JP2004278807A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
JP2004278807A
JP2004278807A JP2003066602A JP2003066602A JP2004278807A JP 2004278807 A JP2004278807 A JP 2004278807A JP 2003066602 A JP2003066602 A JP 2003066602A JP 2003066602 A JP2003066602 A JP 2003066602A JP 2004278807 A JP2004278807 A JP 2004278807A
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Japan
Prior art keywords
tube
heat exchanger
refrigerant
fluid
meandering
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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.)
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JP2003066602A
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Japanese (ja)
Inventor
Koichi Nakashita
功一 中下
Ken Yamamoto
山本　　憲
Norihide Kawachi
典秀 河地
Takeshi Okinoya
剛 沖ノ谷
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Denso Corp
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Denso Corp
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Publication date
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Priority to JP2003066602A priority Critical patent/JP2004278807A/en
Publication of JP2004278807A publication Critical patent/JP2004278807A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0016—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • 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
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of reducing a head loss of hot water to be supplied generated in the heat exchanger. <P>SOLUTION: The heat exchanger is structured so that a plurality of partitioning members 23 are stacked in the thickness direction of outer plates 22 (in the vertical direction to the sheet surface) in the space formed between the two outer plates 22. Thereby a plurality rows of meandering paths 24 overlapping in the thickness direction of the outer plates 22 can be formed in the mentioned space, and it is possible to reduce the head loss by enlarging the passage section area of the meandering paths 24 without dropping the ratio (=S/Q) of the heat conduction area S of the hot water passage to the supplied water quantity Q i.e. the meandering paths to the supplied hot water. As a result, the heat exchanger path with refrigerant can be prolonged without enlarging the outside dimensions of the water-refrigerant heat exchanger 20. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、流体が内部で蛇行するとともに、少なくとも一方の断面形状が略凹（バスタブ）状にプレス成形された２枚の外板を接合することによって構成されたチューブを有する熱交換器に関するもので、給湯水を加熱するための加熱用熱交換器の水チューブに適用して有効である。
