JP2003004396A - Heat exchanger and refrigerating air conditioner - Google Patents

Heat exchanger and refrigerating air conditioner

Info

Publication number
JP2003004396A
JP2003004396A JP2001193830A JP2001193830A JP2003004396A JP 2003004396 A JP2003004396 A JP 2003004396A JP 2001193830 A JP2001193830 A JP 2001193830A JP 2001193830 A JP2001193830 A JP 2001193830A JP 2003004396 A JP2003004396 A JP 2003004396A
Authority
JP
Japan
Prior art keywords
side fluid
heat exchanger
flow path
fluid
primary
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.)
Pending
Application number
JP2001193830A
Other languages
Japanese (ja)
Inventor
Mari Uchida
麻理 内田
Hitoshi Matsushima
松島　　均
Mitsugi Aoyama
貢 青山
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Priority to JP2001193830A priority Critical patent/JP2003004396A/en
Publication of JP2003004396A publication Critical patent/JP2003004396A/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

PROBLEM TO BE SOLVED: To suppress the occurrence of drying out in the course of evaporation even when the equivalent diameter of a fluid flow passage becomes smaller. SOLUTION: On the surfaces of a heat exchanger plate 1a constituting the primary-side fluid flow passage 6 of a heat exchanger and another heat exchanger plate 1b constituting the secondary-side fluid passage 7 of the heat exchanger, hydrophilic surface treatment is applied.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【発明の属する技術分野】本発明は、熱交換器および冷
凍空調装置に係り、特に、二次側流体として単相流体、
一次側流体として相変化する冷媒を用い、チラーユニッ
ト用冷凍サイクルや空気調和機に用いるに好適な熱交換
器およびこの熱交換器を用いた冷凍空調装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger and a refrigeration / air-conditioning system, and more particularly to a single-phase fluid as a secondary fluid,
The present invention relates to a heat exchanger suitable for use in a chiller unit refrigeration cycle or an air conditioner, which uses a phase-change refrigerant as a primary fluid, and a refrigeration air conditioning system using this heat exchanger.

【０００２】[0002]

【従来の技術】従来、熱交換器として、ヘッダとヘッダ
とを複数の伝熱管を介して接続し、各伝熱管内に冷媒を
導いて熱交換を行うようにしたものなどが知られてい
る。この種の熱交換器においては、伝熱性能を高めるた
めに、例えば、特開平５−１７２４８４号公報、特開平
５−３２２４７７号公報に記載されているように、伝熱
面上に表面処理を施したり、あるいは、特開平６−１４
７７８４号公報、特開平８−１３６１７８号公報に記載
されているように、伝熱管の内面に親水性あるいは撥水
性処理を施すことが行われている。これらは、いずれも
管内表面に形成された溝部と山部にそれぞれ別々の表面
処理を施すことで、蒸発伝熱性能を向上させたり、ある
いは、優れた蒸発性能と凝縮性能をバランス良く高める
ことができる。2. Description of the Related Art Heretofore, as a heat exchanger, there has been known one in which a header and a header are connected via a plurality of heat transfer tubes, and a refrigerant is introduced into each heat transfer tube to perform heat exchange. . In this type of heat exchanger, in order to improve heat transfer performance, surface treatment is performed on the heat transfer surface as described in, for example, JP-A-5-172484 and JP-A-5-322477. Or in Japanese Patent Laid-Open No. 6-14
As described in Japanese Patent No. 7784 and Japanese Patent Laid-Open No. 8-136178, hydrophilic or water repellent treatment is performed on the inner surface of the heat transfer tube. In each of these, by applying different surface treatments to the groove and peak formed on the inner surface of the pipe, it is possible to improve the evaporation heat transfer performance or to improve the excellent evaporation performance and condensation performance in a well-balanced manner. it can.

【０００３】[0003]

【発明が解決しようとする課題】近年、熱交換器のコン
パクト化、省冷媒化のニーズが大きくなってきているこ
とから、伝熱管としてはさらに細径になってきている。
また、プレート熱交換器の伝熱プレートの表面の加工は
複雑になり、積層された伝熱プレートの間隔はさらに狭
くなり、流体流路の相当直径（伝熱プレート間に形成さ
れた流体流路を、例えば、円形の流体流路に置き換えた
ときの内径）が小さくなってきている。In recent years, there has been an increasing need for heat exchangers to be compact and to save refrigerant, so that the heat transfer tubes are becoming thinner.
Further, the processing of the surface of the heat transfer plate of the plate heat exchanger becomes complicated, the distance between the stacked heat transfer plates becomes narrower, and the equivalent diameter of the fluid flow path (the fluid flow path formed between the heat transfer plates is Is becoming smaller, for example, when the fluid is replaced with a circular fluid channel.

【０００４】熱交換器を構成するに際して、伝熱面の間
隔が狭い流路や、相当直径が小さい細径管内の流路状態
をみると、流体流路の広いものとは異なる様式を示すこ
とが考えられる。特に、蒸発過程では、ドライアウトが
早く起きるため、伝熱性能の低下が懸念される。すなわ
ち、伝熱面間の流路間隔が狭くなり、特に、流体流路の
相当直径が３ｍｍ以下になると、冷媒の液膜は表面張力
によって伝熱面に沿って引っ張り上げられるが、伝熱面
上に広がるだけではなく、液面を上昇させる現象が顕著
になる。これにより、蒸発の伝熱形態は、薄膜蒸発では
なく、液膜が厚い状態からの蒸発の様態を示し、蒸発伝
熱性能が低下する。When constructing a heat exchanger, when observing the flow paths in which the intervals between the heat transfer surfaces are narrow and the small diameter tubes having a small equivalent diameter, the flow paths show a mode different from that of the wide fluid flow path. Can be considered. In particular, in the evaporation process, since dryout occurs early, there is concern that the heat transfer performance may deteriorate. That is, when the flow path interval between the heat transfer surfaces becomes narrow, and particularly when the equivalent diameter of the fluid flow path becomes 3 mm or less, the liquid film of the refrigerant is pulled up along the heat transfer surface due to surface tension. Not only does it spread upward, but the phenomenon of raising the liquid level becomes noticeable. As a result, the heat transfer form of evaporation is not a thin film evaporation but a mode of evaporation from a state where the liquid film is thick, and the evaporation heat transfer performance is deteriorated.

【０００５】本発明の課題は、流体流路の相当直径が小
さくなっても、蒸発過程でドライアウトが起きるのを抑
制することができる熱交換器および冷凍空調装置を提供
することにある。An object of the present invention is to provide a heat exchanger and a refrigerating and air-conditioning apparatus which can suppress the occurrence of dryout in the evaporation process even if the equivalent diameter of the fluid passage becomes small.

