JP2010230213A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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JP2010230213A
JP2010230213A JP2009076377A JP2009076377A JP2010230213A JP 2010230213 A JP2010230213 A JP 2010230213A JP 2009076377 A JP2009076377 A JP 2009076377A JP 2009076377 A JP2009076377 A JP 2009076377A JP 2010230213 A JP2010230213 A JP 2010230213A
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fluid passage
fluid
heat transfer
heat exchanger
transfer promoting
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Keiko Kanekawa
桂子 金川
Eiji Kuwabara
永治 桑原
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Toshiba Carrier Corp
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Toshiba Carrier Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of improving heat exchange efficiency. <P>SOLUTION: In the heat exchanger, two plates 4 formed with recessed parts 5 of meandering shapes having a plurality of straight line parts 5a and curve parts 5b connecting ends of the straight line parts 5a are formed in one faces, and protruding parts 6 of meandering shapes having a plurality of straight line parts 6a and curve parts 6b connecting ends of the straight line parts 6a and corresponding to the recessed parts 5 in other faces are joined such that the straight line parts 6a of the protruding part 6 contact each other, and a fluid passage 7 passing fluid is formed between adjacent protruding parts 6. Refrigerant pipes 3 of meandering shapes are respectively fit in the recessed parts 5 of meandering shapes formed in one face of the two plates 4. A heat transfer accelerator 10 protruding into the fluid passage 7 and increasing a surface area of the fluid passage 7 is formed on the plate 4. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

本発明は、熱交換器に関し、特に、冷媒が流れる冷媒管と、この冷媒管の周囲に設けられた流体通路を流れる流体との間での熱交換を効率良く行なえるようにした熱交換器に関する。   The present invention relates to a heat exchanger, and in particular, a heat exchanger capable of efficiently performing heat exchange between a refrigerant pipe through which a refrigerant flows and a fluid flowing through a fluid passage provided around the refrigerant pipe. About.

従来、冷媒が流れる冷媒管と、この冷媒管の周囲に設けられた流体通路を流れる流体との間で熱交換を行なうようにした熱交換器としては、例えば、下記特許文献１に記載されたものが知られている。   Conventionally, as a heat exchanger in which heat is exchanged between a refrigerant pipe through which a refrigerant flows and a fluid flowing through a fluid passage provided around the refrigerant pipe, for example, it is described in Patent Document 1 below. Things are known.

特許文献１に記載された熱交換器は、冷媒との間で熱交換される流体（例えば、水）が流れる流体通路が２枚のプレートを張り合わせた間に形成され、プレート間に形成された流体通路内に、冷媒が流れる冷媒管が配置されている。冷媒管は、複数の直線部と直線部の端部に位置する複数の湾曲部とからなり、蛇行形状に形成されている。   In the heat exchanger described in Patent Document 1, a fluid passage through which a fluid (for example, water) exchanged with a refrigerant flows is formed between two plates, and is formed between the plates. A refrigerant pipe through which the refrigerant flows is disposed in the fluid passage. The refrigerant pipe is composed of a plurality of straight portions and a plurality of curved portions located at the ends of the straight portions, and is formed in a meandering shape.

特開２００７−３０１４号公報JP 2007-3014 A

しかしながら、特許文献１に記載された熱交換器においては、以下の点について考慮されていない。   However, in the heat exchanger described in Patent Document 1, the following points are not considered.

流体通路内を流れる流体は、流体通路の一端側に形成された流体入口から流入し、流体通路の他端側に形成された流体出口から流出する。そして、流体入口から流体出口に向かう方向が、冷媒管の直線部と略直交している。   The fluid flowing in the fluid passage flows in from a fluid inlet formed on one end side of the fluid passage and flows out from a fluid outlet formed on the other end side of the fluid passage. The direction from the fluid inlet to the fluid outlet is substantially orthogonal to the straight portion of the refrigerant pipe.

このため、流体通路内を流れる流体の流量は、流体入口と流体出口とを結ぶ直線上及びその周囲で最大になり、その直線上から離れるについて少なくなる。したがって、流体通路内における流体入口と流体出口とを結ぶ直線から大きく離れた領域では、冷媒と流体との間の熱交換が有効に行なわれず、熱交換器の熱交換効率が低くなっている。   For this reason, the flow rate of the fluid flowing in the fluid passage is maximized on and around the straight line connecting the fluid inlet and the fluid outlet, and decreases with distance from the straight line. Therefore, in a region far away from the straight line connecting the fluid inlet and the fluid outlet in the fluid passage, heat exchange between the refrigerant and the fluid is not effectively performed, and the heat exchange efficiency of the heat exchanger is low.

