JP2005315520A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
JP2005315520A
JP2005315520A JP2004134423A JP2004134423A JP2005315520A JP 2005315520 A JP2005315520 A JP 2005315520A JP 2004134423 A JP2004134423 A JP 2004134423A JP 2004134423 A JP2004134423 A JP 2004134423A JP 2005315520 A JP2005315520 A JP 2005315520A
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Prior art keywords
heat exchanger
fin
heat
tubes
tube
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JP2004134423A
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JP4211671B2 (en
Inventor
Hiroyuki Osakabe
長賀部　　博之
Shigeki Okochi
大河内　　隆樹
Toshihide Ninagawa
蜷川　　稔英
Hiroyuki Genta
啓之 現田
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Denso Corp
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Denso Corp
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Priority to JP2004134423A priority Critical patent/JP4211671B2/en
Priority to DE102005018312A priority patent/DE102005018312A1/en
Publication of JP2005315520A publication Critical patent/JP2005315520A/en
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    • 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
    • F28F13/04—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by preventing the formation of continuous films of condensate on heat-exchange surfaces, e.g. by promoting droplet formation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H8/00—Fluid heaters characterised by means for extracting latent heat from flue gases by means of condensation
    • F24H8/006—Means for removing condensate from the heater
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/40—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Instantaneous Water Boilers, Portable Hot-Water Supply Apparatuses, And Control Of Portable Hot-Water Supply Apparatuses (AREA)
  • Details Of Fluid Heaters (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of suppressing condensed water produced in heat exchanging to be clogged at the lower end part of fins. <P>SOLUTION: This heat exchanger comprises a plurality of tubes 110 in which fluid passages are formed and disposed so as to be stacked on each other and the fins 120 interposed between the plurality of tubes 110 and increasing a heat transfer area. A high temperature gas including steam flows from the upper side to the lower side in the area of the fins 120, a low temperature fluid lower in temperature than the high temperature gas is allowed to flow in the fluid passages of the tubes 110 to recover not only latent heat but also condensing latent heat from the high temperature gas so as to heat the low temperature fluid. Extension parts 121 extended downward in the state of non-contact with the surface of the tubes 110 are formed on the high temperature gas side of the fins 120, and projected parts 122 and 123 projecting from the surfaces of the fins 120 are formed on the extended parts 121. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、チューブ内を流通する流体とチューブ間に介在されるフィン領域を流通する高温の気体との間で熱交換を行う熱交換器に関するものであり、給湯器用の熱交換器に用いて好適である。   The present invention relates to a heat exchanger that performs heat exchange between a fluid flowing in a tube and a high-temperature gas flowing in a fin region interposed between the tubes, and is used for a heat exchanger for a water heater. Is preferred.

従来の熱交換器として、例えば、特許文献１に示されるものが知られている（図１２、図１３）。即ち、この熱交換器は、複数積層されるチューブ１１０の間にフィン１２０が介在されており、チューブ１１０内を流通する流体と、フィン１２０の配置される領域を上方から下方に向かって流れる燃焼ガスとの間で熱交換を行うものとしている。   As a conventional heat exchanger, for example, the one shown in Patent Document 1 is known (FIGS. 12 and 13). That is, in this heat exchanger, fins 120 are interposed between a plurality of stacked tubes 110, and a fluid that flows through the tubes 110 and a combustion that flows from above to below in a region where the fins 120 are disposed. Heat is exchanged with gas.

ここでは、チューブ１１０の表面に突起部を設け、この突起部が燃焼ガスの流通方向に隙間δを持って離散的に並ぶようにしている。具体的には、例えばフィン１２０をオフセットフィンとし、上記突起部を千鳥配置されるセグメント１２４で形成するようにしている。   Here, protrusions are provided on the surface of the tube 110, and these protrusions are arranged in a discrete manner with gaps δ in the flow direction of the combustion gas. Specifically, for example, the fins 120 are offset fins, and the protrusions are formed by segments 124 arranged in a staggered manner.