【０００６】[0006]

【課題を解決するための手段】前記課題を解決するため
に、本発明は、一次側流体の流入口と流出口とを結ぶ一
次側流体流路と、二次側流体の流入口と流出口とを結ぶ
二次側流体流路とを備え、前記一次側流体流路と前記二
次側流体流路のうち少なくとも一方の表面に、親水性の
表面処理を施してなる熱交換器を構成したものである。In order to solve the above-mentioned problems, the present invention provides a primary-side fluid flow path connecting an inlet and an outlet for a primary-side fluid, and an inlet and an outlet for a secondary-side fluid. And a secondary side fluid flow path that connects to each other, at least one surface of the primary side fluid flow path and the secondary side fluid flow path, a heat exchanger is formed by performing a hydrophilic surface treatment. It is a thing.

【０００７】また、本発明は、一次側流体の流入口と流
出口および二次側流体の流入口と流出口を有する容器内
に、前記一次側流体の流入口と流出口とを結ぶ一次側伝
熱プレートと前記二次側流体の流入口と流出口とを結ぶ
二次側伝熱プレートを複数枚積層して収納し、前記容器
と前記いずれか一方の伝熱プレートとの間または前記各
伝熱プレート間に、前記一次側流体の流入口と流出口と
を結ぶ一次側流体流路または前記二次側流体の流入口と
流出口とを結ぶ二次側流体流路を形成し、前記一次側流
体流路と前記二次側流体流路のうち少なくとも一方の表
面に、親水性の表面処理を施してなる熱交換器を構成し
たものである。Further, according to the present invention, a primary side connecting an inlet and an outlet of the primary fluid in a container having an inlet and an outlet of the primary fluid and an inlet and an outlet of the secondary fluid. A plurality of secondary side heat transfer plates that connect the heat transfer plate and the inlet and outlet of the secondary side fluid are stacked and housed, and between the container and any one of the heat transfer plates or each of the above Between the heat transfer plates, a primary-side fluid flow path connecting the inlet and outlet of the primary-side fluid or a secondary-side fluid flow path connecting the inlet and outlet of the secondary-side fluid is formed, A heat exchanger having a hydrophilic surface treatment applied to at least one surface of the primary side fluid passage and the secondary side fluid passage.

【０００８】前記各熱交換器を構成するに際しては、以
下の要素を付加することができる。In constructing each heat exchanger, the following elements can be added.

【０００９】（１）前記一次側流体流路と前記二次側流
体流路の相当直径は３ｍｍ以下である。(1) The equivalent diameter of the primary side fluid passage and the secondary side fluid passage is 3 mm or less.

【００１０】前記した手段によれば、熱交換器の伝熱面
となる一次側流体流路と二次側流体流路のうち少なくと
も一方の表面に親水性の表面処理を施すようにしたた
め、各流体流路における流体が蒸発する過程でドライア
ウトが起きるのを遅らせることができ、安定した流動状
況と伝熱性能を維持することができる。According to the above-mentioned means, the surface of at least one of the primary side fluid passage and the secondary side fluid passage, which is the heat transfer surface of the heat exchanger, is subjected to hydrophilic surface treatment. It is possible to delay the occurrence of dryout in the process of evaporation of the fluid in the fluid flow path, and maintain a stable flow state and heat transfer performance.

【００１１】すなわち、一次側流体または二次側流体と
しての冷媒が蒸発する過程で、冷媒の脈動流を防ぎ、冷
媒を薄膜化してドライアウトが起きる点を遅らせること
ができ、良好な熱伝達特性を得ることができる。また、
一次側流体流路または二次側流体流路の相当直径が３ｍ
ｍ以下の場合に、摩擦損失係数は小さくなるが、これら
の流体流路の表面に親水性の表面処理を施すことで、ポ
ンプ動力の低減を図ることができる。That is, in the process in which the refrigerant as the primary fluid or the secondary fluid evaporates, it is possible to prevent the pulsating flow of the refrigerant, delay the point at which dry-out occurs by thinning the refrigerant, and have good heat transfer characteristics. Can be obtained. Also,
Equivalent diameter of primary side fluid passage or secondary side fluid passage is 3m
When m or less, the friction loss coefficient becomes small, but the pump power can be reduced by subjecting the surfaces of these fluid channels to hydrophilic surface treatment.

【００１２】また、本発明は、一次側流体が循環する一
次側流体流路中に、前記一次側流体を圧縮する圧縮機と
前記一次側流体と熱源との間で熱交換を行わせる熱源側
熱交換器および前記一次側流体を膨張させる膨張弁を有
するとともに、二次側流体が循環する二次側流体流路中
に、熱負荷と二次側流体との間で熱交換を行わせる負荷
側熱交換器を有し、かつ前記一次側流体流路と前記二次
側流体流路中に、前記一次側流体と前記二次側流体との
間で熱交換を行わせる中間熱交換器を有する冷凍空調装
置において、前記中間熱交換器として、前記いずれかの
熱交換器を用いてなることを特徴とする冷凍空調装置を
構成したものである。Further, according to the present invention, in the primary side fluid flow path in which the primary side fluid circulates, a compressor for compressing the primary side fluid and a heat source side for exchanging heat between the primary side fluid and the heat source. A load that has a heat exchanger and an expansion valve that expands the primary fluid, and that causes heat exchange between the heat load and the secondary fluid in the secondary fluid flow path in which the secondary fluid circulates. An intermediate heat exchanger having a side heat exchanger, and performing heat exchange between the primary side fluid and the secondary side fluid in the primary side fluid passage and the secondary side fluid passage. In the refrigerating air conditioner having, the refrigerating air conditioner characterized by using any one of the heat exchangers as the intermediate heat exchanger is constructed.

【００１３】前記冷凍空調装置を構成するに際しては、
一次側流体である作動冷媒として二酸化炭素などの自然
系冷媒を用いることができる。In constructing the refrigerating and air conditioning system,
A natural refrigerant such as carbon dioxide can be used as the working refrigerant that is the primary fluid.

【００１４】[0014]

【発明の実施の形態】以下、本発明の一実施形態を図面
に基づいて説明する。図１は本発明の一実施形態を示す
プレート式熱交換器の要部断面斜視図、図２はプレート
式熱交換器に用いられる伝熱プレートの拡大斜視図、図
３はプレート式熱交換器に用いられる伝熱プレートの平
面図である。BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a cross-sectional perspective view of an essential part of a plate heat exchanger showing an embodiment of the present invention, FIG. 2 is an enlarged perspective view of a heat transfer plate used in the plate heat exchanger, and FIG. 3 is a plate heat exchanger. It is a top view of the heat transfer plate used for.

