるフレーム部１１ａ，１１ａ・・・を有し、１次側第１、２次側第２の各流体通路２２，２３共に密閉型に形成されるものであるのに対し、この実施の形態のものでは、２次側第２の流体通路２３側は、同様に密閉通路に形成されるが、他方１次側第１の流体通路２２の方は、開放型のものに形成され、枠板２８を使用して前後両板２６，２７と共にケーシング内収納構造としたことを特徴とするものである。
【００７０】
もちろん、第１，第２の伝熱プレート１１Ａ，１１Ａ・・・、１１Ｂ，１１Ｂ・・・が外周にフレーム部１１ａ，１１ａを持たず、１次側第１の流体通路２２を開放した状態で重合される図示のような形状のものとなっていることを除いて、その基本的な構造および作用は、全て上述の実施の形態１のものと同様であり、もちろん、実施の形態２，３のような構成の採用も可能である。
【００７１】
（適用例）
以上の各実施の形態に係るプレート式熱交換器は、上記特性から、例えば（１）フロン圧縮式チラーシステムの蒸発器や、（２）液膜流下型ダイナミック氷蓄熱システムにおける過冷却水生成熱交換器、（３）吸収式冷凍装置の蒸発器、吸収器、その他これらに類するものに適している。
【図面の簡単な説明】
【図１】本願発明の実施の形態１に係るプレート式熱交換器の伝熱プレート面の構成を示す正面図である。
【図２】同プレート式熱交換器の伝熱プレート重合状態を示す縦断面図である。
【図３】同プレート式熱交換器の伝熱プレート重合状態を示す横断面図である。
【図４】同プレート式熱交換器の伝熱プレートの要部の構成と作用を示す拡大正面図である。
【図５】同図４の状態の側方から見た断面図である。
【図６】本願発明の実施の形態２に係るプレート式熱交換器の伝熱プレートの要部の構成と作用を示す拡大断面図である。
【図７】本願発明の実施の形態３に係るプレート式熱交換器の伝熱プレートの要部の構成と作用を示す拡大断面図である。
【図８】本願発明の実施の形態４に係るプレート式熱交換器の伝熱プレート面の構成を示す正面図である。
【図９】同プレート式熱交換器の伝熱プレート重合状態を示す横断面図である。
【図１０】本件出願の発明者等が検討した第１の試作例に係るプレート式熱交換器の伝熱プレート面の構成を示す正面図である。
【図１１】同プレート式熱交換器の伝熱プレート要部の構成を示す拡大正面図である。
【図１２】同プレート式熱交換器の伝熱プレート要部の構成を示す断面図である。
【図１３】本件出願の発明者等が検討した第２の試作例に係るプレート式熱交換器の伝熱プレート面の構成を示す正面図である。
【図１４】同プレート式熱交換器の伝熱プレート要部の構成を示す拡大正面図である。
【符号の説明】
１１Ａ，１１Ｂは、第１，第２の伝熱プレート、１３は凹凸溝部、１４ａ，１４ａ・・、１４ｂ，１４ｂ・・は、２次側第２の流体導入導出用の分配ヘッダ接続口、１５は、１次側第１の流体の散布溝、１５ａは、同第１の流体の散布孔、１７は、流体拡散部、１７ａ〜１７ｃは、第１〜第３の凸部、１７ｅ，１７ｆは、第１，第２の凹部、１８は、補強用リブである。[0001]
BACKGROUND OF THE INVENTION
[0002]
The present invention relates to a configuration of a plate heat exchanger.
[Prior art]
[0003]
For example, when a heat exchanger such as an evaporator is formed by a liquid film flow-down type plate heat exchanger, for example, a plurality of first liquid film flow-down heat transfer plates arranged side by side are arranged on the first side. The first fluid is allowed to flow in a liquid film state on one side heat transfer surface of each heat transfer plate, heat exchange with the second fluid on the other surface side, and evaporated. (For example, refer to Japanese Patent Laid-Open No. 2000-283661).
[0004]
Further, in this type of plate heat exchanger, in order to improve the wettability, diffusibility, and heat transfer characteristics of the heat transfer plate surface, concave and convex grooves are formed on the heat transfer surface (Japanese Patent Application Laid-Open No. Hei 10). -300371).