【０００２】
【従来の技術発明が解決しようとする課題】
給湯水と冷媒とを熱交換するヒートポンプ式給湯器用の熱交換器として、発明者は、断面形状が略凹（バスタブ）状にプレス成形された２枚の外板を接合するとともに、２枚の外板間で構成された空間を仕切板で仕切ることにより給湯水通路を蛇行させた水側チューブと細管状の冷媒側チューブとを接合して、給湯水と冷媒とが対向流状態で熱交換するものを開発検討した。
【０００３】
しかし、上記開発品では、給湯水通路を何度（例えば、１００回）も転向させることにより給湯水通路を蛇行路として、熱交換器の外形寸法を大きくすることなく、冷媒との熱交換経路を長くしているので、給湯水通路で発生する圧力損失が大きくなる易いという問題を有している。
【０００４】
本発明は、上記点に鑑み、第１には、従来と異なる新規な熱交換器を提供し、第２には、熱交換器内で発生する圧力損失を低減することを目的とする。
【０００５】
【課題を解決するための手段】
本発明は、上記目的を達成するために、請求項１に記載の発明では、流体が内部で蛇行するとともに、少なくとも一方の断面形状が略凹状にプレス成形された２枚の外板（２２）を接合することによって構成された第１チューブ（２１）と、２枚の外板（２２）間に形成された空間内に配置され、空間内を仕切るようにして流体が流れる蛇行路（２４）を構成する複数枚の仕切部材（２３）と、外板（２２）に接合され、第１チューブ（２１）内を流れる流体と熱交換する流体が流れる第２チューブ（２６）とを備え、複数枚の仕切部材（２３）は、空間内において、外板（２２）の厚み方向に積層されていることを特徴とする。
【０００６】
これにより、前記空間内において、外板（２２）の厚み方向に重なった複数列の蛇行路（２４）が形成され得ることとなる。
【０００７】
したがって、流量（Ｑ）に対する蛇行路（２４）と流体との伝熱面積（Ｓ）との比（＝Ｓ／Ｑ）を低下させることなく、蛇行路（２４）の通路断面積を大きくして圧力損失を低減できるので、熱交換器の外形寸法を大きくすることなく、流体との熱交換経路を長くすることができる。
【０００８】
請求項２に記載の発明では、流体が内部で蛇行するとともに、少なくとも一方の断面形状が略凹状にプレス成形された２枚の外板（２２）を接合することによって構成された第１チューブ（２１）と、２枚の外板（２２）間に形成された空間内に配置され、空間内を仕切るようにして流体が流れる蛇行路（２４）を構成する仕切部材（２３）と、外板（２２）に接合され、第１チューブ（２１）内を流れる流体と熱交換する流体が流れる第２チューブ（２６）とを備え、仕切部材（２３）は、空間内において、外板（２２）の厚み方向に重なった複数列の蛇行路（２４）が形成されるような形状に成形されていることを特徴とする。
【０００９】
これにより、請求項１に記載の発明と同様に、流量（Ｑ）に対する蛇行路（２４）と流体との伝熱面積（Ｓ）との比（＝Ｓ／Ｑ）を低下させることなく、蛇行路（２４）の通路断面積を大きくして圧力損失を低減できるので、熱交換器の外形寸法を大きくすることなく、流体との熱交換経路を長くすることができる。
【００１０】
請求項３に記載の発明では、流体が内部で蛇行するとともに、少なくとも一方の断面形状が略凹状にプレス成形された２枚の外板（２２）を接合することによって構成された第１チューブ（２１）と、２枚の外板（２２）間に形成された空間内に配置され、空間内を仕切るようにして流体が流れる蛇行路（２４）を構成する仕切部材（２３）と、外板（２２）に接合され、第１チューブ（２１）内を流れる流体と熱交換する流体が流れる第２チューブ（２６）とを備えることを特徴とするものである。
【００１１】
請求項４に記載の発明では、第２チューブ（２６）は、第１チューブ（２１）周りにコイル状に巻き付けられた状態で外板（２２）に接合されていることを特徴とするものである。
【００１２】
因みに、上記各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示す一例である。
【００１３】
【発明の実施の形態】
（第１実施形態）
本実施形態は、給湯水を加熱するための加熱用熱交換器の水チューブに本発明を適用したものであって、図１はヒートポンプ式給湯器であり、図２は本実施形態に係るチューブを用いた給湯水と冷媒と熱交換する水冷媒熱交換器２０の外形斜視図である。なお、本実施形態では、冷媒として二酸化炭素を用いている。
【００１４】
因みに、ヒートポンプ式給湯器とは、ヒートポンプ式給湯器は、図１に示すように、冷媒を吸入圧縮する圧縮機１０、水冷媒熱交換器２０、水冷媒熱交換器２０から流出した冷媒を減圧する減圧器３０、外気から吸熱して冷媒を蒸発させる蒸発器４０、及び蒸発器４０から流出した冷媒を液相冷媒と気相冷媒とに分離して余剰冷媒を液相冷媒として蓄えるとともに、気相冷媒を圧縮機１０に供給する気液分離器５０等から構成されたもので、外気から吸熱した熱及び圧縮機１０の圧縮仕事量に相当する熱量を給湯水に与えることにより給湯水を加熱する。
