JP3445727B2 - Compressed air dehumidifier - Google Patents
Compressed air dehumidifierInfo
- Publication number
- JP3445727B2 JP3445727B2 JP22302597A JP22302597A JP3445727B2 JP 3445727 B2 JP3445727 B2 JP 3445727B2 JP 22302597 A JP22302597 A JP 22302597A JP 22302597 A JP22302597 A JP 22302597A JP 3445727 B2 JP3445727 B2 JP 3445727B2
- Authority
- JP
- Japan
- Prior art keywords
- flow path
- partition
- compressed air
- heat transfer
- pressure vessel
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Compressor (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Drying Of Gases (AREA)
Description
【発明の詳細な説明】
【0001】
【発明の属する技術分野】本発明は、圧縮空気除湿装置
に関するものであり、特に、シェルアンドチューブ型熱
交換器を備えた圧縮空気除湿装置の改良に関するもので
ある。
【0002】
【従来の技術】この種の圧縮空気除湿装置としては、例
えば、図5に示すように、円筒形圧力容器121の内部
に、該圧力容器の左右側面板121a,bの夫々に対面
するように、左右仕切板122a,bを設けることによ
り、側面板と仕切板との間に接続流路123bと出口流
路123aとを形成し、左右両仕切板に挟まれた空間を
両仕切板間を連結する隔壁124によって仕切ることに
より予冷流路125と除湿流路126とを画成し、該予
冷流路を貫通して接続流路123bと出口流路123a
とを連通する複数の伝熱パイプ120、・・・を設ける
と共に、除湿流路には、冷凍機による空気冷却器130
を内蔵せしめ、予冷流路には圧縮空気の導入口127と
除湿流路126との連通口126aを設けると共に、除
湿流路には、接続流路123bへの出口開口129を設
けた圧縮空気除湿装置が知られている。
【0003】これは、空気圧縮機の吐出側流路に接続す
る導入口127から、圧力容器内に入った高温の圧縮空
気が、予冷流路125において、冷却除湿後の温度低下
した圧縮空気と熱交換して予冷されてから、除湿流路に
入り、そこで冷却除湿され、次いで、伝熱パイプ12
0、120、・・・中を通過する際に、高温圧縮空気に
よって再熱されて、相対湿度を下げて、乾燥圧縮空気と
して供給口128から、空気機器等へ供給される。14
1、142は、ドレン排出口であり、131は、冷凍機
の冷媒蒸発管である。(実公昭58−12041号参
照)。
【0004】このような従来の多管式熱交換器を予冷流
路125として用いた圧縮空気除湿装置は、予冷効果を
十分に発揮させるために、予冷流路内に多数のバッフル
プレート135、135、・・・を、伝熱パイプ群12
0、・・・が貫通するように設けて、バッフルプレート
によって、伝熱パイプ内を流れる空気流の方向に対し
て、上下方向若しくは左右方向に蛇行する蛇行流路を形
成し、空気圧縮機から導入口を通して予冷流路内に流入
した空気は、伝熱パイプ内の気流方向と直交する方向に
蛇行しつつ熱交換するタイプのものが多い。
【0005】一般に、このタイプの圧縮空気除湿装置を
組み立てる場合は、例えば、先ず、隔壁124中に空気
冷却器130を収納すると共に、その外側に予冷流路と
なるべき伝熱パイプ120とバッフルプレート135と
の組み合わせから成る熱交換器を組み立ててから、これ
らを円筒状胴部中に収納して固定し、次いで、鏡板とな
る左右側面板121a,bを固着することにより、組み
立てが終了する。従って、多数の伝熱パイプが直交状態
で貫通するバッフルプレート群135、・・・を、円筒
状の胴部に収納するには、該胴部内面(圧力容器内面)
とバッフルプレートの端縁との間に、予め若干の間隙が
生じるように、バッフルプレートの寸法と形状を設定し
ておかない限り、円筒状胴部内への収納が困難になる。
【0006】しかしながら、バッフルプレートによる流
路抵抗は、かなり大きくなるため、圧力損失を防止する
見地からも改善の必要性が高いが、更に、予冷流路内に
導入された圧縮空気は、バッフルプレートが作る蛇行流
路を通らないで、圧力容器内壁とバッフルプレート端縁
との間に出来た前記透き間を通って、隣の流路へ短絡し
て流れてしまう気流が存在する。この熱交換にほとんど
寄与しない短絡気流量は、バッフルプレートによって流
路抵抗が増すほど増大し、熱交換効率を低下させる原因
になっている。
【0007】又、前述の従来装置は、多数のバッフルプ
レート135、・・・を、多数の伝熱パイプ120、・
・・が貫通する構成であるため、構成が複雑になると共
に、加工や組み立てに、手作業による熟練した技術と、
多くの時間とを必要とし、装置の製作コストを高くする
原因になっている。このような点を回避するために、予
冷流路のバッフルプレートの数を大幅に少なくしたり、
或いは、皆無にした構成の装置もあるが、伝熱パイプ1
20と除湿流路126とは、圧力容器121の一側に設
けた接続流路を介して反転する構成であるため、伝熱パ
イプ中の気流の方向と除湿流路の気流の方向とは反対に
なっており、従って、熱交換効率を一定限度以上に保持
する必要上、予冷流路内の気流と伝熱パイプ内の気流と
を向流状態にしようとすれば、圧縮空気の導入口127
の取付位置が、供給口に極端に近接した位置に限定され
て、装置の自由度が制限されてしまう不都合があった。
【0008】
【発明が解決しようとする課題】本発明の第1の目的
は、予冷流路における圧力損失が少なくてすみ、しか
も、冷却除湿後の圧縮空気を効率よく再加熱することが
でき、さらに製作が容易で、予冷流路に気密性の高い蛇
行流路を持ち、低コストで高性能な圧縮空気除湿装置を
提供することにある。
【0009】
【課題を解決するための手段】上記目的を達成すべく請
求項1記載の圧縮空気除湿装置は、圧力容器内に、当該
圧力容器の左右側面板の夫々に対面するように左右仕切
板を設けることにより、前記側面板と仕切板との間に接
続流路と出口流路とを形成し、左右両仕切板に挟まれた
空間を両仕切板間を連結する隔壁によって仕切ることに
より予冷流路と除湿流路とを画成し、当該予冷流路を貫
通して前記接続流路と前記出口流路とを連通する複数の
伝熱パイプを設けると共に、前記除湿流路には空気冷却
器を内蔵せしめ、前記予冷流路には圧縮空気の導入口と
前記除湿流路との連通口を設けると共に、前記除湿流路
には前記接続流路への出口開口を設けた圧縮空気除湿装
置において、複数の前記伝熱パイプからそれぞれ成る複
数のグループに前記複数の伝熱パイプを分けて、前記予
冷流路に前記伝熱パイプの伸長方向と並行に設けた弾性
を有する邪魔板によって前記グループの夫々を当該邪魔
板間に挟む状態で分画し、当該夫々の邪魔板の左右何れ
か一端付近と前記左右仕切板の一方との間には反転開口
が設けられると共に、当該各邪魔板における前記隔壁側