[0005]
In such a liquid film flow-down type plate heat exchanger, when the first fluid such as the refrigerant is uniformly wetted on the heat transfer surface, if the flow rate is very high or low, a separate member is attached and the gap There is a way to spread with. However, when the flow rate is increased, the liquid film becomes thicker and the performance is deteriorated, and the attachment of another member has a problem that it is difficult to manufacture due to a complicated structure and an increased number of parts.
[0006]
In view of this, the inventors of the present application have developed the first and second plate-type heat exchangers as shown in FIGS. 10 to 12, 13, and 14, for example. An attempt was made to solve the above problem.
[0007]
First, in FIGS. 10 to 12 as the first prototype, reference numeral 1 denotes the heat transfer plate. The heat transfer plate 1 is formed, for example, by press-molding a vertically long stainless metal plate as a whole, and has a bowl-shaped frame portion 1a for joint integration on the outer periphery of the heat transfer surface, and the center of the heat transfer surface. An uneven groove portion 3 having a V-shaped cross section extending zigzag downward from above to the main heat transfer surface portion on the side, and each distribution header connection port for introducing and derivatizing four second fluids on both sides of the uneven groove portion 3 4a, 4a,..., 4b, 4b,..., A first fluid spraying groove 5 above the concave and convex groove portion 3, and a steam vent 6 and the like below the concave and convex groove portion 3, respectively.
[0008]
On the other hand, a first fluid spray hole 5 a is opened at the flat bottom of the first fluid coolant spray groove 5, and between the spray hole 5 a and the top of the concave and convex groove portion 3, The first, second, and third protrusions 7a, 7b, and 7c are formed between the first, second, and third protrusions 7a, 7b, and 7c. A fluid diffusing portion 7 including recesses 7e and 7f is provided.
[0009]
And the 1st fluid which flowed out from the spray hole 5a of the said 1st fluid first propagates along the flat wall surface 1c of the heat-transfer plate 1, as shown, for example in FIG. 11 and FIG. The first convex portion 7a is reached, and then stays and stays at the first convex portion 7a, and the amount increases to increase the amount by a predetermined width.
[0010]
Thereafter, over the first convex portion 7a, the flow rate increases and flows down into the first concave portion 7e formed between the first convex portion 7a and the next second convex portion 7b, Evenly distributed. Furthermore, after that, the flow velocity drops again at the second convex portion 7b, stagnates and stays, and spreads to the right and left by a predetermined width by increasing the amount.
[0011]
After that, over the second convex portion 7b, the second concave portion 7f formed between the second convex portion 7b and the next third convex portion 7c flows down at an increased flow velocity, and is uniform. To be distributed. Furthermore, after that, the flow velocity again decreases and stays and stays at the third convex portion 7c, and diffuses to the right and left by a predetermined width by increasing the amount.
[0012]
In this way, after finally forming a liquid film-like flow that is widest in the left-right direction and has a uniform thickness, the main part of the heat exchange action on the heat transfer surface of the heat transfer plate 1 is formed. The first fluid is made to flow uniformly over the entire concave-convex groove portion 3 forming a heat-generating (evaporating) effect as efficiently as possible by improving the wettability.
[0013]
On the other hand, FIG. 13 and FIG. 14 show a second prototype example, which is intended to further improve the diffusion effect of the fluid diffusion part 7 in the left-right direction. The lengths in the left-right direction of the second and third convex portions 7a, 7b, and 7c and the first and second concave portions 7e and 7f are made longer, and other configurations are the first prototype example. Is exactly the same.
[Problems to be solved by the invention]
[0014]
As described above, the fluid diffusing action of the fluid diffusing unit 7 plays an extremely important role in flowing the first fluid uniformly over the entire heat transfer surface of the heat transfer plate 1 and improving wettability.
[0015]
Therefore, it is preferable that the fluid diffusion part 7 has a high diffusion performance that can diffuse the flow of the first fluid as widely as possible in the left-right direction.