【００１５】図１ないし図３において、プレート式熱交
換器は、流体流路を構成する容器９を備えており、この
容器９の上部側には上部ヘッダ３ａ、３ｂが配置され、
下部側には下部ヘッダ４ａ、４ｂが配置されている。上
部ヘッダ３ａは一次側流体の流入口または流出口を構成
し、上部ヘッダ３ｂは二次側流体の流入口または流出口
を構成するようになっている。同様に、下部ヘッダ４ａ
は一次側流体の流入口または流出口を構成し、下部ヘッ
ダ４ｂは二次側流体の流入口または流出口を構成するよ
うになっている。さらに、容器９内には、複数枚の伝熱
プレート１ａ、１ｂが互いに積層されて収納されてい
る。伝熱プレート１ａは上部ヘッダ３ａと下部ヘッダ４
ａとを結ぶ一次側伝熱プレートとして構成されており、
伝熱プレート１ｂは上部ヘッダ３ｂと下部ヘッダ４ｂと
を結ぶ二次側伝熱プレートして構成されている。そして
各伝熱プレート１ａ、１ｂにはクロス溝構造が採用さ
れ、複数の凹凸部によって一次側流体流路６、二次側流
体流路７が形成されている。1 to 3, the plate heat exchanger is equipped with a container 9 which constitutes a fluid passage, and upper headers 3a and 3b are arranged on the upper side of the container 9.
Lower headers 4a and 4b are arranged on the lower side. The upper header 3a constitutes an inlet or outlet of the primary fluid, and the upper header 3b constitutes an inlet or outlet of the secondary fluid. Similarly, the lower header 4a
Constitutes an inlet or outlet for the primary fluid, and the lower header 4b constitutes an inlet or outlet for the secondary fluid. Furthermore, in the container 9, a plurality of heat transfer plates 1a and 1b are stacked and housed. The heat transfer plate 1a includes an upper header 3a and a lower header 4
It is configured as a heat transfer plate on the primary side connecting with a,
The heat transfer plate 1b is configured as a secondary side heat transfer plate that connects the upper header 3b and the lower header 4b. A cross groove structure is adopted for each heat transfer plate 1a, 1b, and the primary side fluid flow path 6 and the secondary side fluid flow path 7 are formed by a plurality of uneven portions.

【００１６】すなわち容器９と伝熱プレート１ａまたは
１ｂとの間、各伝熱プレート１ａ、１ｂ間に一次側流体
流路６または二次側流体流路７が形成されている。各流
体流路の相当直径は製作上や油詰まりの観点から３ｍｍ
以下（０．５ｍｍ以上）になっており、伝熱プレート１
ａ、１ｂ間の流路間隔が狭くなったことに伴って、本実
施形態においては、伝熱プレート１ａ、１ｂの伝熱面８
に親水性の表面処理を施すこととしている。That is, a primary side fluid flow path 6 or a secondary side fluid flow path 7 is formed between the container 9 and the heat transfer plate 1a or 1b, and between the heat transfer plates 1a and 1b. The equivalent diameter of each fluid channel is 3 mm from the viewpoint of manufacturing and oil clogging.
Below (0.5 mm or more), heat transfer plate 1
In the present embodiment, the heat transfer surfaces 8 of the heat transfer plates 1a and 1b are accompanied by the narrowing of the flow path interval between the heat transfer plates 1a and 1b.
It is supposed that a hydrophilic surface treatment is applied to the.

【００１７】伝熱プレート１ａ、１ｂに親水性の表面処
理を施すに際しては、伝熱プレート１ａ、１ｂを、例え
ば、アルミ材で構成した場合、有機被膜を付ける方法、
ベーマイト処理方法、ゾルゲル法によるシリカ被膜のコ
ーティングを付ける方法を採用することができる。When the heat transfer plates 1a and 1b are subjected to hydrophilic surface treatment, when the heat transfer plates 1a and 1b are made of, for example, an aluminum material, a method of applying an organic coating,
A boehmite treatment method or a method of applying a silica coating by a sol-gel method can be adopted.

【００１８】上記構成によるプレート式熱交換器を蒸発
器として使用する場合、一次側流体は、図３の実線の矢
印で示すように、下部ヘッダ４ａから液冷媒が多い２相
状態で、一次側流体流路６を下部側から上部側に向かっ
て移動する過程で二次側流体流路７の流体と熱交換され
て蒸発気化し、上部ヘッダ３ａから流出する。When the plate type heat exchanger having the above structure is used as an evaporator, the primary side fluid is in a two-phase state in which a large amount of liquid refrigerant flows from the lower header 4a as shown by the solid line arrow in FIG. In the process of moving from the lower side to the upper side in the fluid flow path 6, the heat is exchanged with the fluid in the secondary side fluid flow path 7 to evaporate and vaporize, and the liquid flows out from the upper header 3a.

【００１９】一方、プレート式熱交換器を凝縮器として
用いる場合、ガス冷媒は上部ヘッダ３ａから一次側流体
流路６内に流入し、一次側流体流路６を上部側から下部
側に向かって移動する過程で二次側流体流路７における
流体と熱交換されて凝縮液化されたあと下部ヘッダ４ａ
から流出する。On the other hand, when the plate type heat exchanger is used as the condenser, the gas refrigerant flows from the upper header 3a into the primary side fluid flow path 6, and the primary side fluid flow path 6 goes from the upper side to the lower side. In the process of moving, it is heat-exchanged with the fluid in the secondary side fluid flow path 7 to be condensed and liquefied, and then the lower header 4a.
Drained from.

【００２０】ここで、一次側流体流路６を冷媒が移動す
る過程で、伝熱プレート１ａ、１ｂ間の流路間隔が狭
く、流体流路の相当直径が３ｍｍ以下になっているの
で、伝熱プレート１ａ、１ｂの表面に親水性処理が施さ
れていないときには、冷媒の液膜は表面張力による伝熱
面に沿って引っ張り上げられるが、伝熱面上に広がるだ
けではなく、液面を上昇させる減少が顕著になる。これ
により、蒸発の伝熱形態は、薄膜蒸発ではなく、液膜が
薄い状態からの蒸発の様態を示し、蒸発伝熱性能が低下
する。Here, in the process in which the refrigerant moves through the primary side fluid flow path 6, the flow path spacing between the heat transfer plates 1a and 1b is narrow, and the equivalent diameter of the fluid flow path is 3 mm or less. When the surfaces of the heat plates 1a and 1b are not subjected to the hydrophilic treatment, the liquid film of the refrigerant is pulled up along the heat transfer surface due to the surface tension, but not only spreads on the heat transfer surface but also the liquid surface. The increasing decrease becomes noticeable. As a result, the heat transfer form of evaporation is not a thin film evaporation but a mode of evaporation from a state where the liquid film is thin, and the evaporation heat transfer performance is deteriorated.