本発明はこのような課題を解決するためになされたもので、その目的は、熱交換効率を高めることができる熱交換器を提供することである。   The present invention has been made to solve such a problem, and an object of the present invention is to provide a heat exchanger capable of improving the heat exchange efficiency.

本発明の実施の形態に係る第１の特徴は、熱交換器において、一方の面に複数本の直線部と前記直線部の端部同士を繋ぐ曲線部とを有する蛇行形状の凹部が形成され、他方の面に複数本の直線部と前記直線部の端部同士を繋ぐ曲線部とを有して前記凹部に対応する蛇行形状の凸部が形成された２枚のプレートを、前記凸部の前記直線部が接するように接合し、隣接する前記凸部間に流体が流れる流体通路が形成されたプレート本体と、前記プレート本体に設けられて前記流体通路の一端側に連通された流体入口と前記プレート本体に設けられて前記流体通路の他端側に連通された流体出口と、２枚の前記プレートの一方の面に形成された蛇行形状の前記凹部にそれぞれ嵌め込まれた蛇行形状の冷媒管と、前記プレートに形成されて前記流体通路内に突出し、この流体通路の表面積を増大させる伝熱促進体と、を備えることである。   A first feature according to the embodiment of the present invention is that, in the heat exchanger, a meandering recess having a plurality of straight portions and a curved portion connecting the ends of the straight portions is formed on one surface. Two plates, each having a plurality of straight portions and a curved portion connecting the ends of the straight portions, each having a meandering convex portion corresponding to the concave portion, A plate main body formed with a fluid passage through which fluid flows between adjacent convex portions, and a fluid inlet provided in the plate main body and communicated with one end side of the fluid passage. And a fluid outlet provided in the plate body and communicated with the other end of the fluid passage, and a meandering refrigerant fitted in a meandering recess formed on one surface of the two plates. A tube and the fluid passage formed in the plate. Projects within the heat transfer accelerating members to increase the surface area of the fluid passageway, is to comprise a.

本発明によれば、伝熱促進体を設けることにより流体通路の表面積が増大し、熱交換効率を高めることができる。   According to the present invention, by providing the heat transfer promoting body, the surface area of the fluid passage is increased, and the heat exchange efficiency can be increased.

本発明の第１の実施の形態の熱交換器の内部構造を断面にして示す斜視図である。It is a perspective view which shows the internal structure of the heat exchanger of the 1st Embodiment of this invention in a cross section. 熱交換器を構成する、２枚のプレートからなるプレート本体と、プレートの凹部に嵌め込まれた冷媒管とを示す斜視図である。It is a perspective view which shows the plate main body which consists of two plates which comprise a heat exchanger, and the refrigerant pipe engage | inserted by the recessed part of the plate. 図２の分解斜視図である。FIG. 3 is an exploded perspective view of FIG. 2. 図２におけるＢ−Ｂ線断面図である。It is the BB sectional view taken on the line in FIG. 伝熱促進体の第１の変形例を示す断面図である。It is sectional drawing which shows the 1st modification of a heat-transfer promoter. 伝熱促進体の第２の変形例を示す断面図である。It is sectional drawing which shows the 2nd modification of a heat-transfer promoter. 伝熱促進体の第３の変形例を示す断面図である。It is sectional drawing which shows the 3rd modification of a heat-transfer promoter.

以下、本発明の実施の形態を図面を用いて説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

（実施の形態）
本発明の一実施の形態を、図１ないし図４に基づいて説明する。熱交換器１は、図１に示すように、積層された複数のプレート本体２と、内部を冷媒が流れる複数の冷媒管３とにより構成されている。なお、複数の冷媒管３は、その流入側と流出側とでそれぞれ集合されている。 (Embodiment)
An embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 1, the heat exchanger 1 includes a plurality of stacked plate bodies 2 and a plurality of refrigerant tubes 3 through which refrigerant flows. The plurality of refrigerant tubes 3 are assembled on the inflow side and the outflow side, respectively.