[0016]
In that sense, the inventors of the present application initially have better diffusion performance in the second prototype (FIGS. 13 and 14) than in the first prototype (FIGS. 10 to 12). I thought.
[0017]
However, when the fluid is actually flowed, there is almost no difference in the diffusion performance between the two as shown in FIG. 11 and FIG. Even in each of the second and third convex portions 7a, 7b, and 7c, diffusion occurs in the concave and convex portions from the wall surface 1c to the first convex portion 7a and from the first convex portion 7a to the second convex portion 7b. Although the effect is seen, it has been found that the diffusion effect is hardly seen in the uneven portions after the second convex portion 7b.
[0018]
Therefore, the diffusion performance cannot be improved only by increasing the width of the uneven portion of the fluid diffusion portion 7 as in the second prototype.
[0019]
In view of such circumstances, as a result of conducting various studies and analysis, the cause described above is that the fluid dropped from the fluid spray hole once adheres to the flat wall surface and flows down, and the flow velocity is increased at that time. Since the first convex portion is reached in a state where the velocity energy has been reduced and the velocity energy has been reduced, the velocity component vector already spreading in the left-right direction has become smaller in the first convex portion itself. I found out that
[0020]
Based on such knowledge, the present invention ensures that the drop energy is ensured by dropping the fluid directly from the fluid spray hole to the first convex part of the fluid diffusion part in the fall state. It is an object of the present invention to provide a plate heat exchanger that is utilized to effectively improve diffusion performance.
[Means for Solving the Problems]
[0021]
In order to achieve the object, the present invention includes the following problem solving means.
[0022]
(1) First Problem Solving Means First, the first problem solving means of the present invention comprises a plurality of heat transfer plates 11A, 11B, 11A, 11B..., And each of the heat transfer plates 11A, 11B, 11A. , 11B,... On the main heat transfer surface of the heat transfer surface, and the distribution header connection ports 14a, 14a,. 14b... Are provided with a first fluid X spray groove 15 above the concave-convex groove 13 and adjacent to the plurality of heat transfer plates 11A, 11B, 11A, 11B. The first fluid X is dropped from one of the heat transfer plates 11A and 11B on one side surface from the fluid spray groove 15 to diffuse and flow in the form of a liquid film, and the second fluid Y and the heat flowing on the other side surface. Liquid film flow down type to be exchanged A formula heat exchanger, between the first fluid X in the spraying hole 15a and the heat transfer plate 11A provided at the bottom of the fluid dispenser groove 15, a main heat transfer surface of the 11B, the first A plurality of convex portions 17a, 17b, and 17c that gradually widen in the left-right direction from the upper side to the lower side that diffuse the fluid X over the entire heat transfer surface , and the concave portions 7e and 7f between the respective convex portions 17a, 17b, and 17c. and has a fluid diffusion portion 17 of the concave-convex structure formed, fluid spreading section 17, the than spraying hole 15a of the first fluid X located below at least a specific distance L, spraying holes of this first fluid X The first fluid X dropped from 15a does not travel through the wall surfaces 11c and 11c of the heat transfer plates 11A and 11B, but collides in a fall state with a predetermined gravitational acceleration, and spreads to the left and right with the energy at the time of the collision. Configured The
[0023]
Therefore, in such a configuration, the first fluid X dropped from the spray hole 15a of the first fluid X has a plurality of convex portions 17a, 17b, 17c and a plurality of concave portions 17e, 17b, 17c between the respective convex portions 17a, 17b, 17c collide with the first convex portion 17a of the fluid diffusing portion 17 of the concave-convex structure with a predetermined gravitational acceleration, and diffusion at the time of the collision The energy spreads to the left and right much larger than before.
[0024]
Then, the first fluid X that has spread greatly is further diffused and made uniform in the following uneven portions 17e, 17b, 17f, and 17c as in the prior art.
[0025]
Moreover, the fluid diffusion unit 17, the than spraying hole 15a of the first fluid X located below at least a specific distance L, a first fluid X that is dropped from the spray holes 15a of this first fluid X There without traveling through the wall 11c, 11c of the heat transfer plates 11A, 11B, since the colliding directly falling state at a predetermined acceleration of gravity, and is configured by Uni widely spread in left and right energy at the time of the collision, diffusion High effect.