【００２１】ところが、一次側流体流路６、二次側流体
流路７を移動する冷媒が合流あるいは分岐を繰り返しな
がら移動する過程で、伝熱プレート１ａ、１ｂの伝熱面
８に親水性の表面処理が施されていると、冷媒は伝熱面
８に沿って均一に広がることができ、伝熱面８上で冷媒
が液枯れを起こすことなく、すなわち、ドライアウトが
起きる点を遅くすることで、良好な熱伝達特性を得るこ
とができる。However, in the process in which the refrigerant moving in the primary side fluid flow path 6 and the secondary side fluid flow path 7 moves while repeating merging or branching, the heat transfer surfaces 8 of the heat transfer plates 1a and 1b are hydrophilic. When the surface treatment is applied, the refrigerant can spread uniformly along the heat transfer surface 8, and the refrigerant does not run out on the heat transfer surface 8, that is, the point at which dryout occurs is delayed. As a result, good heat transfer characteristics can be obtained.

【００２２】本実施形態においては、伝熱プレート１
ａ、１ｂの伝熱面８の表面構造としてクロス溝構造を採
用したものについて述べたが、伝熱プレート１ａ、１ｂ
の伝熱面８の構造はクロス溝構造に限定されるものでは
なく、傾斜した溝と隣合うプレートで逆方向に重ねた構
造のものや、連続した溝によってＷ字形状となるＷ溝構
造のものあるいは、波形溝構造のものを用いることもで
きる。In the present embodiment, the heat transfer plate 1
Although the cross groove structure is adopted as the surface structure of the heat transfer surfaces 8 of a and 1b, the heat transfer plates 1a and 1b are described.
The structure of the heat transfer surface 8 is not limited to the cross groove structure, and may be a structure in which the inclined groove and the adjacent plate are stacked in the opposite direction, or a W groove structure in which the continuous groove forms a W shape. Alternatively, a corrugated groove structure may be used.

【００２３】流体流路の相当直径が３ｍｍ以下で０．５
ｍｍ以上の熱交換器を構成するに際しては、平板状の伝
熱プレート１ａ、１ｂを用いる代わりに、例えば、扁平
状チューブに複数の流体流路を設けた扁平多孔管や、細
径管を複数本組合わせて流体流路を構成したものを用い
ることができる。If the equivalent diameter of the fluid passage is 3 mm or less, 0.5
When constructing a heat exchanger of mm or more, instead of using the flat heat transfer plates 1a and 1b, for example, a flat porous tube provided with a plurality of fluid flow paths in a flat tube, or a plurality of small diameter tubes are used. It is possible to use a fluid flow path constituted by this combination.

【００２４】図４に扁平多孔管２で構成された熱交換器
の構造を示す。扁平多孔管２は、図５に示すように、管
の長手方向（軸方向）に沿って多数の細孔の一次側流体
流路６が形成されている。各一次側流体流路６は互いに
独立した流体流路を構成しており、各一次側流体流路６
の内周面（伝熱面８）には親水性の表面処理が施されて
いる。FIG. 4 shows the structure of the heat exchanger composed of the flat porous tube 2. As shown in FIG. 5, the flat porous tube 2 has a large number of pores on the primary side fluid passage 6 formed along the longitudinal direction (axial direction) of the tube. Each of the primary side fluid flow paths 6 constitutes an independent fluid flow path, and each of the primary side fluid flow paths 6
The inner peripheral surface (heat transfer surface 8) is subjected to hydrophilic surface treatment.

【００２５】複数の扁平多孔管２はそれぞれ軸方向一端
部がそれぞれまとめられて上部ヘッダ３に接続されてい
るとともに、軸方向他端側がそれぞれまとめられて下部
ヘッダ４に接続されている。そして各扁平多孔管２は二
次側流体流路１７中に挿入されている。すなわち、扁平
多孔管２は容器と各扁平多孔管２との間に形成された二
次側流体流路７中に挿入され、各扁平多孔管２の表面に
二次側流体が流れ、各扁平多孔管２内の一次側流体が二
次側流体と熱交換されるようになっている。One end of each of the plurality of flat perforated tubes 2 in the axial direction is grouped together and connected to the upper header 3, and the other end of each of the flat axial tubes 2 is grouped together and connected to the lower header 4. Each flat porous tube 2 is inserted in the secondary fluid passage 17. That is, the flat porous tube 2 is inserted into the secondary-side fluid flow path 7 formed between the container and each flat porous tube 2, and the secondary fluid flows on the surface of each flat porous tube 2 so that each flat tube The primary fluid in the perforated pipe 2 is designed to exchange heat with the secondary fluid.

【００２６】図６に複数の細径伝熱管５で構成された熱
交換器の構造を示す。各細径伝熱管５は、相当直径３ｍ
ｍ以下の管を用いてジグザグ状に折り曲げられて構成さ
れており、各細径伝熱管５の軸方向一端側はそれぞれ上
部ヘッダ３に接続され、軸方向他端側はそれぞれ下部ヘ
ッダ４に接続され、一次側流体流路を構成するようにな
っている。そして各細径伝熱管５は容器と細径伝熱管５
との間に形成された二次側流体流路７中に挿入されてお
り、細径伝熱管５内を流れる一次側流体は二次側流体流
路を流れる二次側流体と熱交換されるようになってい
る。各細径伝熱管５をジグザグ状に折り曲げることで、
直線状に形成したものより伝熱面積を大きくすることが
できる。FIG. 6 shows the structure of a heat exchanger composed of a plurality of small-diameter heat transfer tubes 5. Each small diameter heat transfer tube 5 has an equivalent diameter of 3 m
It is configured to be bent in a zigzag shape using a tube of m or less, one end side in the axial direction of each small-diameter heat transfer tube 5 is connected to the upper header 3, and the other end side in the axial direction is connected to the lower header 4, respectively. The primary side fluid flow path is configured. And each small-diameter heat transfer tube 5 is a container and a small-diameter heat transfer tube 5
Is inserted into the secondary side fluid flow path 7 formed between the secondary side fluid flow path 7 and the secondary side fluid flow path 7, and the primary side fluid flowing in the small diameter heat transfer tube 5 is heat-exchanged with the secondary side fluid flowing in the secondary side fluid flow path. It is like this. By bending each small-diameter heat transfer tube 5 in a zigzag shape,
The heat transfer area can be made larger than that formed linearly.