プレート本体２は、２枚のプレート４を接合することにより形成されている。各プレート４の一方の面である表面には、図３に示すように、複数本の直線部５ａとこれらの直線部５ａの端部同士を繋ぐ曲線部５ｂとを有する蛇行形状の凹部５が形成されている。各プレート４の他方の面である裏面には、複数の直線部６ａとこれらの直線部６ａの端部同士を繋ぐ曲線部６ｂとを有する蛇行形状の凸部６が形成されている。なお、凸部６は凹部５に対応する形状に形成されており、凹部５と凸部６とはプレート４をプレス加工することにより形成されており、このプレス加工により突出した側が凸部６となり、へこんだ側が凹部５となり、凸部６と凹部５とは対応する形状に形成されている。２枚のプレート４において、隣合う直線部５の間隔は同じに形成されている。また、直線部５ａ，６ａの一部は、後述する流体通路７を形成するために曲線部５ｂ，６ｂを越えるプレート４の端部まで延出されている。   The plate body 2 is formed by joining two plates 4 together. As shown in FIG. 3, a meandering concave portion 5 having a plurality of straight portions 5a and a curved portion 5b connecting the ends of these straight portions 5a is formed on the surface which is one surface of each plate 4. Is formed. On the back surface, which is the other surface of each plate 4, a meandering convex portion 6 having a plurality of linear portions 6a and a curved portion 6b connecting the ends of these linear portions 6a is formed. In addition, the convex part 6 is formed in the shape corresponding to the concave part 5, and the concave part 5 and the convex part 6 are formed by press-working the plate 4, The side which protruded by this press work becomes the convex part 6. The indented side becomes the concave portion 5, and the convex portion 6 and the concave portion 5 are formed in corresponding shapes. In the two plates 4, the interval between the adjacent straight portions 5 is the same. Moreover, a part of straight part 5a, 6a is extended to the edge part of the plate 4 exceeding curve part 5b, 6b in order to form the fluid channel | path 7 mentioned later.

２枚のプレート４は、凸部６の直線部６ａ同士が接するように接合されている。なお、凸部６の曲線部６ｂは、２枚のプレート４を接合させた場合に互いに接しないように位置をずらして形成されている。   The two plates 4 are joined so that the straight portions 6a of the convex portions 6 are in contact with each other. In addition, the curved part 6b of the convex part 6 is formed by shifting the position so as not to contact each other when the two plates 4 are joined.

そして、プレート本体２には、２枚のプレート４を接合することにより隣接する凸部６間に流体通路７が形成されている。この流体通路７には、図２において破線の矢印で示すように流体である水が流れる。   In the plate body 2, a fluid passage 7 is formed between adjacent convex portions 6 by joining two plates 4. Water, which is a fluid, flows through the fluid passage 7 as indicated by the dashed arrows in FIG.

また、プレート本体２には、流体通路７の一端側に連通されて流体通路７内に流入する水が流入する流体入口８と、流体通路７の他端側に連通されて流体通路７内を経由した水が流出する流体出口９とが形成されている。   In addition, the plate body 2 communicates with one end of the fluid passage 7 so that water flowing into the fluid passage 7 flows into the plate body 2 and communicates with the other end of the fluid passage 7 through the fluid passage 7. A fluid outlet 9 is formed through which the water passing through flows out.

冷媒配管３は、各プレート４の表面に形成された蛇行形状の凹部５と同じ蛇行形状に形成され、冷媒配管３は各プレート４の凹部５に嵌め込まれている。   The refrigerant pipe 3 is formed in the same meandering shape as the meandering concave part 5 formed on the surface of each plate 4, and the refrigerant pipe 3 is fitted in the concave part 5 of each plate 4.