【００１５】
次に、水冷媒熱交換器２０の構造について述べる。
【００１６】
水冷媒熱交換器２０の水側チューブ２１は、図３に示すように、断面形状が略凹（バスタブ）状にプレス成形された２枚の外板２２を接合するとともに、図４に示すように、２枚の外板２２間で構成された空間を複数枚の仕切部材２３で仕切ることにより蛇行した給湯水通路、つまり蛇行路２４を構成したもので、本実施形態では、外板２２及び仕切部材２３を耐食性に優れた金属（例えば、銅やステンレス）製として、これらをろう接にて接合している。
【００１７】
そして、本実施形態では、図３に示すように、２枚の外板２２間で構成された空間内において、複数枚の仕切部材２３を外板２２の厚み方向（紙面上下方向）に積層することにより、前記空間内において、外板２２の厚み方向に重なった複数列の蛇行路２４を形成している。
【００１８】
なお、「ろう接」とは、例えば「接続・接合技術」（東京電機大学出版局）に記載されているように、ろう材やはんだを用いて母材を溶融させないように接合する技術を言う。因みに、融点が４５０℃以上の溶加材を用いて接合するときをろう付けと言い、その際の溶加材をろう材と呼び、融点が４５０℃以下の溶加材を用いて接合するときをはんだ付けと言い、その際の溶加材をはんだと呼ぶ。
【００１９】
因みに、本実施形態では、外板２２及び仕切部材２３の厚みを共に約０．５ｍｍとし、両者２２、２３は箔状のりん銅溶加材にろう接され、外板２２同士も箔状のりん銅溶加材にろう接されているが、例えば棒状の溶加材を所定箇所に配置してもよい。
【００２０】
また、仕切部材２３は、図５に示すように、板材を略矩形波状にプレス成形することにより、蛇行路２４の一部を構成する複数本の溝部２４ａを形成したもので、隣り合う溝部２４ａは、連通路２４ｂを介して連通する。
【００２１】
因みに、本実施形態では、仕切部材２３を金属製とすることにより、給湯水と水側チューブ２１との伝熱面積を増大させるフィンとして効果も担っている。
【００２２】
ところで、本実施形態では、圧縮機１０の吐出圧を冷媒の臨界圧力以上としているので、水冷媒熱交換器２０に冷媒と給湯水とが熱交換する際に、冷媒は凝縮することなく、冷媒温度を低下させながらそのエンタルピを低下させることから、図２に示すように、冷媒の流れと給湯水の流れとが対向流れとなるように、複数本（本実施形態では、３本）の細管状冷媒チューブ２６を束ねて１本とし、その束ねた冷媒チューブ２６を水側チューブ２１周りにコイル状に巻き付けた状態で外板２２にろう接している。
【００２３】
なお、本実施形態では、冷媒チューブ２６をりん脱酸銅をローラ成形機にてコイル状に成形したものであり、りん銅の溶加材にて水側チューブ２１、つまり外板２２にろう接している。
【００２４】
次に、本実施形態の作用効果を述べる。
【００２５】
本実施形態では、２枚の外板２２間で構成された空間内において、複数枚の仕切部材２３を外板２２の厚み方向（紙面上下方向）に積層しているので、前述のごとく、前記空間内において、外板２２の厚み方向に重なった複数列の蛇行路２４が形成されることとなる。
【００２６】
したがって、給水量（Ｑ）に対する給湯水通路、つまり蛇行路２４と給湯水との伝熱面積（Ｓ）との比（＝Ｓ／Ｑ）を低下させることなく、蛇行路２４の通路断面積を大きくして圧力損失を低減できるので、水冷媒熱交換器２０の外形寸法を大きくすることなく、冷媒との熱交換経路を長くすることができる。
【００２７】
（第２実施形態）
第１実施形態では、仕切部材２３を矩形波状にプレス成形したが、本実施形態は、図６に示すように、仕切部材２３を正弦波状にプレス成形したものである。
【００２８】
なお、本実施形態では、２枚の外板２２間で構成された空間内において、外板２２の厚み方向に重なった複数列の蛇行路２４は、第１実施形態ほど、厳密に区画されていない。
【００２９】
（第３実施形態）
上述の実施形態では、２枚の外板２２間で構成された空間内において、２枚の仕切部材２３にて外板２２の厚み方向に重なった複数列の蛇行路２４を形成したが、本実施形態は、図７に示すように、１枚の仕切部材２３にて外板２２の厚み方向に重なった複数列の蛇行路２４を形成したものである。
【００３０】
（第４実施形態）
上述の実施形態では、２枚の外板２２間で構成された空間内において、外板２２の厚み方向に重なった複数列の蛇行路２４を形成したが、本実施形態は、図８に示すように、外板２２の厚み方向に重なった複数列の蛇行路２４を設けることなく、蛇行路２４を１列としたものである。
【００３１】
そして、本実施形態においても、１列の蛇行路２４の通路断面積を十分に大きくすれば、圧力損失を十分に小さくすることができる。
【００３２】
（第５実施形態）
上述の実施形態では、冷媒チューブ２６を水側チューブ２１にコイル状に巻き付けたが、本実施形態は、図９に示すように、冷媒チューブ２６を蛇行路２４の進行方向（図９の上下方向）に延びる細管状としたものである。
【００３３】
なお、複数本の冷媒チューブ２６の長手方向両端側には、これら冷媒チューブ２６と連通する冷媒タンク２７が設けられており、給湯水の出口側（紙面上側）に設けられた冷媒タンク２７は、複数本の冷媒チューブ２６に冷媒を分配供給するもので、給湯水の入口側（紙面下側）に設けられた冷媒タンク２７は、複数本の冷媒チューブ２６から流出した冷媒を集合回収するものである。