【００２７】なお、図４および図６では、二次側流体の
流れる方向１７は、一次側流体の流れる方向とほぼ直交
しているが、二次側流体の流れの方向１７としては、一
次側流体の流れる方向と直交する他に、一次側流体と対
向する方向あるいは並行して流れる方向とすることもで
きる。この場合、望ましくは、対向流にすることで、熱
交換の効率を向上させることができる。4 and 6, the flow direction 17 of the secondary fluid is substantially orthogonal to the flow direction of the primary fluid, but the flow direction 17 of the secondary fluid is as follows. In addition to being orthogonal to the direction in which the fluid flows, the direction in which it faces the primary-side fluid or the direction in which it flows in parallel can be adopted. In this case, it is desirable that the counterflow be used to improve the efficiency of heat exchange.

【００２８】また、図４ないし図６に示す熱交換器を構
成するに際しては、各扁平多孔管２内と各細径伝熱管５
内の表面に親水性の表面処理を施すことによって管内の
流動状態を安定させることができる。すなわち、流体の
蒸発時には、脈動流を防ぎ冷媒を薄膜化してドライアウ
トが起きる点を遅らせることができ、良好な熱伝達特性
を得ることができる。さらに、流体の流動損失も低減す
ることができる。When constructing the heat exchangers shown in FIGS. 4 to 6, the inside of each flat porous tube 2 and each small diameter heat transfer tube 5 are arranged.
By applying a hydrophilic surface treatment to the inner surface, the flow state in the tube can be stabilized. That is, when the fluid evaporates, the pulsating flow can be prevented and the refrigerant can be thinned to delay the point where the dryout occurs, so that excellent heat transfer characteristics can be obtained. Further, fluid flow loss can be reduced.

【００２９】扁平多孔管２や細径伝熱管５内に親水性の
表面処理を施すに際しては、各管内周面全面に渡って親
水性の表面処理を施すものについて述べたが、表面処理
を施す面としては、必要に応じて処理すべき面を選択す
ることもできる。When the hydrophilic surface treatment is applied to the flat porous tube 2 and the small-diameter heat transfer tube 5, the hydrophilic surface treatment is applied to the entire inner peripheral surface of each tube. As the surface, a surface to be processed can be selected as needed.

【００３０】また、細径伝熱管５の断面形状としては、
円形形状の他に、楕円形、矩形形状のものを用いること
もできる。さらに、各扁平多孔管２や細径伝熱管５の内
面形状としては平滑面の他に、クロス溝、Ｗ溝などの伝
熱促進のための内面加工が施されたものでもよい。The sectional shape of the small diameter heat transfer tube 5 is as follows.
In addition to the circular shape, an elliptical shape or a rectangular shape can be used. Further, as the inner surface shape of each flat porous tube 2 and the small-diameter heat transfer tube 5, in addition to a smooth surface, a cross groove, a W groove, or the like which has been subjected to inner surface processing for promoting heat transfer may be used.

【００３１】また、伝熱促進のために、各扁平多孔管２
内にインナーフィンを入れた構造の熱交換器を構成する
こともでき、この場合、流体流路内部だけでなく、イン
ナーフィン自体にも親水性の表面処理を施せば、さらに
良好な熱伝達特性を得ることができるとともに流動抵抗
を低減することができる。Further, in order to promote heat transfer, each flat porous tube 2
It is also possible to construct a heat exchanger with a structure in which inner fins are put inside, and in this case, if a hydrophilic surface treatment is applied not only to the inside of the fluid flow path but also to the inner fins themselves, a better heat transfer characteristic can be obtained. And the flow resistance can be reduced.

【００３２】さらに、単相流の流体流路として用いられ
る二次側流体流路７の表面に親水性の表面処理を施すこ
とでポンプ動力の増大を抑制することができる。Further, by applying a hydrophilic surface treatment to the surface of the secondary side fluid passage 7 used as a single-phase fluid passage, an increase in pump power can be suppressed.

【００３３】すなわち、熱交換器の小型化のために、伝
熱プレート１ａ、１ｂの間隔や扁平多孔管２、細径伝熱
管５の径や配置間隔を狭くすると、二次側流体の流路幅
も狭くなる。このような流路を二次側流体が流れる際に
発生する三次元乱れと拡大伝熱面効果により二次側流体
においても非常に高い伝熱促進効果が得られる。しか
し、二次側流体の流路幅を単に狭くしただけでは、流動
に際して圧力損失が増加してポンプ動力が増大すること
になる。このため、二次側流体流路の相当直径が小さい
（３ｍｍ以下）場合、この二次側流体流路内の表面を親
水性にすると、摩擦損失係数が小さくなるので、ポンプ
動力の増大を抑制することができる。That is, in order to reduce the size of the heat exchanger, if the distance between the heat transfer plates 1a and 1b, the diameter of the flat porous tube 2 and the diameter of the small diameter heat transfer tube 5 and the distance between the heat transfer plates are narrowed, the flow path of the secondary side fluid is reduced. The width becomes narrower. Due to the three-dimensional turbulence and the expanded heat transfer surface effect that occur when the secondary fluid flows through such a flow path, a very high heat transfer promotion effect can be obtained even in the secondary fluid. However, if the width of the flow path of the secondary side fluid is simply narrowed, the pressure loss will increase during the flow and the pump power will increase. For this reason, when the equivalent diameter of the secondary side fluid flow path is small (3 mm or less), making the surface inside this secondary side fluid flow path hydrophilic reduces the friction loss coefficient, thus suppressing an increase in pump power. can do.

【００３４】以上のように、一次側流体流路と二次側流
体流路の表面に親水性の表面処理を施すことで、一次側
流体（冷媒）と二次側流体（水）との間で極めて高い熱
伝達特性が得られるとともに、流動に際しても摩擦損失
の低減を図ることができる。As described above, by applying hydrophilic surface treatment to the surfaces of the primary side fluid passage and the secondary side fluid passage, the primary side fluid (refrigerant) and the secondary side fluid (water) are separated from each other. Thus, extremely high heat transfer characteristics can be obtained, and friction loss can be reduced even when flowing.

【００３５】次に、本発明に係る熱交換器を冷凍空調装
置に適用したときの実施形態を図７にしたがって説明す
る。Next, an embodiment in which the heat exchanger according to the present invention is applied to a refrigerating and air-conditioning apparatus will be described with reference to FIG.