[0026]
Thus, finally the heat transfer plates 11A, 11B, 11A, a first fluid X to be supplied to the main heat transfer surface large heat transfer area consisting of the grooved portions 13 of the 11B · · · is made of the same uneven surface It becomes an effective liquid film-like flow that more uniformly covers the entire main heat transfer surface having a large heat transfer area over time .
[0027]
As a result, significantly improved heat exchange efficiency between the second fluid Y.
[0028]
(2) Second problem solving means
Next , the second problem-solving means of the present invention is that the first fluid X is dropped from one of the heat transfer plates 11A and 11B on the side surface side of the fluid spraying groove 15 having a predetermined structure to flow down in a liquid film form. A liquid film flow type plate type heat exchanger that exchanges heat with the second fluid Y flowing on the other side surface, the first fluid X spray hole 15a of the fluid spray groove 15 and the heat transfer plate. Between the main heat transfer surfaces of 11A and 11B, there is a fluid diffusion portion 17 having an uneven structure that diffuses the first fluid X over the entire heat transfer surface, and the fluid diffusion portion 17 includes the first fluid X The first fluid X, which is located below the spraying hole 15a by a predetermined dimension L or more and dropped from the spraying hole 15a of the first fluid X, is transmitted through the wall surfaces 11c and 11c of the heat transfer plates 11A and 11B. It is configured to collide directly in the fall state without The first fluid X spray hole 15a of the fluid spray groove 15 is opposed to the bottom of the fluid spray grooves 15 and 15 of the heat transfer plates 11A and 11B adjacent to each other. It forms in the inclined surface to perform, and it is comprised so that it may drip in the discharge state toward the 1st convex part 17a, 17a surface of the fluid diffusion part 17, 17 of the other party heat-transfer plate 11A, 11B .
[0029]
Therefore, in such a configuration, the first fluid X dropped from the spray hole 15a of the first fluid X is the first convex portion 17a of the fluid diffusion portion 17 as in the case of the invention of claim 1 above. It collides with a predetermined gravitational acceleration and spreads to the left and right much larger than before with the diffusion energy at the time of the collision.
[0030]
Moreover, in the configuration of the present invention, in that case, the first fluid X discharged from the fluid spray hole 15a of the first fluid X at the bottom of the fluid spray groove 15 of each of the heat transfer plates 11A and 11B adjacent to each other. However, it collides with the first convex parts 17a and 17a of the fluid diffusion parts 17 and 17 facing each other with a predetermined gravitational acceleration so that the diffusion energy at the time of the collision spreads to the left and right much larger than before. It has become.
[0031]
Then, the first fluid X that spreads particularly greatly is further diffused and uniformed in the following uneven portions 17b, 17c, 17e, and 17f as in the prior art.
[0032]
Accordingly, the first fluid X that is finally supplied to the main heat transfer surfaces of the heat transfer plates 11A and 11B becomes a more effective liquid film flow that covers the entire main heat transfer surfaces more uniformly. .
[0033]
As a result, the efficiency of heat exchange with the second fluid Y is further improved.
[0034]
(3) Third Problem Solving Means The third problem solving means of the present invention is that the spray hole 15a of the fluid spray groove 15 in the configuration of the first problem solver is formed on the flat surface of the bottom of the fluid spray groove 15. They are formed and dropped downward in the vertical direction.
[0035]
Therefore, in such a configuration, the fluid X dripping vertically downward from the fluid spray hole 15a formed in the flat surface of the bottom of the fluid spray groove 15 is predetermined on the first convex portion 17a of the fluid diffusion portion 17. It collides with gravitational acceleration and spreads to the left and right much larger than before with the diffusion energy at the time of the collision.
[0036]
Then, the first fluid X that has spread greatly is further diffused and made uniform in the following uneven portions 17b, 17c, 17e, and 17f as in the conventional case.
[0037]
(4) Fourth Problem Solving Means According to a fourth problem solving means of the present invention, the spray hole 15a of the fluid spray groove 15 in the configuration of the first problem solver is formed on the inclined surface of the bottom of the fluid spray groove 15. They are formed and dropped downward in the vertical direction.