これにより、熱交換時に燃焼ガスから生成される凝縮水の膜が、隙間δによって細かく分断されるので、セグメント１２４に付着した凝縮水の膜厚が大きくなるのを防止して、凝縮水による熱抵抗の増大を抑制するようにしている。
特開２００２−１１５９１６号公報 As a result, the film of condensed water generated from the combustion gas during heat exchange is finely divided by the gap δ, so that the film thickness of the condensed water adhering to the segment 124 is prevented from increasing, and the heat generated by the condensed water is prevented. The increase in resistance is suppressed.
JP 2002-115916 A

しかしながら、フィン１２０は、チューブ１１０表面の平面部を形成する領域内に設けられるようにしているので、フィン１２０から排出されようとする凝縮水は、フィン１２０の下端部から隣接するチューブ１１０の下端部に繋がるように膜を張り（図１２中の下側）、詰まりを起こしやすいという問題があった。   However, since the fin 120 is provided in a region forming a flat portion on the surface of the tube 110, the condensed water to be discharged from the fin 120 is from the lower end of the fin 120 to the lower end of the adjacent tube 110. There was a problem that a film was stretched so as to be connected to the portion (lower side in FIG. 12) and clogging was likely to occur.

本発明の目的は、上記問題に鑑み、フィンの下端部において熱交換時に生成される凝縮水が詰まるのを抑制できる熱交換器を提供することにある。   In view of the above problems, an object of the present invention is to provide a heat exchanger that can suppress clogged condensate generated at the time of heat exchange at the lower end of the fin.

本発明は上記目的を達成するために、以下の技術的手段を採用する。   In order to achieve the above object, the present invention employs the following technical means.

請求項１に記載の発明では、内部に流体通路を形成すると共に、積層配置される複数のチューブ（１１０）と、複数のチューブ（１１０）の間に介在されて、伝熱面積を増大するフィン（１２０）とを備え、フィン（１２０）の領域を上方から下方に向かって水蒸気を含む高温の気体が流れ、チューブ（１１０）の流体通路内に高温の気体より低温となる低温の流体を流通させて、高温の気体から顕熱のみならず凝縮潜熱をも回収して低温の流体を加熱する熱交換器であって、フィン（１２０）の高温の気体の出口側には、チューブ（１１０）の表面と非接触となって下方へ延設される延設部（１２１）が設けられ、且つ、延設部（１２１）には、フィン（１２０）の表面から突出する突出部（１２２、１２３）が設けられたことを特徴としている。   According to the first aspect of the present invention, the fluid passage is formed in the interior, the plurality of tubes (110) arranged in a stack, and the fins interposed between the plurality of tubes (110) to increase the heat transfer area. (120), and a high-temperature gas containing water vapor flows through the fin (120) from the top to the bottom, and a low-temperature fluid having a temperature lower than that of the high-temperature gas flows in the fluid passage of the tube (110). A heat exchanger that collects not only sensible heat but also latent heat of condensation from a high-temperature gas to heat a low-temperature fluid, and a tube (110) is provided at the high-temperature gas outlet side of the fin (120). An extended portion (121) that extends downward in a non-contact manner with the surface of the fin is provided, and the extended portion (121) has a protruding portion (122, 123) that protrudes from the surface of the fin (120). ) There.

これにより、熱交換時にフィン（１２０）の表面で高温の気体から生成される凝縮水は、そのままフィン（１２０）の表面を伝わって流れ落ち、フィン（１２０）の延設部（１２１）に至るので、非接触と成るチューブ（１１０）との間で膜を張ることが無い。   As a result, the condensed water generated from the high-temperature gas on the surface of the fin (120) during heat exchange flows down the surface of the fin (120) as it is, and reaches the extended portion (121) of the fin (120). The membrane is not stretched between the tube (110) which becomes non-contact.

そして、凝縮水は突出部（１２２、１２３）によって、点あるいは線で接触することになるので、延設部（１２１）内での付着、膜張りが抑えられて、スムースに落下していくようになり、凝縮水の詰まりが抑制される。よって、高温の気体の流通抵抗が増大するのを抑えて熱交換効率の悪化を防止することができる。   The condensed water comes into contact with the protrusions (122, 123) at points or lines, so that adhesion and film tension in the extended portion (121) are suppressed, and the condensed water falls smoothly. And clogging of condensed water is suppressed. Therefore, it is possible to prevent the heat exchange efficiency from deteriorating by suppressing an increase in the flow resistance of the high-temperature gas.