(若しくは前記圧力容器内面側)の縁辺が固定端縁とし
て当該隔壁(若しくは当該圧力容器内面)に固着され、
かつ当該固定端縁に対向する当該圧力容器内面側(若し
くは当該隔壁側)における他の縁辺が自由端縁として当
該圧力容器内面(若しくは当該隔壁)に弾性復帰力によ
って圧接されることによって前記導入口から前記連通口
に至る一連の圧縮空気蛇行流路が画成され、当該各邪魔
板は、その両端が前記左右仕切板に固着されて当該邪魔
板に沿って伸長するように設けられた1以上の支持棒に
よって弾性復帰方向と反対の側から支持されていること
を特徴とする。
【0010】上記圧縮空気除湿装置は、予冷流路内に流
入した高温圧縮空気を案内する邪魔板は、複数のグルー
プに分けられた伝熱パイプを、そのグループ毎に、両側
から挟む状態(換言すれば、伝熱パイプのグループを、
圧力容器の内面と隔壁と一対の邪魔板とによって囲む状
態)で分画する構成を備えている。従来の伝熱パイプ
は、多数の邪魔板(バッフルプレート)を貫通する状態
で設けられていたのに対して、本願における邪魔板の場
合は、伝熱パイプが邪魔板を貫通することがなく、伝熱
パイプの伸長する方向に沿って、邪魔板も並行に伸長し
て設けられている点に特徴がある。
【0011】また、これらの邪魔板は、ステンレススチ
ール板や弾性を高めた鋼板などの弾性板から構成し、一
端縁を隔壁側に固着して固定端縁とし、この固定端縁と
圧力容器内面との最短距離よりも、邪魔板の縦方向の幅
(固定端縁から自由端縁に至る長さ)を長く設定し、圧
力容器内に組み込むとき、弾性限度内で邪魔板を撓めた
状態で圧力容器内に送入する。かくして、これらの邪魔
板の自由端縁は、邪魔板の弾性復帰力(スプリングバッ
ク)によって圧力容器内壁に圧接し、蛇行流路を構成す
ることができる。反転開口は、邪魔板の左右何れかの端
縁を、仕切板との間に若干の距離を設けた状態で臨まし
めるか、若しくは、邪魔板の左右端縁付近に交互に開口
を穿設すればよい。
【0012】このようにして形成される圧縮空気蛇行流
路を流れる高温圧縮空気は、伝熱パイプの方向とほぼ並
行して流れ、若し、隣り合う蛇行流路の一方の高温圧縮
空気が、伝熱パイプ内を流れる除湿後の圧縮空気と向流
状態であれば、隣り合う他方の蛇行流路の高温圧縮空気
は、並流状態となる。故に、向流状態となる蛇行流路に
は、多数の伝熱パイプを収容し、並流となる蛇行流路に
は、邪魔板等を固定するための必要最小限の数か、或い
は、伝熱パイプを皆無にして、単に、気流方向を転換さ
せて向流状態を作るための反転流路とすることにより、
熱交換効率を高めることができる。
【0013】また、邪魔板が伝熱パイプの伸長方向に沿
って設けられているので、構成が簡素となり、製作や組
み立てに熟練を必要とせず製造コストと製造に要する時
間とが少なくて済む。また、邪魔板は、主として、導入
口の選択の自由度と伝熱パイプ内の気流と向流状態が得
られれば、その主たる目的を達成するので、邪魔板の数
は、従来のバッフルプレート(135)の数に比して、
圧倒的に少なくて済み、従って圧力損失も極めて少な
い。更に、邪魔板の弾性復帰力により邪魔板と圧力容器
内壁面の透き間がほぼ無くなるので、気流が蛇行流路間
を短絡して流れることがなく、熱交換効率が向上する。
【0014】また、邪魔板の自由端縁は、固定端縁によ
って、その方向性を規定されている。しかしながら、邪
魔板の圧力容器内面への圧接力は、夫々の邪魔板におい
て、必ずしも一定ではない。従って、その位置がずれる
可能性がある。この点、その両端が左右仕切板に固着さ
れて邪魔板に沿って伸長するように設けられた1以上の
支持棒によって邪魔板を支持したことにより、その位置
ずれを防止することができる。これにより、邪魔板が、
圧縮空気導入初期にかかる圧力に負けて反転するなどの
変位を防止することもできる。この場合、支持棒は、伝
熱パイプであってもよい。支持棒は、勿論、邪魔板の両
側に設けてもよい。
【0015】
【発明の実施の形態】図1〜3は、本発明に係る圧縮空
気除湿装置の一実施態様を示すものである。円筒形圧力
容器1内に、その左右側面板をなす鏡板1a、1bの夫
々に対面するように、左右仕切板2a,bを設けること
により、鏡板1a,bと左右仕切板2a,bとの間に出
口流路3aと接続流路3bとを形成し、左右両仕切板2
a,bに挟まれた空間を、両仕切板2a,b間を連結す
る円筒状隔壁4によって2室に仕切ることにより、空気
圧縮機から吐出された高温圧縮空気の予冷流路5と除湿
流路6とが画成されている。圧力容器1は耐圧性の高い
円筒形であることが望ましいが、隔壁4は、耐圧性を要
せず、圧力容器1の内面と左右仕切板とに囲まれた空間
を2分すれば足りるので、いかなる形状でもよい。
【0016】予冷流路5中を貫通して、多数の伝熱パイ
プ、7、7、・・・が圧力容器1の中心軸と平行に設け
られており、夫々の伝熱パイプの両端は、左右仕切板が
予冷流路5に対面する面を、気密に貫通して、夫々、接
続流路3bと出口流路3aとに開口することにより、接
続流路3bと出口流路3aとは、伝熱パイプ群7、・・
・を介して連通している。除湿流路6には、圧力容器1
の外部に設けられた冷凍機(図示せず)の冷媒蒸発管1
1とフィンプレート12とから成る空気冷却器10が収
納されている。12a、12a、・・・は、気流を蛇行
させるためのバッフルプレートである。予冷流路5に
は、圧縮空気の導入口9が設けられると共に、出口流路
3aには、除湿乾燥された圧縮空気の供給口8が、開口
している。
【0017】このような構成は、実質的に、従来の装置
と変わりはない。本願装置の特徴は、以下の構造にあ
る。予冷流路5中を気密に貫通する伝熱パイプ群7、
7、・・・は、横断面方向から見た場合に、図2に示す
ように、耐圧容器1の垂直な直径を含む仮想垂直面の両
側に、左右対称に、2グループづつ、合計4個のグルー
プG1〜G4になるように、夫々のグループ毎にパイプ
間の相互距離を近接させて設けてあり、これらのグルー
プG1〜G4の夫々を両側から挟むように、邪魔板P1
〜P8が設けられている。
【0018】夫々の邪魔板P1〜P8は、弾性鋼板やス
テンレススチール製薄板のような弾性を備えた耐熱性板
体で作られており、一側の縁辺が隔壁4(若しくは圧力
容器内面)の外面に固着されて固定端縁となっており、
この固定端縁に対向する他の縁辺は自由端縁として、圧
力容器1の内面(若しくは隔壁の外面)に、邪魔板素材
の持つ復帰弾性力で圧接し、隔壁4と圧力容器内面との
間を遮断している。例えば、邪魔板P1及びP5は、図
2〜3に示すように、長方形の板体50を、横断面が略
く字形をなすように屈曲(50a)させておき、その固
定端縁51を更に略L状に屈曲させて溶接代51aを作
り、これを隔壁4の外面4aに溶接して固着すると、板
体50は、溶接代51aのなす角度によって、所定の方
向に立ち上がって固定される。
【0019】圧力容器内に挿入すべき予冷流路と除湿流
路とが完成したら、組み立てに当たっては、板体のもつ
弾性に抗して、矢印Y方向に向けて、板体50をく字形
に深く曲げた状態で圧力容器1内に挿入する。自由端縁
52は、板体の持つ弾性の復帰力によって、圧力容器1
の内壁面1cに圧接する。53、53、・・・は、邪魔
板P1、・・・等の位置のずれを防止して、所定の位置
に保持するための支持棒で、その両端は、左右仕切板2
a,b間に固定されている。邪魔板の固定端縁の隔壁4
への固定方法は、溶接に限らず、他の一般的な方法が採