各プレート４には、図４に示すように、流体通路７内に突出する複数の伝熱促進体１０が形成され、これらの伝熱促進体１０が形成されることにより、流体通路７の表面積が増大されている。また、これらの伝熱促進体１０は、流体通路７内を流れる水の流れ方向を流体通路１０の壁面を構成するプレート４に向ける形状に形成されている。さらに、伝熱促進体１０は、流体通路７内を流れる水の流速を、水の流れ方向に沿った流体通路７の各部において略均一にするような密度で形成されている。具体的には、水の流れ方向が反転する流体通路７の端部側には伝熱促進体１０が設けられず、流体通路７の直線部分にのみ伝熱促進体１０が設けられている。これは、伝熱促進体１０を設けることにより流体通路７の断面積が小さくなって流速が速くなるが、流体通路７の端部側では曲線部６ｂにより流体通路７の断面積が狭められて既に流速が速くなっているためである。また、一方のプレート４に形成された伝熱促進体１０と他方のプレート４に形成された伝熱促進体１０とは、水の流れに沿った方向の同じ位置に配置されず、図４に示すようにその位置をずらして配置されている。   As shown in FIG. 4, each plate 4 is formed with a plurality of heat transfer promoting bodies 10 protruding into the fluid passage 7. By forming these heat transfer promoting bodies 10, the surface area of the fluid passage 7 is formed. Has been increased. Further, these heat transfer promoting bodies 10 are formed in a shape in which the flow direction of water flowing in the fluid passage 7 is directed to the plate 4 constituting the wall surface of the fluid passage 10. Furthermore, the heat transfer promoting body 10 is formed with a density that makes the flow velocity of the water flowing in the fluid passage 7 substantially uniform in each part of the fluid passage 7 along the flow direction of the water. Specifically, the heat transfer promoting body 10 is not provided on the end side of the fluid passage 7 where the flow direction of water is reversed, and the heat transfer promoting body 10 is provided only on the straight portion of the fluid passage 7. This is because the provision of the heat transfer promoting body 10 reduces the cross-sectional area of the fluid passage 7 and increases the flow velocity, but the cross-sectional area of the fluid passage 7 is narrowed by the curved portion 6b on the end side of the fluid passage 7. This is because the flow velocity is already high. Further, the heat transfer promoting body 10 formed on one plate 4 and the heat transfer promoting body 10 formed on the other plate 4 are not arranged at the same position in the direction along the flow of water. As shown, the positions are shifted.

このような構成において、この熱交換器１では、高温の冷媒が矢印Ａで示すように冷媒管３内を流れる。また、水が、流体入口８から流入し、破線の矢印で示すように流体通路７内を流れ、流体出口９から流出する。そして、水が流体通路７内を流れる間に、冷媒管３内を流れる高温の冷媒との間で熱交換され、温水となる。   In such a configuration, in the heat exchanger 1, high-temperature refrigerant flows through the refrigerant pipe 3 as indicated by an arrow A. In addition, water flows in from the fluid inlet 8, flows in the fluid passage 7 as indicated by the dashed arrow, and flows out from the fluid outlet 9. And while water flows in the fluid passage 7, heat is exchanged with the high-temperature refrigerant flowing in the refrigerant pipe 3, and becomes hot water.

流体通路７内においては、一方のプレート４に形成された伝熱促進体１０と他方のプレート４に形成された伝熱促進体１０とが水の流れに沿って位置をずらして配置されているため、流体通路７内を流れる水は、図４の矢印で示すように、蛇行しながら流れる。   In the fluid passage 7, the heat transfer promoting body 10 formed on one plate 4 and the heat transfer promoting body 10 formed on the other plate 4 are arranged with their positions shifted along the flow of water. Therefore, the water flowing in the fluid passage 7 flows while meandering as shown by the arrows in FIG.

ここで、冷媒と水との間での熱交換効率を高めるためには、流体通路７の表面積を大きくすることや、流体通路７内を流れる水の流れ方向を流通通路７の壁面に向けることや、流体通路７内を流れる水の流速を速くすることや、流体通路７内を流れる水の流れ方向に沿った流速を流体通路７内の各部において均一化することが考えられる。   Here, in order to increase the heat exchange efficiency between the refrigerant and the water, the surface area of the fluid passage 7 is increased or the flow direction of the water flowing in the fluid passage 7 is directed to the wall surface of the circulation passage 7. Alternatively, it is conceivable to increase the flow velocity of the water flowing in the fluid passage 7 and to equalize the flow velocity along the flow direction of the water flowing in the fluid passage 7 in each part in the fluid passage 7.

したがって、図４に示すように流体通路７内に伝熱促進体１０を設けることにより、流体通路７の表面積が増大し、冷媒と水との間の熱交換効率を高めることができる。   Therefore, by providing the heat transfer promoting body 10 in the fluid passage 7 as shown in FIG. 4, the surface area of the fluid passage 7 is increased, and the heat exchange efficiency between the refrigerant and water can be increased.

また、流体通路７内に伝熱促進体１０を設けることにより、流体通路７の直線部分の断面積が小さくなるためにこの直線部分を流れる水の流速が速くなり、冷媒と水との間の熱交換効率を高めることができる。   Further, by providing the heat transfer promoting body 10 in the fluid passage 7, the cross-sectional area of the straight portion of the fluid passage 7 is reduced, so that the flow rate of water flowing through the straight portion is increased, and the flow rate between the refrigerant and water is increased. Heat exchange efficiency can be increased.