【００３４】
（その他の実施形態）
第１、２実施形態では、２枚の外板２２間で構成された空間内において、２枚の仕切部材２３にて外板２２の厚み方向に重なった複数列の蛇行路２４を形成したが、本実施形態はこれに限定されるものではなく、例えば３枚以上の仕切部材２３にて外板２２の厚み方向に重なった複数列の蛇行路２４を形成してもよい。
【００３５】
上述の実施形態では、板材に矩形波状にプレス成形を施すことにより仕切部材２３を形成したが、本発明はこれに限定されるものではなく、例えばコの字状断面又は目の字状断面を有す押し出し又は引き抜き材にて仕切部材２３を形成してもよい。
【００３６】
また、上述の実施形態では、２枚の外板２２を共にバスタブ状としたが、本発明はこれに限定されるものではなく、例えば一方側の外板２２のバスタブ状とし、他方側を平板状としてもよい。
【００３７】
また、上述実施形態では、冷媒と給湯水とを熱交換する水冷媒熱交換器２０の水側チューブ２１に本発明を適用したが、本発明の適用はこれに限定されるものではない。
【図面の簡単な説明】
【図１】本発明の実施形態に係るヒートポンプ式給湯器の模式図である。
【図２】本発明の第１実施形態に係る水冷媒熱交換器の外形斜視図である。
【図３】本発明の第１実施形態に係る水側チューブの断面図である。
【図４】本発明の第１実施形態に係る水側チューブの概念図である。
【図５】本発明の第１実施形態に係る仕切部材の斜視図である。
【図６】本発明の第２実施形態に係る水側チューブの断面図である。
【図７】本発明の第２実施形態に係る水側チューブの断面図である。
【図８】本発明の第３実施形態に係る水冷媒熱交換器の外形斜視図である。
【図９】本発明の第３実施形態に係る水冷媒熱交換器の外形斜視図である。
【符号の説明】
２１…チューブ、２２…外板、２３…仕切部材、２６…冷媒チューブ。[0001]
TECHNICAL FIELD OF THE INVENTION
TECHNICAL FIELD The present invention relates to a heat exchanger having a tube formed by joining two outer plates that are formed by pressurizing a fluid in a meandering inside and at least one of the cross-sectional shapes of at least one of them into a substantially concave (bathtub) shape. This is effective when applied to a water tube of a heating heat exchanger for heating hot water.
[0002]
[Problems to be solved by the prior art invention]
As a heat exchanger for a heat pump type water heater for exchanging heat between hot water and a refrigerant, the inventor joined two outer plates press-formed in a substantially concave (bathtub) cross section and joined two outer plates. The space formed between the outer plates is partitioned by a partition plate to join the water-side tube and the thin-walled refrigerant-side tube meandering in the hot-water supply passage, so that the hot-water supply and the refrigerant exchange heat in a counterflow state. We studied what to do.
[0003]
However, in the above-mentioned developed product, the hot water passage is turned many times (for example, 100 times) so that the hot water passage becomes a meandering path, and the heat exchange path with the refrigerant is increased without increasing the external dimensions of the heat exchanger. Therefore, there is a problem that the pressure loss generated in the hot water supply passage is likely to be large.