用出来る。
【0020】他の邪魔板の固定構造もほぼ同様である。
この邪魔板固定構造は、耐圧性を要する容器1の内壁
に、一切の加工を必要とせず(例えば、部分的に溶接等
の熱処理が加わることがなく)、又、予め、邪魔板を隔
壁に固着した後に、圧力容器内の胴部に収納して組み立
てても、邪魔板と圧力容器内面1cとの間に透き間が生
じない。邪魔板P1〜P8の左右の端縁は、邪魔板の配
置を図示するため図2におけるBーB断面を模式的に展
開した図4に示すように、邪魔板の左右の側縁の一方
は、左右の仕切板の何れか一方に当接しており、他方の
側縁は、気流が反転するための反転開口15、15、・
・・となっている。反転開口は、左右仕切板間に当接す
るように設けた邪魔板の一端付近に、開口部を穿設した
ものでもよい。反転開口の面積は、反転開口で気流が絞
られることがないように、反転開口における気流の速度
は、気流反転の前後の流速の中間になるように、開口面
積が定められている。
【0021】図4において、導入口9が開口する中央部
の流路(邪魔板P1とP5とに挟まれた流路)は、伝熱
パイプ7、・・・が無い反転流路21となり、邪魔板P
1とP5とは、共に右仕切板2a側に反転開口15、1
5を有することにより、導入口9からの圧縮空気流は、
この両反転開口から、反転流路21の両側にある熱交換
流路22、23に分流して、伝熱パイプ内の気流方向と
向流状態をなすべく、右仕切板2a側から左仕切板2b
側へと流れ、更に、左仕切板側において反転して、伝熱
パイプが存在しない反転流路24、25を通って、再
び、伝熱パイプ内の気流と向流状態で、熱交換流路2
6、27を流れる。
【0022】このようにして、反転流路21の両側に形
成された圧縮空気の蛇行流路を通過した気流は、隔壁4
の下部に形成された反転流路28において合流し、隔壁
4の右仕切板2aに近接した位置において、反転流路2
8と除湿流路6とを連通する連通口12、12に至る。
予冷流路を経た高温圧縮空気は、除湿流路6において冷
却除湿され、出口開口13から接続流路3bを経て伝熱
パイプ中を通り、出口流路3aに抜ける間に、熱交換流
路22、23、26、27を向流状態で流れる高温吐出
圧縮空気により再熱されて、更に相対湿度が低下した乾
燥圧縮空気となって、供給口8から装置外に出て行く。
【0023】上記実施態様においては、反転流路21に
導入口9が開口する構成であるから、導入口9が、反転
流路21に開口していさえすれば、熱交換効率は、ほぼ
同一であり、従って、導入口の取付位置選択の自由度
は、極めて高い。上記実施態様では、反転流路の両側に
気流を分流させ、対称形に蛇行流路を配したが、これ
は、一連の蛇行流路として構成して、一端側の反転流路
に導入口を設け他端側の流路から除湿流路に導くもので
もよい。反転流路は、伝熱パイプが一切含まれない場合
を例示したが、これは、支持棒53の代わりに、伝熱パ
イプを設けたものなどでもよく、必ずしも、伝熱パイプ
を皆無にする必要はない。
【0024】
【発明の効果】本願圧縮空気除湿装置は、予冷流路に形
成した蛇行流路の気流の方向が伝熱パイプの伸長方向と
並行になるように構成し、かつ複数の伝熱パイプからそ
れぞれ成る複数のグループに複数の伝熱パイプを分け
て、予冷流路に伝熱パイプの伸長方向と並行に設けた弾
性を有する邪魔板によってグループの夫々を邪魔板間に
挟む状態で分画したことにより、圧力損失を極めて小さ
くすることができる。更に、邪魔板の隔壁側(若しくは
圧力容器内面側)の縁辺が固定端縁として隔壁(若しく
は圧力容器内面)に固着され、かつ固定端縁に対向する
圧力容器内面側(若しくは隔壁側)における他の縁辺が
自由端縁として圧力容器内面(若しくは隔壁)に弾性復
帰力によって圧接されることにより、構造の簡素化と組
み立ての容易性とを確保できる結果、製造コストを大幅
に削減することができる。しかも、予冷流路において、
熱交換効率を向上させるための邪魔板と圧力容器(若し
くは隔壁)との透き間は、従来、避け得なかったが、邪
魔板は自らの弾性復帰力によってその自由端縁を圧力容
器内面側(若しくは隔壁側)に圧接することによってこ
の透き間を消滅させて、予冷流路における気流の短絡を
防止することができる。したがって、熱交換効率を向上
させることができる。また、その両端が左右仕切板に固
着されて邪魔板に沿って伸長するように設けられた1以
上の支持棒によって邪魔板を支持することにより、邪魔
板の位置ずれを防止することができる。したがって、圧
縮空気導入初期にかかる圧力によって邪魔板が反転する
などの変位を確実に防止することができる。 Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressed air dehumidifier, and more particularly to an improved compressed air dehumidifier having a shell-and-tube heat exchanger. It is. 2. Description of the Related Art As this type of compressed air dehumidifier, for example, as shown in FIG. 5, inside a cylindrical pressure vessel 121, right and left side plates 121a and 121b of the pressure vessel face each other. By providing the left and right partition plates 122a and 122b, a connection channel 123b and an outlet channel 123a are formed between the side plate and the partition plate, and the space sandwiched between the left and right partition plates is partitioned by both. A pre-cooling channel 125 and a dehumidifying channel 126 are defined by partitioning by a partition 124 connecting the plates, and a connection channel 123b and an outlet channel 123a penetrating through the pre-cooling channel.
Are provided, and an air cooler 130 by a refrigerator is provided in the dehumidifying flow path.