[0038]
Therefore, in such a configuration, the fluid spraying hole 15a formed on the inclined surface of the bottom of the fluid spraying groove 15 can be easily dropped downward in the vertical direction without approaching the wall surface of the heat transfer plates 11A and 11B. The dripping fluid collides with the first convex portion 17a of the fluid diffusion portion 17 with a predetermined gravitational acceleration, and spreads to the left and right much more than before with the diffusion energy at the time of the collision.
[0039]
Then, the first fluid X that has spread greatly is further diffused and made uniform in the following uneven portions 17b, 17c, 17e, and 17f as in the conventional case.
[0040]
(5) Fifth Problem Solving Means A fifth problem solving means of the present invention is the first convex portion 17a of the fluid diffusion portion 17 in the configuration of the first, second, third or fourth problem solving means. Is configured to be higher than the convex portions 17b and 17c on the lower side.
[0041]
Therefore, in such a configuration, the first fluid X dripping from the first fluid spray hole 15a surely collides with the first convex portion 17a, and more effectively performs the above-described action.
【The invention's effect】
[0042]
As a result, according to the present invention, it is possible to form a liquid film having a uniform and appropriate thickness on the heat transfer surface without increasing the amount of sprayed dropped fluid or providing another member for forming a gap.
[0043]
Therefore, the structure is simple, the manufacture is easy, and a high-performance plate heat exchanger can be provided at low cost.
DETAILED DESCRIPTION OF THE INVENTION
[0044]
Hereinafter, several embodiments of the present invention will be described with reference to the accompanying drawings.
[0045]
(Embodiment 1)
First, FIG. 1 to FIG. 5 show the structure and operation of the entire plate-type heat exchanger according to the embodiment of the present invention and the main part.
[0046]
As shown in FIGS. 1 to 3, for example, the plate heat exchanger 10 includes first and second heat transfer plates 11A, 11A, and 11B, 11B, between front and rear plates 26, 27. The first fluid passage 22 and the second fluid passage 23 are sequentially arranged adjacent to each other alternately, and the first fluid X flowing in the first fluid passage 22 downward from above The second fluid Y (not shown) flowing through the second fluid passage 23 is configured to exchange heat.
[0047]
The first fluid passage 22 is formed in each of the first and second heat transfer plates 11A and 11B and is inclined in a direction opposite to each other at a predetermined inclination angle with respect to the vertical direction. It is a multi-stage inclined passage where the inclination direction repeats reversal. These inclined passages may have only one stage as required.
[0048]
Each of these inclined passages is composed of, for example, an uneven groove portion 13 having a V-shaped cross section provided in a relative relationship on both front and rear surfaces of the first and second heat transfer plates 11A and 11B. The inclined passage on the first heat transfer plate 11A side and the inclined passage on the second heat transfer plate 11B side are configured to communicate with each other.
[0049]
With this configuration, the inclined passage on the first heat transfer plate 11A side and the inclined passage on the second heat transfer plate 11B side that respectively constitute the first fluid passage 22 are communicated with each other in an intersecting state. Thus, the first fluid X flowing through the inclined passage on the first heat transfer plate 11A side or the inclined passage on the second heat transfer plate 11B side flows down the second heat transfer. It becomes possible to flow into the inclined passage on the plate 11B side or the inclined passage on the first heat transfer plate 11A side, and the entire heat transfer surface of each of the first and second heat transfer plates 11A and 11B is the first fluid. X will be uniformly wetted. As a result, there is no region where heat exchange is not performed, and the heat transfer performance is greatly improved.
[0050]
By the way, the first and second heat transfer plates 11A and 11B are each formed by press-molding a vertically long stainless steel metal plate as a whole, as shown in FIG. Frame portions 11a and 11a bent in a bowl shape for superposition joining provided on the outer peripheral side, and an uneven groove portion having a V-shaped cross section that extends in a zigzag from the top to the bottom at the center of the heat transfer surface and forms the above-described inclined passage 13. Distribution header connection ports 14a, 14a,..., 14b, 14b,... For introducing and deriving four second fluids Y provided on each of the left and right sides of the concave / convex groove 13 and the upper portion of the concave / convex groove 13 A first fluid spraying groove 15 provided in the upper part, a steam vent part 16 provided in the lower part of the concave-convex groove part 13 and the like are respectively provided.