[0004]
In view of the above points, the present invention firstly provides a new heat exchanger different from the conventional one, and secondly, aims to reduce a pressure loss generated in the heat exchanger.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, according to the first aspect of the present invention, a fluid meanders inside, and at least one of the two outer plates (22) press-formed in a substantially concave cross section. Meandering path (24), which is disposed in a space formed between a first tube (21) formed by joining the first and second outer plates (22) and partitions the space, through which a fluid flows. And a second tube (26) joined to the outer plate (22) and through which a fluid that exchanges heat with a fluid flowing through the first tube (21) flows. The partition members (23) are stacked in the thickness direction of the outer plate (22) in the space.
[0006]
Thereby, a plurality of rows of meandering paths (24) overlapping in the thickness direction of the outer plate (22) can be formed in the space.
[0007]
Therefore, the passage cross-sectional area of the meandering path (24) can be increased without decreasing the ratio (= S / Q) of the meandering path (24) to the heat transfer area (S) with respect to the flow rate (Q). Since the pressure loss can be reduced, the heat exchange path with the fluid can be lengthened without increasing the external dimensions of the heat exchanger.
[0008]
According to the second aspect of the present invention, the fluid is meandered inside, and at least one of the first tubes (22) is formed by joining two outer plates (22) press-formed in a substantially concave cross section. 21) a partition member (23) disposed in a space formed between the two outer plates (22) and forming a meandering path (24) through which a fluid flows so as to partition the space; A second tube (26) joined to the first tube (21) and through which a fluid that exchanges heat with the fluid flowing through the first tube (21) flows, and the partition member (23) is provided with an outer plate (22) Is formed in such a shape that a plurality of rows of meandering paths (24) overlapping in the thickness direction are formed.
[0009]
Accordingly, the meandering path (24) and the ratio of the heat transfer area (S) of the fluid to the meandering path (S) to the flow rate (Q) (= S / Q) are reduced, as in the first aspect of the present invention. Since the pressure loss can be reduced by increasing the passage cross-sectional area of the passage (24), the heat exchange path with the fluid can be lengthened without increasing the external dimensions of the heat exchanger.
[0010]
According to the third aspect of the present invention, the fluid is meandered inside, and at least one of the first tubes (22) is formed by joining two outer plates (22) that are press-formed in a substantially concave cross section. 21) a partition member (23) disposed in a space formed between the two outer plates (22) and forming a meandering path (24) through which a fluid flows so as to partition the space; And a second tube (26) joined to the first tube (21) and through which a fluid that exchanges heat with a fluid that flows in the first tube (21) flows.
[0011]
According to a fourth aspect of the present invention, the second tube (26) is joined to the outer plate (22) while being wound in a coil shape around the first tube (21). is there.
[0012]
Incidentally, reference numerals in parentheses of the above-mentioned units are examples showing the correspondence with specific units described in the embodiments described later.
[0013]
BEST MODE FOR CARRYING OUT THE INVENTION
(1st Embodiment)
In the present embodiment, the present invention is applied to a water tube of a heating heat exchanger for heating hot water, FIG. 1 shows a heat pump water heater, and FIG. 2 shows a tube according to the present embodiment. FIG. 3 is an external perspective view of a water-refrigerant heat exchanger 20 that performs heat exchange between hot water and a refrigerant using the water. In the present embodiment, carbon dioxide is used as the refrigerant.
[0014]
As shown in FIG. 1, the heat pump water heater is a compressor that sucks and compresses a refrigerant, a water refrigerant heat exchanger 20, and a pressure reducing refrigerant flowing out of the water refrigerant heat exchanger 20, as shown in FIG. A decompressor 30, an evaporator 40 that absorbs heat from the outside air to evaporate the refrigerant, and separates the refrigerant flowing out of the evaporator 40 into a liquid-phase refrigerant and a gas-phase refrigerant to store excess refrigerant as a liquid-phase refrigerant. A gas-liquid separator 50 for supplying a phase refrigerant to the compressor 10 and the like. The hot water is heated by giving the heat absorbed from the outside air and the heat corresponding to the compression work of the compressor 10 to the hot water. I do.
[0015]
Next, the structure of the water-refrigerant heat exchanger 20 will be described.