Compressed air dehumidification provided with a communication port 126a between the compressed air inlet 127 and the dehumidification channel 126 in the pre-cooling channel and an outlet opening 129 to the connection channel 123b in the dehumidification channel. Devices are known. [0003] This is because high-temperature compressed air that has entered the pressure vessel from the inlet 127 connected to the discharge-side flow path of the air compressor flows through the pre-cooling flow path 125 into the compressed air whose temperature has been lowered after cooling and dehumidification. After being pre-cooled by heat exchange, it enters the dehumidification channel, where it is cooled and dehumidified, and then the heat transfer pipe 12
., Are reheated by the high-temperature compressed air to lower the relative humidity, and are supplied as dry compressed air from the supply port 128 to pneumatic equipment or the like. 14
Reference numerals 1 and 142 are drain discharge ports, and 131 is a refrigerant evaporating tube of the refrigerator. (See No. 58-12041). A compressed air dehumidifier using such a conventional multi-tube heat exchanger as the precooling passage 125 has a large number of baffle plates 135 and 135 in the precooling passage in order to sufficiently exhibit the precooling effect. , ..., the heat transfer pipe group 12
Are provided so as to penetrate through, and the baffle plate forms a meandering flow path meandering in the vertical or horizontal direction with respect to the direction of the air flow flowing in the heat transfer pipe. In many cases, the air that has flowed into the pre-cooling passage through the inlet port exchanges heat while meandering in a direction perpendicular to the air flow direction in the heat transfer pipe. In general, when assembling a compressed air dehumidifier of this type, for example, first, an air cooler 130 is housed in a partition wall 124, and a heat transfer pipe 120 and a baffle plate to be a pre-cooling flow path are provided outside thereof. After assembling the heat exchanger including the combination with the heat exchanger 135, these are housed and fixed in the cylindrical body, and then the left and right side plates 121a and 121b serving as end plates are fixed, thereby completing the assembly. Therefore, in order to store the baffle plate group 135,... Through which a large number of heat transfer pipes penetrate in an orthogonal state, in the cylindrical body, the inside of the body (the inside of the pressure vessel)
Unless the size and shape of the baffle plate are set so that a slight gap is formed between the baffle plate and the edge of the baffle plate, it is difficult to store the baffle plate in the cylindrical body. However, since the flow resistance of the baffle plate becomes considerably large, it is highly necessary to improve the flow resistance from the viewpoint of preventing pressure loss. There is an airflow that does not flow through the meandering flow path created by the above but passes through the gap formed between the inner wall of the pressure vessel and the edge of the baffle plate and short-circuits to the adjacent flow path. The short-circuit air flow rate, which hardly contributes to the heat exchange, increases as the flow path resistance increases due to the baffle plate, causing the heat exchange efficiency to decrease. [0007] In addition, the above-mentioned conventional apparatus includes a large number of baffle plates 135,.