そして、請求項１における突出部（１２２、１２３）は、請求項２に記載の発明のように、ルーバ（１２２）として容易に形成することができる。   And the protrusion part (122,123) in Claim 1 can be easily formed as a louver (122) like the invention of Claim 2.

また、突出部（１２２、１２３）は、請求項３に記載の発明のように、フィン（１２０）の表面から切り起こされて形成される切り起こし部（１２３）としても良い。   Further, the protruding portions (122, 123) may be cut and raised portions (123) formed by being cut and raised from the surface of the fin (120), as in the third aspect of the invention.

本熱交換器は、請求項４に記載の発明のように、高温の気体を燃焼ガスとし、また、低温の流体を給湯水として、この給湯水を加熱する給湯器用の熱交換器（１００）に用いて好適である。   As in the invention according to claim 4, the present heat exchanger uses a high-temperature gas as a combustion gas, and uses a low-temperature fluid as a hot-water supply to heat the hot-water supply heat exchanger (100). It is suitable for use.

尚、上記各手段の括弧内の符号は、後述する実施形態記載の具体的手段との対応関係を示すものである。   In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment description mentioned later.

（第１実施形態）
本発明の第１実施形態を図１〜図７に示す図面に基づいて説明する。尚、図１は熱交換器１００を示す側面図、図２は図１のＡ方向から見た矢視図（平面図）、図３は図１のＢ方向から見た矢視図（左側面図）、図４は図３のＣ−Ｃ部における断面図、図５は図４のＤ方向から見た矢視図、図６は燃焼ガス風速に対するコア部１００ａの通風抵抗における本実施形態の効果を示すグラフ、図７は燃焼ガス風速に対するコア部１００ａの熱伝達率における本実施形態の効果を示すグラフである。 (First embodiment)
1st Embodiment of this invention is described based on drawing shown in FIGS. 1 is a side view showing the heat exchanger 100, FIG. 2 is an arrow view (plan view) seen from the direction A in FIG. 1, and FIG. 3 is an arrow view (left side view) seen from the direction B in FIG. 4) is a cross-sectional view taken along the line CC in FIG. 3, FIG. 5 is an arrow view seen from the direction D in FIG. 4, and FIG. 6 is a drawing of the present embodiment in the ventilation resistance of the core 100a against the combustion gas wind speed. FIG. 7 is a graph showing the effect of this embodiment on the heat transfer coefficient of the core portion 100a with respect to the combustion gas wind speed.

本発明の熱交換器１００は、図示しない給湯器に使用されものであり、ケース部材の中に配設される。この熱交換器１００においては、熱交換器１００のコア部１００ａを流通する燃焼ガス（本発明における高温の気体に対応）と、熱交換器１００（チューブ１１０）内を流通する給湯水（本発明における低温の流体に対応）との間で熱交換が行われ、給湯水が加熱されるようになっている。   The heat exchanger 100 of the present invention is used for a water heater (not shown) and is disposed in a case member. In this heat exchanger 100, the combustion gas (corresponding to the high-temperature gas in the present invention) that flows through the core portion 100a of the heat exchanger 100 and the hot-water supply water (the present invention) that flows in the heat exchanger 100 (tube 110). Heat exchange is performed between the hot water supply water and the hot water supply.

因みに、給湯器には１次熱交換器が設けられており、本熱交換器１００は、この１次熱交換器の上側に配置され、２次熱交換器として機能する。即ち、ガスバーナによって発生され、１次熱交換器を通過した後の燃焼ガスがケース部材に導入され、熱交換器１００に供給されるようになっており、また、給湯水は熱交換器１００を流通した後に１次熱交換器に供給されるようになっている。よって、給湯水は、熱交換器１００で予め加熱され、１次熱交換器で更に加熱されて、湯として使用されることに成る。尚、熱交換器１００を流通した燃焼ガスは、ケース部材から給湯器の本体部に設けられたガス排出口から外部へ排出される。   Incidentally, the water heater is provided with a primary heat exchanger, and the present heat exchanger 100 is disposed on the upper side of the primary heat exchanger and functions as a secondary heat exchanger. That is, the combustion gas generated by the gas burner and having passed through the primary heat exchanger is introduced into the case member and supplied to the heat exchanger 100, and hot water is supplied to the heat exchanger 100. After being distributed, it is supplied to the primary heat exchanger. Therefore, the hot water is heated in advance in the heat exchanger 100 and further heated in the primary heat exchanger, and used as hot water. In addition, the combustion gas which distribute | circulated the heat exchanger 100 is discharged | emitted outside from the gas discharge port provided in the main-body part of the water heater from the case member.