【００３６】図７は、本発明に係る熱交換器を用いた冷
凍空調装置の全体構成を示す系統図である。図７におい
て、一次側流体として、例えば、冷媒ガスが循環する一
次側流体流路中には、一次側流体を圧縮する圧縮機１１
と、一次側流体と熱源との間で熱交換を行わせる熱源側
熱交換器１６と、一次側流体を膨張させる膨張弁１５
と、一次側流体の流路を切替る四方弁１２ａと、一次側
流体と二次側流体との間で熱交換を行わせる中間熱交換
器１０が含まれており、中間熱交換器１０は四方弁１２
ａと膨張弁１５に接続され、膨張弁１５は熱源側熱交換
器１６に接続され、四方弁１２ａは圧縮機１１に接続さ
れている。FIG. 7 is a system diagram showing the entire structure of a refrigerating and air-conditioning apparatus using the heat exchanger according to the present invention. In FIG. 7, as the primary fluid, for example, a compressor 11 that compresses the primary fluid in a primary fluid flow path in which a refrigerant gas circulates.
A heat source side heat exchanger 16 for exchanging heat between the primary side fluid and the heat source, and an expansion valve 15 for expanding the primary side fluid.
And a four-way valve 12a for switching the flow path of the primary side fluid, and an intermediate heat exchanger 10 for exchanging heat between the primary side fluid and the secondary side fluid. Four-way valve 12
a and the expansion valve 15, the expansion valve 15 is connected to the heat source side heat exchanger 16, and the four-way valve 12 a is connected to the compressor 11.

【００３７】一方、二次側流体、例えば、水が循環する
二次側流体流路中には、熱負荷と二次側流体との間で熱
交換を行わせる負荷側熱交換器１４と、二次側流体を圧
送するポンプ１３と、二次側流体の流路を切替る四方弁
１２ｂと、中間熱交換器１０が含まれており、中間熱交
換器１０の両端には負荷側熱交換器１４と四方弁１２ｂ
が接続され、四方弁１２ｂにはポンプ１３が接続されて
いる。On the other hand, in the secondary side fluid passage in which the secondary side fluid, for example, water circulates, the load side heat exchanger 14 for exchanging heat between the heat load and the secondary side fluid, A pump 13 for pumping the secondary side fluid, a four-way valve 12b for switching the flow path of the secondary side fluid, and an intermediate heat exchanger 10 are included, and both ends of the intermediate heat exchanger 10 have load side heat exchange. Device 14 and four-way valve 12b
Is connected, and the pump 13 is connected to the four-way valve 12b.

【００３８】上記構成による冷凍空調装置のうち熱源側
熱交換器１６は、通常室外に設置され、負荷側熱交換器
１４は室内など、空調用あるいは冷凍用などに用いられ
る。The heat source side heat exchanger 16 of the refrigerating and air-conditioning apparatus having the above-mentioned structure is usually installed outdoors, and the load side heat exchanger 14 is used indoors such as for air conditioning or freezing.

【００３９】上記構成による冷凍空調装置において、負
荷側熱交換器１４を室内の冷房あるいは冷却に用いる場
合、一次側流体（冷媒ガス）と二次側流体（水）の循環
方向は、図中の実線の矢印の方向となる。すなわち、圧
縮機１１によって圧縮された冷媒ガスは圧縮機１１の吐
出側から四方弁１２ａを通り、室内の熱源側熱交換器１
６で冷却されて凝縮し、液冷媒となる。この液冷媒は膨
張弁１５において断熱膨張されたあと、中間熱交換器１
０に流入し、この中間熱交換器１０において二次側流体
と熱交換される。熱交換された冷媒は四方弁１２ａを経
て圧縮機１１に戻り、圧縮機１１で再び圧縮される。When the load side heat exchanger 14 is used for indoor cooling or cooling in the refrigerating and air-conditioning apparatus having the above configuration, the circulation directions of the primary side fluid (refrigerant gas) and the secondary side fluid (water) are as shown in the figure. It is in the direction of the solid arrow. That is, the refrigerant gas compressed by the compressor 11 passes through the four-way valve 12a from the discharge side of the compressor 11, and passes through the indoor heat source side heat exchanger 1
It is cooled in 6 and condensed to become a liquid refrigerant. This liquid refrigerant is adiabatically expanded in the expansion valve 15, and then the intermediate heat exchanger 1
0, and heat is exchanged with the secondary side fluid in the intermediate heat exchanger 10. The heat-exchanged refrigerant returns to the compressor 11 via the four-way valve 12a and is compressed again in the compressor 11.

【００４０】一方、二次側流体（水）はポンプ１３で加
圧されたあとポンプ１３の吐出側から四方弁１２ｂを通
ったあと、負荷側熱交換器１４で空気と熱交換される。
空気と熱交換された二次側流体は中間熱交換器１０に戻
るようになっている。この中間熱交換器１０では、一次
側流体（冷媒ガス）は二次側流体（水）から吸熱して相
変化して冷媒ガスとなり、二次側流体は冷却される。こ
のとき、中間熱交換器１０における二つの流体の循環方
向は対向流であり、一次側流体は熱交換器１０の下部側
から流入して蒸発したあと、熱交換器１０の上部側から
流出するような構造であることが望ましい。On the other hand, the secondary side fluid (water) is pressurized by the pump 13 and, after passing through the four-way valve 12b from the discharge side of the pump 13, is heat-exchanged with air by the load side heat exchanger 14.
The secondary fluid that has exchanged heat with air returns to the intermediate heat exchanger 10. In this intermediate heat exchanger 10, the primary fluid (refrigerant gas) absorbs heat from the secondary fluid (water) and undergoes a phase change to become a refrigerant gas, and the secondary fluid is cooled. At this time, the two fluids in the intermediate heat exchanger 10 circulate in opposite directions, and the primary fluid flows in from the lower side of the heat exchanger 10 and evaporates, and then flows out from the upper side of the heat exchanger 10. Such a structure is desirable.

【００４１】また負荷側熱交換器１４を室内の暖房に用
いる場合には、一次側流体と二次側流体の循環方向は冷
房時とは逆方向になるように、四方弁１２ａ、１２ｂで
流路の切替を行うことで、負荷側熱交換器１４を用いて
室内を暖房することができる。When the load-side heat exchanger 14 is used for heating the room, the four-way valves 12a and 12b are used so that the circulation directions of the primary fluid and the secondary fluid are opposite to those in cooling. By switching the paths, it is possible to heat the room using the load-side heat exchanger 14.

【００４２】本実施形態では、二次側流体の流体の循環
方法を切替る手段として四方弁１２ａ、１２ｂを用いた
ものについて述べたが、必要に応じて、逆方向に運転可
能なポンプを用いたり、流体の循環方向を変えるための
回路を電磁弁などで構成することもできる。In the present embodiment, the one using the four-way valves 12a and 12b as means for switching the fluid circulation method of the secondary side fluid has been described, but if necessary, a pump capable of operating in the reverse direction is used. Alternatively, the circuit for changing the circulation direction of the fluid may be configured by a solenoid valve or the like.