・ ・ Because of the penetrating structure, the structure becomes complicated, and the skilled artisans by hand work in processing and assembling,
This requires a lot of time and increases the manufacturing cost of the device. In order to avoid such a point, the number of baffle plates in the pre-cooling channel is significantly reduced,
Alternatively, there is an apparatus having a configuration in which the heat transfer pipe 1 is omitted.
20 and the dehumidifying flow path 126 are configured to be inverted via a connection flow path provided on one side of the pressure vessel 121, so that the direction of the air flow in the heat transfer pipe is opposite to the direction of the air flow in the dehumidifying flow path. Therefore, in order to maintain the heat exchange efficiency above a certain limit, if the air flow in the pre-cooling passage and the air flow in the heat transfer pipe are made to flow in countercurrent, the compressed air inlet 127
Is limited to a position extremely close to the supply port, which limits the degree of freedom of the apparatus. A first object of the present invention is to reduce pressure loss in a precooling passage and efficiently reheat compressed air after cooling and dehumidification. /> can, the easy addition manufacture, has a high serpentine passage airtight pre-cooling flow path, a high-performance compressed air dehumidifier at a low cost
To provide . [0009] To achieve the above object, there is a contract
The compressed air dehumidifier according to claim 1 , wherein the left and right partition plates are provided in the pressure vessel so as to face each of the left and right side plates of the pressure vessel. a connecting channel and the outlet channel is formed between, defining a pre-cooling channel and dehumidifying passage by partitioning the sandwiched both left and right partition plate space by a partition connecting the two partition plates, the A plurality of heat transfer pipes are provided to penetrate the precooling flow path and communicate the connection flow path and the outlet flow path, and an air cooler is built in the dehumidification flow path, and compressed air is provided in the precooling flow path. double provided with a communication port between the inlet and the dehumidifying passage, in the compressed air dehumidifier provided with an outlet opening of said dehumidifying passage into said connecting channel, comprising each of a plurality of the heat transfer pipe
Dividing the plurality of heat transfer pipes in a group of several, sandwiching the each of the groups to the baffle plates by a baffle plate having elasticity provided in parallel with the extending direction of the heat transfer pipe in the pre-cooling passage fractionated state, with between the one and the vicinity of the left or right end of the respective baffle plate of the lateral partition plate inverted opening is provided, wherein the partition wall side of the respective baffle plates
(Or the inner side of the pressure vessel) is a fixed edge.
Is fixed to the partition wall (or the pressure inside vessel surface) Te,
And the inner surface of the pressure vessel facing the fixed edge (if
Or the other side of the partition wall) as a free edge.
A series of compressed air serpentine passage leading to the communication port from the inlet port by being pressed by the elastic restoring force to the pressure vessel inner surface (or the partition wall) is defined, each such baffle
The plate is fixed at both ends to the left and right partition plates so that
One or more support rods that extend along the board
Therefore, it is characterized by being supported from the side opposite to the elastic return direction . In the above-described compressed air dehumidifier, the baffle plate for guiding the high-temperature compressed air flowing into the pre-cooling flow path sandwiches the heat transfer pipes divided into a plurality of groups for each group from both sides (in other words, Then a group of heat transfer pipes,
(A state surrounded by the inner surface of the pressure vessel, the partition wall and the pair of baffles). Conventional heat transfer pipes are provided in a state of penetrating a number of baffle plates (baffle plates), whereas in the case of the baffle plate in the present application, the heat transfer pipe does not penetrate the baffle plates, It is characterized in that the baffle plate is also provided to extend in parallel along the direction in which the heat transfer pipe extends. Further, these baffle plates, composed of an elastic plate such as a steel sheet with improved stainless steel plate and elastic, by fixing the one end edge on the partition wall side and the fixed edge, the fixed edge and the pressure vessel inner surface The length of the baffle plate in the vertical direction (the length from the fixed edge to the free edge) is set longer than the shortest distance between the baffle plate and the baffle plate bent within the elastic limit when assembled in the pressure vessel Into the pressure vessel. Thus, the free edges of these baffles can be pressed against the inner wall of the pressure vessel by the elastic return force (spring back) of the baffles to form a meandering flow path. The reversing opening is formed by facing either the left or right edge of the baffle plate with a slight distance from the partition plate, or alternately drilling openings near the left and right edges of the baffle plate. I just need. The high-temperature compressed air flowing in the compressed air meandering channel formed in this manner flows almost in parallel with the direction of the heat transfer pipe, and if one of the adjacent meandering channels has a high temperature compressed air, If the dehumidified compressed air flowing in the heat transfer pipe is in a counter-current state, the high-temperature compressed air in the other adjacent meandering flow path is in a co-current state. Therefore, the meandering flow path in the countercurrent state accommodates a large number of heat transfer pipes, and the meandering flow path in the parallel flow has a minimum necessary number for fixing the baffle plate or the like, or By eliminating the heat pipe, simply by changing the direction of the air flow and creating a reverse flow path to create a countercurrent state,
Heat exchange efficiency can be increased. Further , since the baffle plate is provided along the direction in which the heat transfer pipe extends, the structure is simplified, and the production and assembly do not require skill, so that the production cost and the time required for production are reduced. In addition, the baffle plate achieves its main purpose as long as the degree of freedom of selection of the inlet and the airflow and countercurrent state in the heat transfer pipe can be obtained. 135)
Overwhelmingly little, and therefore very little pressure loss. Further, since there is almost no gap between the baffle plate and the inner wall surface of the pressure vessel due to the elastic return force of the baffle plate, the air flow does not flow by short-circuiting between the meandering flow paths, and the heat exchange efficiency is improved. Further, the free end edge of the baffle, by a fixed edge, is defined with its direction. However, the pressure of the baffle against the inner surface of the pressure vessel is not always constant at each baffle. Therefore, the position may be shifted. At this point, both ends are fixed to the left and right partition plates.