また、流体通路７内に伝熱促進体１０を設けることにより、流体通路７内を流れる水は、図４の矢印で示すように伝熱促進体１０に当たった後その伝熱促進体１０が形成されているプレート４と反対側のプレート４に向かうようになり、流体通路７内を流れる水が伝熱促進体１０を含む流体通路７の壁面にぶつかり、冷媒と水との間の熱交換効率を高めることができる。   Further, by providing the heat transfer promoting body 10 in the fluid passage 7, the water flowing in the fluid passage 7 hits the heat transfer promoting body 10 as shown by the arrow in FIG. The water flowing in the fluid passage 7 collides with the wall surface of the fluid passage 7 including the heat transfer facilitator 10, and the heat exchange between the refrigerant and the water occurs. Efficiency can be increased.

また、流体通路７内の伝熱促進体１０を、水の流れ方向が反転する流体通路７の端部側には設けず、流体通路７の直線部分のみに設けているため、伝熱促進体１０を設けない場合には流体通路７の端部側に比べて流速が遅い直線部分の流速を速くすることができる。これにより、流体通路７内を流れる水の流れ方向に沿った流速を流体通路７内の各部において均一化するとと共に速めることができ、冷媒と水との間の熱交換を熱交換器１内の各部で略均等に行なうことができ、熱交換効率を高めることができる。   Further, the heat transfer promoting body 10 in the fluid passage 7 is not provided on the end portion side of the fluid passage 7 where the flow direction of water is reversed, and is provided only on the straight portion of the fluid passage 7. When 10 is not provided, the flow velocity of the straight portion where the flow velocity is slower than that of the end portion of the fluid passage 7 can be increased. Thereby, the flow velocity along the flow direction of the water flowing in the fluid passage 7 can be made uniform in each part in the fluid passage 7 and can be accelerated, and the heat exchange between the refrigerant and water can be performed in the heat exchanger 1. Each part can be performed substantially evenly, and the heat exchange efficiency can be increased.

なお、本実施の形態では、水の流れ方向が反転する流体通路７の端部側には伝熱促進体１０を設けず、流体通路７の直線部分にのみ伝熱促進体１０を設けた場合を例に挙げて説明したが、流体通路７の端部側に少数の伝熱促進体１０を設け、流体通路７の直線部分に多数の伝熱促進体１０を設けることにより、流体通路７内を流れる水の流速を、水の流れ方向に沿った流体通路７の各部において略均一にするようにしてもよい。   In the present embodiment, the heat transfer promoting body 10 is not provided on the end portion side of the fluid passage 7 where the water flow direction is reversed, and the heat transfer promoting body 10 is provided only on the straight portion of the fluid passage 7. However, by providing a small number of heat transfer promoting bodies 10 on the end side of the fluid passage 7 and providing a large number of heat transfer promoting bodies 10 on the straight portion of the fluid passage 7, The flow velocity of the water flowing through the water may be substantially uniform in each part of the fluid passage 7 along the water flow direction.

（第１の変形例）
以下、伝熱促進体の変形例について説明する。 (First modification)
Hereinafter, modifications of the heat transfer promoting body will be described.

図５は、第１の変形例の伝熱促進体１１を示している。この伝熱促進体１１は、図４に示した伝熱促進体１０に比べて、流体通路７内への突出寸法が大きく形成されている。   FIG. 5 shows the heat transfer promoting body 11 of the first modification. The heat transfer promoting body 11 has a larger projecting dimension into the fluid passage 7 than the heat transfer promoting body 10 shown in FIG.

これにより、流体通路７の表面積がさらに増大し、冷媒と水との間の熱交換効率をさらに高めることができる。   Thereby, the surface area of the fluid channel | path 7 further increases, and the heat exchange efficiency between a refrigerant | coolant and water can further be improved.

また、この伝熱促進体１１を設けることにより、流体通路７の直線部分の断面積がさらに狭くなり、この直線部分を流れる水の流速がさらに速くなり、冷媒と水との間の熱交換効率をさらに高めることができる。   Further, by providing this heat transfer promoting body 11, the cross-sectional area of the straight portion of the fluid passage 7 is further reduced, the flow rate of water flowing through this straight portion is further increased, and the heat exchange efficiency between the refrigerant and water is increased. Can be further enhanced.