[0016]
As shown in FIG. 3, the water-side tube 21 of the water-refrigerant heat exchanger 20 joins two outer plates 22 each having a substantially concave (bathtub) cross-section, and as shown in FIG. 4. A meandering hot water path, that is, a meandering path 24 is formed by partitioning a space formed between the two outer plates 22 with a plurality of partition members 23. In the present embodiment, the outer plate 22 and the The partition member 23 is made of a metal having excellent corrosion resistance (for example, copper or stainless steel), and these are joined by brazing.
[0017]
In the present embodiment, as shown in FIG. 3, a plurality of partition members 23 are stacked in the thickness direction of the outer plate 22 (vertical direction on the paper) in a space formed between the two outer plates 22. Thereby, a plurality of rows of meandering paths 24 overlapping in the thickness direction of the outer plate 22 are formed in the space.
[0018]
The term “brazing” refers to a technique for joining a base material using a brazing material or solder so as not to be melted, as described in, for example, “Connection and Joining Technology” (Tokyo Denki University Press). . By the way, when joining using a filler material with a melting point of 450 ° C or more, it is called brazing, and the filler material at that time is called a brazing material, and when joining using a filler material with a melting point of 450 ° C or less. Is called soldering, and the filler material at that time is called solder.
[0019]
By the way, in the present embodiment, the thickness of both the outer plate 22 and the partition member 23 is about 0.5 mm, the two 22 and 23 are brazed to the foil-like phosphor copper filler material, and the outer plates 22 are also foil-like. Although it is brazed to the phosphor copper filler metal, for example, a rod-shaped filler material may be arranged at a predetermined position.
[0020]
As shown in FIG. 5, the partition member 23 is formed by pressing a plate material into a substantially rectangular wave shape to form a plurality of grooves 24a constituting a part of the meandering path 24. Communicate with each other through the communication passage 24b.
[0021]
By the way, in the present embodiment, the partition member 23 is made of metal, which also serves as a fin that increases the heat transfer area between the hot water and the water side tube 21.
[0022]
By the way, in the present embodiment, since the discharge pressure of the compressor 10 is equal to or higher than the critical pressure of the refrigerant, when the refrigerant exchanges heat with the hot water in the water-refrigerant heat exchanger 20, the refrigerant is not condensed, and the refrigerant is not condensed. Since the enthalpy is lowered while lowering the temperature, as shown in FIG. 2, a plurality of (three in this embodiment) thin tubes are set so that the flow of the refrigerant and the flow of the hot water flow in opposite directions. The refrigerant tubes 26 are bundled into one, and the bundled refrigerant tubes 26 are wound around the water-side tube 21 in a coil shape and brazed to the outer plate 22.
[0023]
In the present embodiment, the refrigerant tube 26 is formed by coiling phosphorous deoxidized copper into a coil by a roller forming machine, and is brazed to the water side tube 21, that is, the outer plate 22 with a filler material of phosphorous copper. ing.
[0024]
Next, the operation and effect of the present embodiment will be described.
[0025]
In the present embodiment, a plurality of partition members 23 are stacked in the thickness direction of the outer plate 22 (vertical direction on the paper) in the space formed between the two outer plates 22. In the space, a plurality of rows of meandering paths 24 overlapping in the thickness direction of the outer plate 22 are formed.
[0026]
Therefore, without decreasing the ratio (= S / Q) of the hot water supply passage to the water supply amount (Q), that is, the ratio of the heat transfer area (S) between the meandering passage 24 and the hot water, the passage cross-sectional area of the meandering passage 24 is reduced. Since the pressure loss can be reduced by increasing the size, the heat exchange path with the refrigerant can be lengthened without increasing the external dimensions of the water-refrigerant heat exchanger 20.
[0027]
(2nd Embodiment)
In the first embodiment, the partition member 23 is press-formed in a rectangular wave shape, but in the present embodiment, as shown in FIG. 6, the partition member 23 is press-formed in a sine wave shape.
[0028]
In the present embodiment, in the space formed between the two outer plates 22, the meandering paths 24 in a plurality of rows overlapping in the thickness direction of the outer plates 22 are strictly partitioned as in the first embodiment. Absent.