One or more provided to extend along the baffle
By supporting the baffle plate with the support rod, its position
Shift can be prevented. This allows the baffle to
It is also possible to prevent displacement such as inversion due to the pressure applied in the initial stage of compressed air introduction . In this case, the support rod
It may be a heat pipe. The support rods are, of course, both
It may be provided on the side. 1 to 3 show one embodiment of a compressed air dehumidifier according to the present invention. By providing left and right partition plates 2a and 2b in the cylindrical pressure vessel 1 so as to face the respective left and right side plates 1a and 1b, the end plates 1a and 2b and the left and right partition plates 2a and 2b are separated from each other. out between
An opening channel 3a and a connecting channel 3b are formed, and both left and right partition plates 2 are formed.
The space sandwiched between a and b is divided into two chambers by a cylindrical partition wall 4 connecting the two partition plates 2a and 2b, so that the pre-cooling flow path 5 of the high-temperature compressed air discharged from the air compressor and the dehumidifying flow Road 6 is defined. The pressure vessel 1 is desirably a cylindrical shape having high pressure resistance, but the partition wall 4 does not require pressure resistance, and it suffices to divide the space surrounded by the inner surface of the pressure vessel 1 and the left and right partition plates into two. , Any shape. A large number of heat transfer pipes 7, 7,... Are provided in parallel with the central axis of the pressure vessel 1 so as to penetrate through the pre-cooling flow path 5, and both ends of each heat transfer pipe are The left and right partition plates airtightly penetrate the surface facing the pre-cooling flow path 5 to open the connection flow path 3b and the outlet flow path 3a, respectively, so that the connection flow path 3b and the outlet flow path 3a Heat transfer pipe group 7,
・ Communicating via The pressure vessel 1 is provided in the dehumidifying channel 6.
Refrigerant evaporating pipe 1 of a refrigerator (not shown) provided outside
An air cooler 10 including a fin plate 1 and a fin plate 12 is housed therein. Reference numerals 12a, 12a, ... denote baffle plates for meandering the air flow. The pre-cooling channel 5 is provided with an inlet 9 for compressed air, and the outlet channel 3a is provided with a supply port 8 for compressed air that has been dehumidified and dried. Such a configuration is substantially the same as the conventional device. The feature of the device of the present application is in the following structure. A heat transfer pipe group 7 that passes through the pre-cooling passage 5 in an airtight manner;
.., When viewed from the cross-sectional direction, as shown in FIG. 2, two groups are symmetrically arranged on both sides of an imaginary vertical plane including the vertical diameter of the pressure-resistant container 1, that is, a total of four Are provided close to each other so as to form the groups G1 to G4, and the baffle P1 is sandwiched between the groups G1 to G4 from both sides.
To P8. Each of the baffle plates P1 to P8 is made of a heat-resistant plate having elasticity such as an elastic steel plate or a thin plate made of stainless steel, and one side edge of the baffle plate 4 (or the inner surface of the pressure vessel). It is fixed to the outer surface and becomes a fixed edge,
The other edge opposite to the fixed edge is a free edge, and is pressed against the inner surface of the pressure vessel 1 (or the outer surface of the partition wall) by the return elastic force of the baffle plate material, and the gap between the partition wall 4 and the inner surface of the pressure vessel is formed. Is shut off. For example, as shown in FIGS. 2 and 3, the baffle plates P <b> 1 and P <b> 5 are formed by bending (50 a) a rectangular plate body 50 so that the cross section thereof has a substantially rectangular shape, and further fixing the fixed edge 51 thereof. When the welding margin 51a is formed by being bent substantially into an L shape, and the welding margin 51a is welded and fixed to the outer surface 4a of the partition wall 4, the plate body 50 rises in a predetermined direction and is fixed by an angle formed by the welding margin 51a. When the pre-cooling channel and the dehumidifying channel to be inserted into the pressure vessel are completed, in assembling, the plate 50 is formed in a rectangular shape in the direction of arrow Y against the elasticity of the plate. It is inserted into the pressure vessel 1 while being bent deeply. The free edge 52 is pressed by the pressure vessel 1 due to the elastic restoring force of the plate body.
To the inner wall surface 1c. Are support rods for preventing the position of the baffle plates P1,..., Etc. from being shifted, and holding them at predetermined positions.
It is fixed between a and b. Partition wall 4 at fixed edge of baffle plate
The method of fixing to the surface is not limited to welding, and other general methods can be adopted. The other baffle plate fixing structure is almost the same.
This baffle plate fixing structure does not require any processing on the inner wall of the container 1 that requires pressure resistance (for example, no heat treatment such as welding is partially applied), and the baffle plate is previously attached to the partition wall. Even after being fixed, it is stored in the body of the pressure vessel and assembled, so that no gap is formed between the baffle plate and the inner surface 1c of the pressure vessel. The left and right edges of the baffle plates P1 to P8 have one of the left and right side edges of the baffle plate as shown in FIG. , Abuts one of the left and right partition plates, and the other side edge has a reversing opening 15, 15,.
・ ・The reversing opening may be one in which an opening is formed near one end of a baffle plate provided so as to abut between the left and right partition plates. The area of the inversion opening is determined such that the airflow at the inversion opening is intermediate between the flow velocities before and after the airflow inversion so that the airflow is not restricted by the inversion opening. In FIG. 4, a flow path (flow path sandwiched between the baffles P1 and P5) at the center where the introduction port 9 is opened is an inverted flow path 21 without the heat transfer pipes 7,. Baffle P
1 and P5 are both inverted openings 15 and 1 on the right partition plate 2a side.
5, the compressed air flow from the inlet 9 is
From these two reversing openings, the flow is diverted to the heat exchange channels 22 and 23 on both sides of the reversing flow channel 21 so that the air flows in the heat transfer pipe in a countercurrent state with the air flow direction. 2b
Side, and further inverts on the left partition plate side, passes through the inversion channels 24 and 25 where there is no heat transfer pipe, and again in a counter-current state with the air flow in the heat transfer pipe, 2
Flow through 6, 27. In this manner, the airflow passing through the meandering channel of the compressed air formed on both sides of the inversion channel 21 is
At a position adjacent to the right partition plate 2 a of the partition wall 4,
It reaches the communication ports 12, 12 that communicate the 8 and the dehumidifying flow path 6.