また、この伝熱促進体１１を設けることにより、流体通路７内を流れる水がプレート４の壁面に強くぶつかるようになり、冷媒と水との間の熱交換効率をさらに高めることができる。   Further, by providing this heat transfer promoting body 11, the water flowing in the fluid passage 7 comes into a strong collision with the wall surface of the plate 4, and the heat exchange efficiency between the refrigerant and the water can be further increased.

（第２の変形例）
図６は、第２の変形例の伝熱促進体１２，１３を示している。一方のプレート４には流体通路７内への突出寸法が小さい伝熱促進体１２が形成され、他方のプレート４には流体通路７内への突出寸法が大きい伝熱促進体１３が形成されている。また、伝熱促進体１２，１３における水の流れ方向の下流側に向けた面の傾きが緩やかになっている。 (Second modification)
FIG. 6 shows the heat transfer promoting bodies 12 and 13 of the second modification. One plate 4 is formed with a heat transfer promoting body 12 with a small projecting dimension into the fluid passage 7, and the other plate 4 is formed with a heat transfer promoting body 13 with a large projecting dimension into the fluid passage 7. Yes. Moreover, the inclination of the surface toward the downstream of the flow direction of water in the heat transfer promoting bodies 12 and 13 is gentle.

これにより、流体通路７内を流れる水が伝熱促進体１２，１３から剥離せずに伝熱促進体１２，１３の表面をなめるように流れるようになり、冷媒と水との間の熱交換効率をさらに高めることができる。   As a result, the water flowing in the fluid passage 7 flows so as to lick the surfaces of the heat transfer promoting bodies 12 and 13 without being separated from the heat transfer promoting bodies 12 and 13, and heat exchange between the refrigerant and the water is performed. Efficiency can be further increased.

（第３の変形例）
図７は、第３の変形例の伝熱促進体１４を示している。前述した実施の形態及び各変形例では、一方のプレート４と他方のプレート４とに形成された伝熱促進体１０〜１３は、水の流れに沿った方向の位置をずらして配置されているが、第３の変形例の伝熱促進体１４は、水の流れに沿った方向の同じ位置に配置されている。 (Third Modification)
FIG. 7 shows a heat transfer promoting body 14 of a third modification. In the embodiment and each modification described above, the heat transfer promoting bodies 10 to 13 formed on one plate 4 and the other plate 4 are arranged with the positions in the direction along the water flow being shifted. However, the heat transfer promotion bodies 14 of the third modification are arranged at the same position in the direction along the flow of water.

このように、二つのプレート４に形成された伝熱促進体１４を水の流れ方向に沿った同じ位置で対向させた場合でも、流体通路７の表面積を大きくすることができ、また、流体通路７内を流れて伝熱促進体１４を通過した水を流通通路７の壁面に向けることができ、また、流体通路７内を流れる水の流速を速くすることができ、冷媒と水との間の熱交換効率を高めることができる。   As described above, even when the heat transfer promoting bodies 14 formed on the two plates 4 are opposed to each other at the same position along the water flow direction, the surface area of the fluid passage 7 can be increased, and the fluid passage The water that has passed through the heat transfer promoting body 14 through the inside of the flow path 7 can be directed to the wall surface of the flow passage 7, and the flow rate of the water that flows through the fluid path 7 can be increased. The heat exchange efficiency can be increased.

なお、前述した実施の形態及び各変形例では、２つのプレート４にそれぞれ伝熱促進体１０〜１４を形成した場合について説明したが、伝熱促進体を一方のプレート４にのみ形成し、他方のプレート４には伝熱促進体を形成しなくてもよい。   In the above-described embodiment and each modification, the case where the heat transfer promoting bodies 10 to 14 are formed on the two plates 4 has been described, but the heat transfer promoting body is formed only on one plate 4 and the other. It is not necessary to form a heat transfer promoting body on the plate 4.

このように、一方のプレート４にのみ伝熱促進体を形成した場合でも、冷媒と水との間の熱交換効率を高めることができる。   Thus, even when a heat transfer promoting body is formed only on one plate 4, the heat exchange efficiency between the refrigerant and water can be increased.