熱交換器１００は、図１〜図４に示すように、複数のチューブ１１０をアウターフィン（以下、フィン）１２０と共に積層して構成されるいわゆるドロンカップタイプの熱交換器としている。尚、この熱交換器１００を構成する各部材（以下で説明）は、すべてステンレス系の材料としており、各部材が熱交換器１００の形状に組み立てられた後に、一体的にろう付け接合されている。   As shown in FIGS. 1 to 4, the heat exchanger 100 is a so-called drone cup type heat exchanger configured by stacking a plurality of tubes 110 together with outer fins (hereinafter, fins) 120. Each member (described below) constituting the heat exchanger 100 is made of a stainless steel material, and after the members are assembled in the shape of the heat exchanger 100, they are integrally brazed and joined. Yes.

チューブ１１０は、一対のチューブプレート１１１、１１２から成り、両チューブプレート１１１、１１２の外周部に設けられたフランジ部１１１ａ、１１２ａで互いに当接して接合されている。両チューブプレート１１１、１１２の長手方向の両端側は、中間領域よりも深く絞り加工されており、チューブ１１０として中間領域に扁平管部１１０ａが、両端側にそれぞれ第１タンク部１１０ｂ、第２タンク部１１０ｃが形成されている。   The tube 110 includes a pair of tube plates 111 and 112, and is in contact with and joined to each other by flange portions 111a and 112a provided on the outer peripheral portions of the tube plates 111 and 112. Both end sides in the longitudinal direction of both tube plates 111 and 112 are drawn deeper than the intermediate region. As the tube 110, a flat tube portion 110a is provided in the intermediate region, and a first tank portion 110b and a second tank are provided on both end sides, respectively. A portion 110c is formed.

尚、チューブ２１０の扁平管部２１０ａの内部（本発明における流体通路に対応）には、伝熱面積を増大すると共に内部を流通する給湯水に乱流効果を与える断面凹凸状のインナーフィン１６０（図４）が挿入されている。因みに、このインナーフィンは、凹凸状断面がオフセットされて並ぶように形成されるいわゆるオフセット型フィンとしている。   In addition, in the inside of the flat tube portion 210a of the tube 210 (corresponding to the fluid passage in the present invention), an inner fin 160 having an uneven cross section that increases the heat transfer area and gives a turbulent flow effect to hot water flowing inside the tube 210 ( 4) has been inserted. Incidentally, the inner fin is a so-called offset type fin formed so that the concavo-convex cross-sections are offset and arranged.

そして、複数のチューブ１１０は、第１タンク部１１０ｂ同士、第２タンク部１１０ｃ同士が連通するように積層されている。よって、複数の扁平管部１１０ａは、各第１タンク部１１０ｂ、第２タンク部１１０ｃを介して、それぞれ連通している。   The plurality of tubes 110 are stacked so that the first tank portions 110b communicate with each other and the second tank portions 110c communicate with each other. Accordingly, the plurality of flat tube portions 110a communicate with each other via the first tank portions 110b and the second tank portions 110c.

フィン１２０は、断面が波形に形成され、放熱面に複数のルーバ１２２が設けられたコルゲートタイプのフィンであり、各チューブ１１０の扁平管部１１０ａ間に介在されている。そして、扁平管部１１０ａとフィン１２０とによって、コア部（熱交換部）１００ａが形成される。尚、本発明においては、このフィン１２０の形状に特徴を持たせており、詳細については後述する。   The fin 120 is a corrugated fin having a corrugated cross section and a plurality of louvers 122 provided on the heat dissipation surface, and is interposed between the flat tube portions 110 a of the tubes 110. The flat tube portion 110a and the fins 120 form a core portion (heat exchange portion) 100a. In the present invention, the shape of the fin 120 is characterized, and details will be described later.