[0051]
On the other hand, at the flat bottom of the first fluid spraying groove 15, for example, as shown in FIGS. 4 and 5, a fluid spraying hole 15 a is opened, and the fluid spraying hole 15 a and the top of the concave and convex groove 13 are formed. Between the first, second and third convex portions 17a, 17b, 17c and the first and second concave portions, which form a substantially trapezoidal shape as a whole and gradually increase in width in the left-right direction from top to bottom. A fluid diffusing portion 17 composed of 7e and 7f is provided. The first convex portion 17a of the fluid diffusion portion 17 is configured to have a height higher than the convex portions 17b and 17c on the lower side.
[0052]
The fluid diffusion portion 17 is located below a predetermined dimension L (a dimension that is much larger than the first and second prototypes) L than the first fluid X spray hole 15a, and The first fluid X dripped from the spray hole 15a of the first fluid X does not travel along the flat wall surface 11c of the first and second heat transfer plates 11A and 11B, and directly collides in the fall state. It is configured. As a result of the above, the wide flat wall surface portion 11c is provided with reinforcing ribs 18 and 18 at predetermined intervals on both the left and right sides within a range that does not prevent the first fluid X from dropping. To do.
[0053]
Therefore, the first fluid X flowing out of the first fluid spray hole 15a is first completely transmitted through the flat wall surface 11c of the first and second heat transfer plates 11A and 11B, for example, as shown in FIG. Instead, it directly collides with the upper surface of the first first convex portion 17a of the fluid diffusion portion 17 with a predetermined gravitational acceleration, and spreads to the left and right much more than before with the diffusion energy at the time of the collision.
[0054]
Then, the first fluid X that has spread greatly is further formed over the first convex portion 7a and between the first convex portion 7a and the next second convex portion 7b. The flow rate is increased in the recessed portion 7e to flow down and dispersed uniformly. Thereafter, the flow velocity again decreases and stays and stays at the second convex portion 7b, and diffuses right and left by a predetermined width by increasing the amount.
[0055]
After that, over the second convex portion 7b, the flow rate increases into the concave portion 7f formed between the second convex portion 7b and the next third convex portion 7c, and then flows down and becomes uniform again. Distributed. After that, the flow rate drops again at the third convex portion 7c, stagnates and stays, and finally spreads to the left and right of the predetermined width by increasing the amount.
[0056]
Therefore, the first fluid X that is finally supplied to the first and second heat transfer plates 11A and 11B uniformly covers the entire main heat transfer surface having the concave and convex groove portions 13 and flows in a zigzag manner. It becomes a liquid-like flow.
[0057]
As a result, the efficiency of heat exchange with the second fluid Y is further greatly improved.
[0058]
As a result, a liquid film having a uniform and appropriate thickness can be formed on the heat transfer surface without increasing the amount of dripping fluid applied or providing a separate member for forming a gap as in the prior art. become.
[0059]
Therefore, the structure is simple, the manufacture is easy, and a high-performance plate heat exchanger can be provided at low cost.
[0060]
(Embodiment 2)
Next, FIG. 6 shows the structure and operation of the main part of the heat transfer plate of the plate heat exchanger according to Embodiment 2 of the present invention.
[0061]
In this plate heat exchanger, the bottom surface of the first fluid X spray groove 15 of the heat transfer plates 11A and 11B is an inclined surface as shown in FIG. The fluid X spray holes 15 a are provided so as to collide with the upper surface of the highest first convex portion 17 a of the lower fluid diffusion portion 17.
[0062]
With such a configuration, the heat transfer plate 1 can be more reliably separated from the flat wall surface portion 11c and allowed to collide with the first convex portion 17a.
[0063]
Other configurations and operations are the same as those of the first embodiment.
[0064]
(Embodiment 3)
Next, FIG. 7 shows the structure and operation of the main part of the heat transfer plate of the plate heat exchanger according to Embodiment 3 of the present invention.