【００４３】本実施形態によれば、二次側流体（水）の
流路断面積を、中間熱交換器１０を流れる二次側流体の
量に対応して小さくしても、中間熱交換器１０の流体流
路の表面には親水性の表面処理が施されているため、流
動抵抗を低く抑えることができ、ポンプの消費電力を低
減することができる。According to the present embodiment, even if the flow passage cross-sectional area of the secondary side fluid (water) is reduced in accordance with the amount of the secondary side fluid flowing through the intermediate heat exchanger 10, the intermediate heat exchanger is obtained. Since the surface of the fluid passage 10 is subjected to hydrophilic surface treatment, the flow resistance can be suppressed to a low level and the power consumption of the pump can be reduced.

【００４４】また本実施形態においては、冷凍空調装置
の一次側冷媒と二次側冷媒とを熱交換させる中間熱交換
器１０として、流体流路の相当直径が３ｍｍ以下のもの
を用いて、各流体流路の表面に親水性の表面処理を施す
ようにすることで、流体流路の細径化に伴って、封入す
る冷媒量を少なくすることができる。Further, in the present embodiment, as the intermediate heat exchanger 10 for exchanging heat between the primary side refrigerant and the secondary side refrigerant of the refrigerating and air-conditioning apparatus, a fluid passage having an equivalent diameter of 3 mm or less is used. By performing the hydrophilic surface treatment on the surface of the fluid channel, it is possible to reduce the amount of refrigerant to be enclosed as the diameter of the fluid channel is reduced.

【００４５】また本実施形態における冷凍空調装置で
は、負荷側熱交換器１４が設置された室内空間に一次側
流体（冷媒）が入ることがないため、従来から用いられ
ている冷媒以外のＨＣ冷媒、二酸化炭素、アンモニアな
どの可燃性や毒性の心配される自然系冷媒を用いた際の
危険防止に対しても極めて大きな効果が得られる。Further, in the refrigerating and air-conditioning apparatus according to this embodiment, since the primary side fluid (refrigerant) does not enter the indoor space in which the load side heat exchanger 14 is installed, the HC refrigerant other than the conventionally used refrigerant is used. Also, a very large effect can be obtained for prevention of danger when using a natural refrigerant such as carbon dioxide, ammonia, etc., which is concerned about flammability and toxicity.

【００４６】さらに、本発明に係る熱交換器を用いた冷
凍空調装置ではコンパクトで且つエネルギー効率が良好
であるとともに、封入冷媒量を低減できるため、自然系
冷媒を用いた冷凍空調装置に最適である。Further, the refrigerating air conditioner using the heat exchanger according to the present invention is compact and has good energy efficiency, and the amount of the enclosed refrigerant can be reduced. Therefore, it is most suitable for the refrigerating air conditioner using the natural refrigerant. is there.

【００４７】例えば、二酸化炭素を冷媒として用いた場
合、凝縮器側は超臨界状態となり、冷媒は常にガス状態
となる。このとき、表面処理により、相当直径が小さい
流路を流れる際の摩擦損失係数が小さくなる特性があれ
ば、二酸化炭素を冷却するガスクーラとしての性能を引
き出すのに好適である。また、流路を細径化した際に問
題となる、冷凍機油のつまりに対しても、親水性処理に
より油滴が一個所に付着したままの状態になるのを防止
することができる。For example, when carbon dioxide is used as a refrigerant, the condenser side is in a supercritical state and the refrigerant is always in a gas state. At this time, if the surface treatment has a characteristic that a friction loss coefficient when flowing through a flow path having a small equivalent diameter becomes small, it is suitable to bring out the performance as a gas cooler for cooling carbon dioxide. Further, even if the refrigerating machine oil is clogged, which is a problem when the diameter of the flow path is reduced, it is possible to prevent the oil droplets from being left attached to one place by the hydrophilic treatment.

【００４８】以上のように本実施形態によれば、安定し
た流動状態と伝熱性能を維持することができるととも
に、設計の自由度が高いプレート式熱交換器を得ること
ができる。さらに熱交換器を用いて冷凍空調装置の効率
を高めることができる。As described above, according to this embodiment, it is possible to obtain a plate heat exchanger which can maintain a stable flow state and heat transfer performance and has a high degree of freedom in design. In addition, the heat exchanger can be used to increase the efficiency of the refrigeration air conditioner.

【００４９】[0049]

【発明の効果】以上説明したように、本発明によれば、
熱交換器の伝熱面となる一次側流体流路と二次側流体流
路のうち少なくとも一方の表面に親水性の表面処理を施
すようにしたため、各流体流路における流体が蒸発する
過程でドライアウトが起きるのを遅らせることができ、
安定した流動状況と伝熱性能を維持することができる。As described above, according to the present invention,
At least one surface of the primary-side fluid flow path and the secondary-side fluid flow path that is the heat transfer surface of the heat exchanger is subjected to a hydrophilic surface treatment, so that the fluid in each fluid flow path evaporates. You can delay the dry out happening,
It is possible to maintain stable flow conditions and heat transfer performance.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明の一実施形態を示すプレート式熱交換器
の一部断面を含む斜視図である。FIG. 1 is a perspective view including a partial cross section of a plate heat exchanger showing an embodiment of the present invention.

【図２】本発明に係るプレート式熱交換器に用いられる
伝熱プレートの拡大斜視図である。FIG. 2 is an enlarged perspective view of a heat transfer plate used in the plate heat exchanger according to the present invention.

【図３】本発明に係るプレート式熱交換器に用いられる
伝熱プレートの平面図である。FIG. 3 is a plan view of a heat transfer plate used in the plate heat exchanger according to the present invention.

【図４】扁平多孔管で構成された熱交換器の要部斜視図
である。FIG. 4 is a perspective view of a main part of a heat exchanger configured by a flat porous tube.

【図５】扁平多孔管の断面図である。FIG. 5 is a cross-sectional view of a flat porous tube.

【図６】細径伝熱管で構成された熱交換器の要部斜視図
である。FIG. 6 is a perspective view of a main part of a heat exchanger including a small diameter heat transfer tube.

【図７】本発明に係る熱交換器を用いた冷凍空調装置の
系統図である。FIG. 7 is a system diagram of a refrigerating and air-conditioning apparatus using a heat exchanger according to the present invention.