The high-temperature compressed air that has passed through the pre-cooling flow path is cooled and dehumidified in the dehumidification flow path 6, passes through the heat transfer pipe from the outlet opening 13 through the connection flow path 3b, and exits to the outlet flow path 3a. , 23, 26, and 27, is reheated by the high-temperature discharge compressed air flowing in the countercurrent state, and becomes dry compressed air having a further reduced relative humidity, and goes out of the apparatus through the supply port 8. In the above embodiment, since the inlet 9 is open to the inversion channel 21, the heat exchange efficiency is substantially the same as long as the inlet 9 is open to the inversion channel 21. Yes, and therefore, the degree of freedom in selecting the mounting position of the inlet is extremely high. In the above embodiment, the airflow is divided on both sides of the inversion flow path, and the meandering flow path is arranged symmetrically.This is configured as a series of meandering flow paths, and the inlet is provided in the inversion flow path on one end side. It may be one that leads from the flow path on the other end side to the dehumidification flow path. Although the case where the inversion flow path does not include any heat transfer pipe is illustrated, this may be a structure in which a heat transfer pipe is provided instead of the support rod 53, and it is not necessary to completely eliminate the heat transfer pipe. There is no. The present compressed air dehumidifier according to the present invention is configured so that the direction of the air flow of the meandering passage formed precooling passage is parallel to the extending direction of the heat transfer pipe, and a plurality of heat transfer pipes Karaso
Dividing multiple heat transfer pipes into multiple groups
To the pre-cooling flow path,
Each group in between the baffles
By fractionated in a state of sandwiching, it can be made extremely small pressure loss. Furthermore, the partition wall side of the baffle plate (or
The edge of the pressure vessel ( on the inner surface side) is fixed to the partition wall (or the inner surface of the pressure vessel) as a fixed edge , and faces the fixed edge.
Other edges on the inner surface side (or partition side) of the pressure vessel
By being pressed by the elastic restoring force to the pressure vessel inner surface (or partition wall) as a free end edge, a result can be ensured and ease of assembly and simplify the structure, significantly the manufacturing cost
It can be reduced to. Moreover, in the pre-cooling channel,
Baffles and pressure vessels ( to improve heat exchange efficiency)
Ku gap between the partition wall) have traditionally did not unavoidable, baffles pressure volume its free edge by its own elastic restoring force
By pressing against the inner surface side (or the partition wall side), the gap can be eliminated, and a short circuit of the airflow in the precooling flow path can be prevented . Therefore, heat exchange efficiency is improved
Can be done. Also, fix both ends to the left and right partition plates.
One or more provided to extend along the baffle
By supporting the baffle plate with the upper support rod,
The displacement of the plate can be prevented. Therefore, the pressure
The baffle plate is reversed by the pressure applied at the beginning of compressed air introduction
Such displacement can be reliably prevented.
【図面の簡単な説明】
【図1】本発明の一実施態様を示す断面説明図である。
【図2】図1のA−A断面説明図である。
【図3】図2における邪魔板の一例を示す斜視図であ
る。
【図4】図2のB−B断面に沿って展開した邪魔板の配
置を示す説明図である。
【図5】従来技術の一例を示す説明図である。
【符号の説明】
1 圧力容器
2a、b 左右仕切板
3a 出口流路
3b 接続流路
4 隔壁
5 予冷流路
6 除湿流路
7 伝熱パイプ
8 供給口
9 導入口
10 空気冷却器
12 連通口
P1〜P8 邪魔板
G1〜G4 伝熱パイプのグループ
21、24、25、28 反転流路
22、23、26、27 熱交換流路
50 弾性を備えた板体
51 固定端縁
52 自由端縁
53 支持棒BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an explanatory sectional view showing an embodiment of the present invention. FIG. 2 is an explanatory sectional view taken along the line AA of FIG. 1; FIG. 3 is a perspective view showing an example of a baffle plate in FIG. FIG. 4 is an explanatory view showing an arrangement of baffle plates developed along a BB section in FIG. 2; FIG. 5 is an explanatory diagram showing an example of a conventional technique. [Description of Signs] 1 Pressure vessels 2a, b Left and right partition plates 3a Outlet flow path 3b Connection flow path 4 Partition wall 5 Precooling flow path 6 Dehumidification flow path 7 Heat transfer pipe 8 Supply port 9 Inlet 10 Air cooler 12 Communication port P1 PP8 Baffle plates G1 to G4 Group of heat transfer pipes 21, 24, 25, 28 Reversed flow paths 22, 23, 26, 27 Heat exchange flow paths 50 Plate body 51 with elasticity Fixed edge 52 Free edge 53 Support rod
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 実開 昭61−141567(JP,U) 実開 昭60−117490(JP,U) 特公 平7−43227(JP,B2) 実公 平6−24685(JP,Y2) (58)調査した分野(Int.Cl.7,DB名) F28D 7/16 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A 61-141567 (JP, U) JP-A 60-117490 (JP, U) JP 7-43227 (JP, B2) JP 6-141 24685 (JP, Y2) (58) Fields investigated (Int. Cl. 7 , DB name) F28D 7/16
Claims (1)
板の夫々に対面するように左右仕切板を設けることによ
り、前記側面板と仕切板との間に接続流路と出口流路と
を形成し、左右両仕切板に挟まれた空間を両仕切板間を
連結する隔壁によって仕切ることにより予冷流路と除湿
流路とを画成し、当該予冷流路を貫通して前記接続流路
と前記出口流路とを連通する複数の伝熱パイプを設ける
と共に、前記除湿流路には空気冷却器を内蔵せしめ、前
記予冷流路には圧縮空気の導入口と前記除湿流路との連
通口を設けると共に、前記除湿流路には前記接続流路へ
の出口開口を設けた圧縮空気除湿装置において、複数の前記伝熱パイプからそれぞれ成る複数のグループ
に前記複数の伝熱パイプ を分けて、前記予冷流路に前記
伝熱パイプの伸長方向と並行に設けた弾性を有する邪魔
板によって前記グループの夫々を当該邪魔板間に挟む状
態で分画し、当該夫々の邪魔板の左右何れか一端付近と
前記左右仕切板の一方との間には反転開口が設けられる
と共に、当該各邪魔板における前記隔壁側(若しくは前
記圧力容器内面側)の縁辺が固定端縁として当該隔壁
(若しくは当該圧力容器内面)に固着され、かつ当該固
定端縁に対向する当該圧力容器内面側(若しくは当該隔