[0029]
(Third embodiment)
In the above-described embodiment, a plurality of rows of meandering paths 24 overlapping in the thickness direction of the outer plate 22 are formed by the two partition members 23 in the space formed between the two outer plates 22. In the embodiment, as shown in FIG. 7, a plurality of rows of meandering paths 24 overlapping in the thickness direction of the outer plate 22 are formed by one partition member 23.
[0030]
(Fourth embodiment)
In the above-described embodiment, a plurality of rows of meandering paths 24 overlapping in the thickness direction of the outer plate 22 are formed in the space formed between the two outer plates 22, but this embodiment is shown in FIG. As described above, the meandering paths 24 are arranged in one row without providing the plurality of rows of the meandering paths 24 overlapping in the thickness direction of the outer plate 22.
[0031]
And also in this embodiment, if the passage cross-sectional area of the one-line meandering path 24 is made sufficiently large, the pressure loss can be made sufficiently small.
[0032]
(Fifth embodiment)
In the above-described embodiment, the refrigerant tube 26 is wound around the water-side tube 21 in a coil shape. However, in this embodiment, as shown in FIG. 9, the refrigerant tube 26 is moved in the traveling direction of the meandering path 24 (the vertical direction in FIG. 9). ).
[0033]
A refrigerant tank 27 communicating with the refrigerant tubes 26 is provided at both ends in the longitudinal direction of the plurality of refrigerant tubes 26. The refrigerant tank 27 provided on the outlet side (upper side of the paper) of the hot water supply is The refrigerant is distributed and supplied to the plurality of refrigerant tubes 26, and the refrigerant tank 27 provided on the inlet side (lower side of the paper) of the hot water collects and collects the refrigerant flowing out of the plurality of refrigerant tubes 26. is there.
[0034]
(Other embodiments)
In the first and second embodiments, a plurality of rows of meandering paths 24 overlapping in the thickness direction of the outer plate 22 are formed by the two partition members 23 in the space formed between the two outer plates 22. However, the present embodiment is not limited to this. For example, a plurality of rows of meandering paths 24 overlapping in the thickness direction of the outer plate 22 may be formed by three or more partition members 23.
[0035]
In the above-described embodiment, the partition member 23 is formed by applying a rectangular wave shape to the plate material, but the present invention is not limited to this. For example, a U-shaped cross section or an eye-shaped cross section may be used. The partition member 23 may be formed of an extruded or drawn material.
[0036]
In the above-described embodiment, both of the two outer plates 22 have a bathtub shape. However, the present invention is not limited to this. For example, one outer plate 22 has a bathtub shape and the other side has a flat plate shape. It is good also as a shape.
[0037]
In the above-described embodiment, the present invention is applied to the water-side tube 21 of the water-refrigerant heat exchanger 20 that exchanges heat between the refrigerant and the hot water, but the application of the present invention is not limited to this.
[Brief description of the drawings]
FIG. 1 is a schematic diagram of a heat pump water heater according to an embodiment of the present invention.
FIG. 2 is an external perspective view of the water-refrigerant heat exchanger according to the first embodiment of the present invention.
FIG. 3 is a sectional view of a water-side tube according to the first embodiment of the present invention.
FIG. 4 is a conceptual diagram of a water side tube according to the first embodiment of the present invention.
FIG. 5 is a perspective view of a partition member according to the first embodiment of the present invention.
FIG. 6 is a sectional view of a water side tube according to a second embodiment of the present invention.
FIG. 7 is a sectional view of a water side tube according to a second embodiment of the present invention.
FIG. 8 is an external perspective view of a water-refrigerant heat exchanger according to a third embodiment of the present invention.
FIG. 9 is an external perspective view of a water-refrigerant heat exchanger according to a third embodiment of the present invention.
[Explanation of symbols]
21: tube, 22: outer plate, 23: partition member, 26: refrigerant tube.