[0065]
As shown in the second embodiment, the plate heat exchanger has a bottom surface of the spray groove 15 of the first fluid X in the heat transfer plates 11A and 11B, as shown in FIG. However, the first fluid X spray holes 15a and 15a are opened in the direction of the first convex portions 17a and 17a of the mating heat transfer plates 11A and 11B adjacent to each other on the other inclined surface portion, respectively. In addition, the first fluids X and X are caused to collide with the upper surfaces of the highest first convex portions 17a and 17a of the fluid diffusion portion 17 on the counterpart side, respectively.
[0066]
With such a configuration, it is possible to more reliably move away from the flat wall surface portion 11c of the heat transfer plate 1 and collide with the counterpart first convex portions 17a and 17a in a state where the impact is greater. As a result, the diffusion effect becomes higher.
[0067]
Other configurations and operations are the same as those of the first embodiment.
[0068]
(Embodiment 4)
8 and 9 show the structure of a plate heat exchanger according to Embodiment 4 of the present invention.
[0069]
In the plate heat exchanger 10 according to the first embodiment described above, the first and second heat transfer plates 11A, 11A,..., 11B, 11B. Although it has frame portions 11a, 11a,... Which are integrally joined together, the primary side first, second side second fluid passages 22, 23 are both formed in a sealed type. On the other hand, in this embodiment, the secondary side second fluid passage 23 side is similarly formed as a sealed passage, while the primary side first fluid passage 22 is an open type. In this case, the frame plate 28 is used and the front and rear plates 26 and 27 together with the housing housing structure are provided.
[0070]
Of course, the first and second heat transfer plates 11A, 11A,..., 11B, 11B,... Do not have the frame portions 11a, 11a on the outer periphery and the primary side first fluid passage 22 is opened. Except for the shape shown in the figure to be polymerized, the basic structure and operation are all the same as those of the first embodiment described above, and of course, the second and third embodiments. It is also possible to adopt a configuration such as
[0071]
(Application example)
From the above characteristics, the plate heat exchanger according to each of the above embodiments has, for example, (1) an evaporator of a chlorofluorocarbon compression chiller system and (2) heat generated by supercooled water in a liquid film flow-down dynamic ice heat storage system. It is suitable for exchangers, (3) evaporators and absorbers of absorption refrigeration equipment, and the like.
[Brief description of the drawings]
FIG. 1 is a front view showing a configuration of a heat transfer plate surface of a plate heat exchanger according to Embodiment 1 of the present invention.
FIG. 2 is a longitudinal sectional view showing a heat transfer plate superposition state of the plate heat exchanger.
FIG. 3 is a cross-sectional view showing a heat transfer plate polymerization state of the plate heat exchanger.
FIG. 4 is an enlarged front view showing the configuration and operation of the main part of the heat transfer plate of the plate heat exchanger.
5 is a cross-sectional view seen from the side of the state shown in FIG.
FIG. 6 is an enlarged cross-sectional view showing the configuration and operation of the main part of the heat transfer plate of the plate heat exchanger according to Embodiment 2 of the present invention.
FIG. 7 is an enlarged cross-sectional view showing the configuration and operation of the main part of a heat transfer plate of a plate heat exchanger according to Embodiment 3 of the present invention.
FIG. 8 is a front view showing a configuration of a heat transfer plate surface of a plate heat exchanger according to Embodiment 4 of the present invention.
FIG. 9 is a cross-sectional view showing a heat transfer plate polymerization state of the plate heat exchanger.
FIG. 10 is a front view showing a configuration of a heat transfer plate surface of a plate heat exchanger according to a first prototype studied by the inventors of the present application.
FIG. 11 is an enlarged front view showing the configuration of the main part of the heat transfer plate of the plate heat exchanger.
FIG. 12 is a cross-sectional view showing the configuration of the main part of the heat transfer plate of the plate heat exchanger.
FIG. 13 is a front view showing a configuration of a heat transfer plate surface of a plate heat exchanger according to a second prototype studied by the inventors of the present application.