【符号の説明】[Explanation of symbols]

１ａ、１ｂ 伝熱プレート ２ 扁平多孔管 ３、３ａ、３ｂ 上部ヘッダ ４、４ａ、４ｂ 下部ヘッダ ５ 細径伝熱管 ６ 一次側流体流路 ７ 二次側流体流路 ８ 伝熱面 ９ 容器 １０ 中間熱交換器 １１ 圧縮機 １２ａ、１２ｂ 四方弁 １３ ポンプ １４ 負荷側熱交換器 １５ 膨張弁 １６ 熱源側熱交換器 1a, 1b Heat transfer plate 2 Flat perforated tube 3, 3a, 3b Upper header 4, 4a, 4b Lower header 5 Small diameter heat transfer tube 6 Primary side fluid flow path 7 Secondary side fluid flow path 8 heat transfer surface 9 containers 10 Intermediate heat exchanger 11 compressor 12a, 12b four-way valve 13 pumps 14 Load side heat exchanger 15 Expansion valve 16 Heat source side heat exchanger

───────────────────────────────────────────────────── フロントページの続き (72)発明者 青山 貢 静岡県清水市村松390番地 株式会社日立 空調システム清水生産本部内 Ｆターム(参考） 3L103 AA35 BB42 CC02 CC18 CC30 DD15 DD19 DD57    ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Mitsugu Aoyama             Hitachi, Ltd. 390 Muramatsu, Shimizu City, Shizuoka Prefecture             Air conditioning system Shimizu Production Headquarters F term (reference) 3L103 AA35 BB42 CC02 CC18 CC30                       DD15 DD19 DD57

Claims (5)

【特許請求の範囲】[Claims] 【請求項１】 一次側流体の流入口と流出口とを結ぶ一
次側流体流路と、二次側流体の流入口と流出口とを結ぶ
二次側流体流路とを備え、前記一次側流体流路と前記二
次側流体流路のうち少なくとも一方の表面に、親水性の
表面処理を施してなる熱交換器。1. A primary side fluid flow path connecting an inlet and an outlet of a primary side fluid, and a secondary side fluid flow path connecting an inlet and an outlet of a secondary side fluid, the primary side A heat exchanger having a hydrophilic surface treatment applied to at least one surface of a fluid flow path and the secondary side fluid flow path. 【請求項２】 一次側流体の流入口と流出口および二次
側流体の流入口と流出口を有する容器内に、前記一次側
流体の流入口と流出口とを結ぶ一次側伝熱プレートと前
記二次側流体の流入口と流出口とを結ぶ二次側伝熱プレ
ートを複数枚積層して収納し、前記容器と前記いずれか
一方の伝熱プレートとの間または前記各伝熱プレート間
に、前記一次側流体の流入口と流出口とを結ぶ一次側流
体流路または前記二次側流体の流入口と流出口とを結ぶ
二次側流体流路を形成し、前記一次側流体流路と前記二
次側流体流路のうち少なくとも一方の表面に、親水性の
表面処理を施してなる熱交換器。2. A primary-side heat transfer plate that connects the inlet and outlet of the primary fluid in a container having an inlet and outlet of the primary fluid and an inlet and outlet of the secondary fluid. A plurality of secondary heat transfer plates that connect the inlet and the outlet of the secondary fluid are stacked and stored, and between the container and any one of the heat transfer plates or between the heat transfer plates. A primary side fluid flow path connecting the inlet and outlet of the primary side fluid or a secondary side fluid flow path connecting the inlet and outlet of the secondary side fluid, the primary side fluid flow A heat exchanger having a hydrophilic surface treatment applied to at least one surface of the flow path and the secondary side fluid flow path. 【請求項３】 請求項１または２に記載の熱交換器にお
いて、前記一次側流体流路と前記二次側流体流路の相当
直径は３ｍｍ以下であることを特徴とする熱交換器。3. The heat exchanger according to claim 1, wherein the equivalent diameter of the primary side fluid passage and the secondary side fluid passage is 3 mm or less. 【請求項４】 一次側流体が循環する一次側流体流路中
に、前記一次側流体を圧縮する圧縮機と前記一次側流体
と熱源との間で熱交換を行わせる熱源側熱交換器および
前記一次側流体を膨張させる膨張弁を有するとともに、
二次側流体が循環する二次側流体流路中に、熱負荷と二
次側流体との間で熱交換を行わせる負荷側熱交換器を有
し、かつ前記一次側流体流路と前記二次側流体流路中
に、前記一次側流体と前記二次側流体との間で熱交換を
行わせる中間熱交換器を有する冷凍空調装置において、
前記中間熱交換器として、請求項１、２または３のうち
いずれか１項に記載の熱交換器を用いてなることを特徴
とする冷凍空調装置。4. A heat source side heat exchanger for causing heat exchange between a compressor for compressing the primary side fluid and the primary side fluid and a heat source in a primary side fluid flow path in which the primary side fluid circulates, With an expansion valve for expanding the primary fluid,
The secondary side fluid flow path in which the secondary side fluid circulates has a load side heat exchanger for exchanging heat between the heat load and the secondary side fluid, and the primary side fluid flow path and the In a secondary side fluid flow path, in a refrigerating air conditioner having an intermediate heat exchanger for performing heat exchange between the primary side fluid and the secondary side fluid,
A refrigerating and air-conditioning apparatus comprising the heat exchanger according to any one of claims 1, 2 and 3 as the intermediate heat exchanger. 【請求項５】 請求項４に記載の冷凍空調装置におい
て、前記一次側流体として自然系冷媒を用いてなること
を特徴とする冷凍空調装置。5. The refrigerating air conditioner according to claim 4, wherein a natural refrigerant is used as the primary fluid.
JP2001193830A 2001-06-27 2001-06-27 Heat exchanger and refrigerating air conditioner Pending JP2003004396A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2001193830A JP2003004396A (en) 2001-06-27 2001-06-27 Heat exchanger and refrigerating air conditioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2001193830A JP2003004396A (en) 2001-06-27 2001-06-27 Heat exchanger and refrigerating air conditioner

Publications (1)

Publication Number Publication Date
JP2003004396A true JP2003004396A (en) 2003-01-08

Family

ID=19032044

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Application Number Title Priority Date Filing Date
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Country Link
JP (1) JP2003004396A (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013528276A (en) * 2010-05-26 2013-07-08 アルファ・ラバル・コーポレイト・エービー Heat exchanger plate with antifouling properties
WO2015111175A1 (en) 2014-01-23 2015-07-30 三菱電機株式会社 Heat pump apparatus
JP2020082027A (en) * 2018-11-30 2020-06-04 国立大学法人東北大学 Drop collection device

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013528276A (en) * 2010-05-26 2013-07-08 アルファ・ラバル・コーポレイト・エービー Heat exchanger plate with antifouling properties
WO2015111175A1 (en) 2014-01-23 2015-07-30 三菱電機株式会社 Heat pump apparatus
CN105940276A (en) * 2014-01-23 2016-09-14 三菱电机株式会社 Heat pump apparatus
US20160320105A1 (en) * 2014-01-23 2016-11-03 Mitsubishi Electric Corporation Heat pump apparatus
JPWO2015111175A1 (en) * 2014-01-23 2017-03-23 三菱電機株式会社 Heat pump equipment
US10605498B2 (en) 2014-01-23 2020-03-31 Mitsubishi Electric Corporation Heat pump apparatus
JP2020082027A (en) * 2018-11-30 2020-06-04 国立大学法人東北大学 Drop collection device

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