１…熱交換器，２…プレート本体，３…冷媒管，４…プレート，５…凹部，５ａ…直線部，５ｂ…曲線部，６…凸部，６ａ…直線部，６ｂ…曲線部，７…流体通路，８…流体入口，９…流体出口，１０…伝熱促進体，１１，１２，１３…伝熱促進体   DESCRIPTION OF SYMBOLS 1 ... Heat exchanger, 2 ... Plate main body, 3 ... Refrigerant tube, 4 ... Plate, 5 ... Recessed part, 5a ... Straight part, 5b ... Curved part, 6 ... Convex part, 6a ... Straight part, 6b ... Curved part, 7 ... Fluid passage, 8 ... Fluid inlet, 9 ... Fluid outlet, 10 ... Heat transfer enhancer, 11, 12, 13 ... Heat transfer enhancer

Claims (5)

一方の面に複数本の直線部と前記直線部の端部同士を繋ぐ曲線部とを有する蛇行形状の凹部が形成され、他方の面に複数本の直線部と前記直線部の端部同士を繋ぐ曲線部とを有して前記凹部に対応する蛇行形状の凸部が形成された２枚のプレートを、前記凸部の前記直線部が接するように接合し、隣接する前記凸部間に流体が流れる流体通路が形成されたプレート本体と、
前記プレート本体に設けられて前記流体通路の一端側に連通された流体入口と前記プレート本体に設けられて前記流体通路の他端側に連通された流体出口と、
２枚の前記プレートの一方の面に形成された蛇行形状の前記凹部にそれぞれ嵌め込まれた蛇行形状の冷媒管と、
前記プレートに形成されて前記流体通路内に突出し、この流体通路の表面積を増大させる伝熱促進体と、
を備えることを特徴とする熱交換器。 A serpentine concave portion having a plurality of straight portions and a curved portion connecting the ends of the straight portions is formed on one surface, and the plurality of straight portions and the ends of the straight portions are formed on the other surface. Two plates having meandering convex portions corresponding to the concave portions formed by connecting the curved plates to each other so that the linear portions of the convex portions are in contact with each other, and the fluid between the adjacent convex portions is fluidized. A plate body in which a fluid passage through which the gas flows is formed;
A fluid inlet provided in the plate body and communicated with one end of the fluid passage; a fluid outlet provided in the plate body and communicated with the other end of the fluid passage;
Meander-shaped refrigerant pipes respectively fitted in the meander-shaped concave portions formed on one surface of the two plates;
A heat transfer facilitator formed in the plate and projecting into the fluid passage to increase the surface area of the fluid passage;
A heat exchanger comprising: 前記伝熱促進体は、前記流体通路内を流れる流体の流れ方向をこの流体通路の壁面に向ける形状に形成されていることを特徴とする請求項１記載の熱交換器。   The heat exchanger according to claim 1, wherein the heat transfer promoting body is formed in a shape in which a flow direction of a fluid flowing in the fluid passage is directed to a wall surface of the fluid passage. 前記伝熱促進体は、前記流体通路を流れる流体の流速を流体の流れ方向に沿った前記流体通路の各部において略均一にするような密度で形成されていることを特徴とする請求項１又は２記載の熱交換器。   2. The heat transfer promoting body is formed at a density that makes the flow velocity of the fluid flowing through the fluid passage substantially uniform in each part of the fluid passage along the fluid flow direction. 2. The heat exchanger according to 2. 前記伝熱促進体は、２枚の前記プレートのそれぞれに形成されていることを特徴とする請求項１ないし３のいずれか一項に記載の熱交換器。   The heat exchanger according to any one of claims 1 to 3, wherein the heat transfer promoting body is formed on each of the two plates. ２枚の前記プレートにそれぞれ形成された前記伝熱促進体は、位置をずらして対向していることを特徴とする請求項４記載の熱交換器。   5. The heat exchanger according to claim 4, wherein the heat transfer promoting bodies respectively formed on the two plates are opposed to each other while being shifted in position.
JP2009076377A 2009-03-26 2009-03-26 Heat exchanger Pending JP2010230213A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013105487A1 (en) * 2012-01-13 2013-07-18 パナソニック株式会社 Heat exchanger
EP2706320A3 (en) * 2012-09-10 2014-09-10 FTAS GmbH Tube heat exchanger

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013105487A1 (en) * 2012-01-13 2013-07-18 パナソニック株式会社 Heat exchanger
EP2706320A3 (en) * 2012-09-10 2014-09-10 FTAS GmbH Tube heat exchanger

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