壁側)における他の縁辺が自由端縁として当該圧力容器
内面(若しくは当該隔壁)に弾性復帰力によって圧接さ
れることによって前記導入口から前記連通口に至る一連
の圧縮空気蛇行流路が画成され、当該各邪魔板は、その
両端が前記左右仕切板に固着されて当該邪魔板に沿って
伸長するように設けられた1以上の支持棒によって弾性
復帰方向と反対の側から支持されていることを特徴とす
る圧縮空気除湿装置。(57) to the Claims 1 pressure vessel, by providing a lateral partition plate so as to face the people each of the right and left side plates of the pressure vessel, between the side plate and the partition plate to form a connecting flow path and the outlet passage, defining a pre-cooling channel and dehumidifying passage by partitioning the sandwiched both left and right partition plate space by a partition connecting the two partition plates, the pre-cooling A plurality of heat transfer pipes penetrating the flow path and connecting the connection flow path and the outlet flow path are provided, and the dehumidification flow path has an air cooler built therein, and the pre-cooling flow path has compressed air. In the compressed air dehumidifier provided with an inlet and a communication port between the dehumidifying flow path and an outlet opening to the connection flow path in the dehumidifying flow path, a plurality of groups each including a plurality of the heat transfer pipes are provided.
Wherein the plurality of divided heat transfer pipe, min each of the groups by the baffle plate having elasticity provided in parallel with the extending direction of the heat transfer pipe in the pre-cooled passage in a state of sandwiching the baffle plates fractionated, with between and around the left or right end of the respective baffle plate one of said left and right partition plate inverted opening is provided, the partition side (or front in the respective baffle plates
Edge of the serial pressure vessel inner surface side) is fixed to the partition wall (or the pressure inside vessel surface) as fixed edges, and the solid <br/> the pressure vessel inner surface facing the Teitan edges (or equivalent the partition
Pressure of the elastic return force to the pressure vessel interior surface as another edge is free edge at the wall side) (or the partition wall)
A series of compressed air serpentine passage leading to the communication port from the inlet port is defined by being, each such baffle plates, the
Both ends are fixed to the left and right partition plates along the baffle plate.
Elastic by one or more support rods provided to extend
A compressed air dehumidifier supported from the side opposite to the return direction .
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP22302597A JP3445727B2 (en) | 1997-08-04 | 1997-08-04 | Compressed air dehumidifier |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP22302597A JP3445727B2 (en) | 1997-08-04 | 1997-08-04 | Compressed air dehumidifier |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH1147540A JPH1147540A (en) | 1999-02-23 |
JP3445727B2 true JP3445727B2 (en) | 2003-09-08 |
Family
ID=16791668
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP22302597A Expired - Fee Related JP3445727B2 (en) | 1997-08-04 | 1997-08-04 | Compressed air dehumidifier |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3445727B2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10349150A1 (en) * | 2003-10-17 | 2005-05-19 | Behr Gmbh & Co. Kg | Heat exchanger, in particular for motor vehicles |
CN107051133A (en) * | 2017-06-15 | 2017-08-18 | 国网山东省电力公司龙口市供电公司 | A kind of electric instrument drying device |
-
1997
- 1997-08-04 JP JP22302597A patent/JP3445727B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JPH1147540A (en) | 1999-02-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP3273633B2 (en) | Heat exchange device for cooling dryer in compressed air equipment and tube / plate heat exchanger intended for use in heat exchange device | |
JP6017047B2 (en) | Heat exchanger, air conditioner, refrigeration cycle apparatus, and heat exchanger manufacturing method | |
US6286590B1 (en) | Heat exchanger with flat tubes of two columns | |
US20060054310A1 (en) | Evaporator using micro-channel tubes | |
US6536512B2 (en) | Heat exchanger block | |
US6892803B2 (en) | High pressure heat exchanger | |
JPH04187991A (en) | Heat exchanger | |
EP0802383A2 (en) | Multitubular heat exchanger having an appropriate tube arrangement pattern | |
JPH05312492A (en) | Heat exchanger | |
JP6742112B2 (en) | Heat exchanger and air conditioner | |
JP3445727B2 (en) | Compressed air dehumidifier | |
JP3700481B2 (en) | Heat exchanger | |
US4805694A (en) | Heat exchanger | |
JPH04353397A (en) | Heat exchanger | |
JPH10288476A (en) | Heat-exchanger | |
JP3021298B2 (en) | Heat exchanger for compressed air dehumidification | |
JPS63210595A (en) | Plate fin type heat exchanger | |
JP2837396B2 (en) | Heat exchanger | |
CA1178268A (en) | Compact heat exchanger | |
JP2003302183A (en) | Heat exchanger for air-conditioner | |
JP2891486B2 (en) | Heat exchanger | |
US20220357107A1 (en) | Heat Exchanger | |
JP2570310Y2 (en) | Heat exchanger | |
JPH0512632Y2 (en) | ||
JPH1147541A (en) | Apparatus for dehumidifying compressed air |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090627 Year of fee payment: 6 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100627 Year of fee payment: 7 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110627 Year of fee payment: 8 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120627 Year of fee payment: 9 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120627 Year of fee payment: 9 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130627 Year of fee payment: 10 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
LAPS | Cancellation because of no payment of annual fees |