FIG. 14 is an enlarged front view showing the configuration of the main part of the heat transfer plate of the plate heat exchanger.
[Explanation of symbols]
11A and 11B are first and second heat transfer plates, 13 is an uneven groove portion, 14a, 14a,..., 14b, 14b,. Is a primary side first fluid spray groove, 15a is the first fluid spray hole, 17 is a fluid diffusion portion, 17a to 17c are first to third convex portions, and 17e and 17f are The first and second recesses 18 are reinforcing ribs.

Claims

It consists of a plurality of heat transfer plates (11A), (11B), (11A), (11B)... And each of these heat transfer plates (11A), (11B), (11A), (11B). An uneven groove portion (13) on the main heat transfer surface portion of the heat transfer surface, and distribution header connection ports (14a), (14a) for introducing and derivatizing the second fluid (Y) on both sides of the uneven groove portion (13). .., (14b), (14b)... Are provided with a spray groove (15) for the first fluid (X) above the concave and convex groove portion (13), and the plurality of heat transfer plates. (11A), (11B), (11A), (11B)... The first fluid (X) is placed on one side of the heat transfer plates (11A) and (11B) adjacent to each other. Dropping from the fluid spreading groove (15) to diffuse and flow down in the form of a liquid film, the above-mentioned first flowing on the other side Fluid (Y) with a liquid film falling type plate heat exchanger for heat exchange, the first spraying hole of the fluid (X) provided at the bottom of the fluid dispenser groove (15) and (15a) A plurality of first and second fluids (X) are diffused over the entire heat transfer surface between the heat transfer plates (11A) and (11B), and the width in the left-right direction gradually increases from the top to the bottom. Diffusion structure fluid diffusion portion comprising convex portions (17a), (17b), (17c) and concave portions (7e), (7f) between the convex portions (17a), (17b), (17c) and has a (17), the fluid diffusing portion (17) is positioned below spraying holes (15a) a predetermined distance (L) more than the first fluid (X), of this first fluid ( X) The first fluid (X) dropped from the spray hole (15a) of the heat transfer plate (11A), ( Wall of 1B) (11c), (11c ) without traveling through, collides directly falling state at a predetermined acceleration of gravity, plate type, characterized by being constituted by Uni spreads to the left and right energy during the collision Heat exchanger.

The first fluid (X) is dropped from one of the heat transfer plates (11A) and (11B) from the fluid spray groove (15) having a predetermined structure to be diffused and flowed down in the form of a liquid film. A liquid film flow type plate heat exchanger for exchanging heat with the second fluid (Y) flowing through the first fluid (X) in the fluid spray groove (15) and the above Between the main heat transfer surfaces of the heat transfer plates (11A) and (11B), there is an uneven structure fluid diffusion portion (17) for diffusing the first fluid (X) over the entire heat transfer surface, and the fluid The diffusion part (17) is located below the spray hole (15a) of the first fluid (X) by a predetermined dimension L or more and is dropped from the spray hole (15a) of the first fluid (X). The first fluid (X) is applied to the wall surfaces (11c) and (11c) of the heat transfer plates (11A) and (11B). It is a plate type heat exchanger configured to collide in a direct fall state without breaking, and the spray holes (15a) of the first fluid (X) of the fluid spray groove (15) are mutually connected. The adjacent heat transfer plates (11A) and (11B) are formed on the inclined surfaces facing each other in the fluid distribution grooves (15) and (15), and are opposed to each other. The plate-type heat exchanger is characterized by being dropped in a discharged state toward the first convex portions (17a) and (17a) of the fluid diffusion portions (17) and (17).

The spray hole (15a) of the fluid spray groove (15) is formed on a flat surface at the bottom of the fluid spray groove (15) and is dropped downward in the vertical direction. Plate heat exchanger.

The spray hole (15a) of the fluid spray groove (15) is formed on the inclined surface of the bottom of the fluid spray groove (15) and drops downward in the vertical direction. Plate heat exchanger.

The first convex part (17a) of the fluid diffusion part (17) is configured to have a height higher than the convex parts (17b), (17c) on the lower side thereof. The plate heat exchanger according to 2, 3 or 4.