Claims (4)

流体が内部で蛇行するとともに、少なくとも一方の断面形状が略凹状にプレス成形された２枚の外板（２２）を接合することによって構成された第１チューブ（２１）と、
前記２枚の外板（２２）間に形成された空間内に配置され、前記空間内を仕切るようにして流体が流れる蛇行路（２４）を構成する複数枚の仕切部材（２３）と、
前記外板（２２）に接合され、前記第１チューブ（２１）内を流れる流体と熱交換する流体が流れる第２チューブ（２６）とを備え、
前記複数枚の仕切部材（２３）は、前記空間内において、前記外板（２２）の厚み方向に積層されていることを特徴とする熱交換器。A first tube (21) formed by joining two outer plates (22) each having a fluid meandering inside and at least one of the cross-sectional shapes pressed into a substantially concave shape;
A plurality of partition members (23) arranged in a space formed between the two outer plates (22) and forming a meandering path (24) through which a fluid flows so as to partition the space;
A second tube (26) joined to the outer plate (22) and through which a fluid that exchanges heat with a fluid flowing through the first tube (21) flows;
The heat exchanger, wherein the plurality of partition members (23) are stacked in the space in the thickness direction of the outer plate (22). 流体が内部で蛇行するとともに、少なくとも一方の断面形状が略凹状にプレス成形された２枚の外板（２２）を接合することによって構成された第１チューブ（２１）と、
前記２枚の外板（２２）間に形成された空間内に配置され、前記空間内を仕切るようにして流体が流れる蛇行路（２４）を構成する仕切部材（２３）と、
前記外板（２２）に接合され、前記第１チューブ（２１）内を流れる流体と熱交換する流体が流れる第２チューブ（２６）とを備え、
前記仕切部材（２３）は、前記空間内において、前記外板（２２）の厚み方向に重なった複数列の前記蛇行路（２４）が形成されるような形状に成形されていることを特徴とする熱交換器。A first tube (21) formed by joining two outer plates (22) each having a fluid meandering inside and at least one of the cross-sectional shapes pressed into a substantially concave shape;
A partition member (23) arranged in a space formed between the two outer plates (22) and forming a meandering path (24) through which a fluid flows so as to partition the space;
A second tube (26) joined to the outer plate (22) and through which a fluid that exchanges heat with a fluid flowing through the first tube (21) flows;
The partition member (23) is formed in a shape such that a plurality of rows of the meandering paths (24) overlapping in the thickness direction of the outer plate (22) are formed in the space. Heat exchanger. 流体が内部で蛇行するとともに、少なくとも一方の断面形状が略凹状にプレス成形された２枚の外板（２２）を接合することによって構成された第１チューブ（２１）と、
前記２枚の外板（２２）間に形成された空間内に配置され、前記空間内を仕切るようにして流体が流れる蛇行路（２４）を構成する仕切部材（２３）と、
前記外板（２２）に接合され、前記第１チューブ（２１）内を流れる流体と熱交換する流体が流れる第２チューブ（２６）とを備えることを特徴とする熱交換器。A first tube (21) formed by joining two outer plates (22) each having a fluid meandering inside and at least one of the cross-sectional shapes pressed into a substantially concave shape;
A partition member (23) arranged in a space formed between the two outer plates (22) and forming a meandering path (24) through which a fluid flows so as to partition the space;
A heat exchanger, comprising: a second tube (26) joined to the outer plate (22) and through which a fluid that exchanges heat with a fluid flowing through the first tube (21) flows. 前記第２チューブ（２６）は、前記第１チューブ（２１）周りにコイル状に巻き付けられた状態で前記外板（２２）に接合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１つに記載の熱交換器。The said 2nd tube (26) is joined to the said outer plate (22) in the state wound around the said 1st tube (21) in coil shape, The Claim 1 characterized by the above-mentioned. A heat exchanger according to one.
JP2003066602A 2003-03-12 2003-03-12 Heat exchanger Withdrawn JP2004278807A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008202846A (en) * 2007-02-20 2008-09-04 Usui Kokusai Sangyo Kaisha Ltd Heat transfer tube for heat exchanger and egr gas cooling device using the same
JP2011127865A (en) * 2009-12-21 2011-06-30 Fujitsu General Ltd Heat exchanger

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008202846A (en) * 2007-02-20 2008-09-04 Usui Kokusai Sangyo Kaisha Ltd Heat transfer tube for heat exchanger and egr gas cooling device using the same
JP2011127865A (en) * 2009-12-21 2011-06-30 Fujitsu General Ltd Heat exchanger

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