そして、チューブ１１０の積層方向の一方の端部には、給湯口１３０および出湯口１４０が設けらており、給湯口１３０は第１タンク部１１０ｂに連通するように接続され、出湯口１４０は第２タンク部１１０ｃに連通するように接続されている。また、積層方向の両端に配置されるチューブ１１０の第１タンク部１１０ｂ、第２タンク部１１０ｃに対応する領域には、補強プレート１５０が設けられている。   A hot water supply port 130 and a hot water outlet 140 are provided at one end in the stacking direction of the tubes 110, and the hot water supply port 130 is connected to communicate with the first tank unit 110b. The two tank portions 110c are connected to communicate with each other. Reinforcing plates 150 are provided in regions corresponding to the first tank portion 110b and the second tank portion 110c of the tube 110 disposed at both ends in the stacking direction.

この熱交換器１００は、チューブ１１０の積層方向および長手方向が略水平方向となる姿勢で使用され、燃焼ガスがフィン１２０領域の上方から下方に向けて供給されるようにしている（図１、図３）。本発明においては、上記フィン１２０の燃焼ガスの出口側に、チューブ１１０の表面と非接触となって下方に延設される延設部１２１を設けるようにしており、更に、この延設部１２１には、本発明における突出部を成すルーバ１２２が形成されるようにしている。尚、ここでは延設部１２１は、チューブ１１０のフランジ部１１１ａ、１１２ａの下端部よりも更に下側まで延びるようにしている。   The heat exchanger 100 is used in a posture in which the stacking direction and the longitudinal direction of the tubes 110 are substantially horizontal, and the combustion gas is supplied from the upper side to the lower side of the fin 120 region (FIG. 1). FIG. 3). In the present invention, an extended portion 121 that extends downwardly in a non-contact manner with the surface of the tube 110 is provided on the outlet side of the combustion gas of the fin 120, and this extended portion 121 is further provided. The louver 122 which forms the protrusion in the present invention is formed. Here, the extended portion 121 extends further below the lower end portions of the flange portions 111a and 112a of the tube 110.

次に、上記構成に基づく熱交換器１００の作動およびその作用効果について説明する。給湯水は、熱交換器１００の給湯口１３０から第１タンク部１１０ｂに流入し、各チューブ１１０の扁平管部１１０ａを流れて、第２タンク部１１０ｃから出湯口１４０を通って流出する。   Next, the operation of the heat exchanger 100 based on the above configuration and the operation and effect thereof will be described. The hot water flows into the first tank portion 110b from the hot water inlet 130 of the heat exchanger 100, flows through the flat tube portion 110a of each tube 110, and flows out from the second tank portion 110c through the hot water outlet 140.

一方、燃焼ガス（１次熱交換器通過後の２００℃レベルの燃焼ガス）は、図示しないケース部材に導入されて熱交換器１００のコア部１００ａを上方から下方に向けて通過し、給湯器のガス排出口から外部に排出される。   On the other hand, the combustion gas (combustion gas at 200 ° C. after passing through the primary heat exchanger) is introduced into a case member (not shown) and passes through the core portion 100a of the heat exchanger 100 from the top to the bottom. It is discharged outside from the gas outlet.

燃焼ガスは、コア部１００ａを通過する際に給湯水との熱交換を行い、給湯水を加熱する。この時、燃焼ガスは、少なくともコア部１００ａの出口側で露点温度以下（例えば３０〜５０℃）まで温度低下して凝縮する。即ち、この熱交換器１００は、燃焼ガスの顕熱だけでなく、燃焼ガスが凝縮する際に放出される潜熱をも吸収して給湯水を加熱することができる。   When the combustion gas passes through the core portion 100a, it exchanges heat with hot water and heats the hot water. At this time, the combustion gas is condensed at a temperature lower than the dew point temperature (for example, 30 to 50 ° C.) at least on the outlet side of the core portion 100a. That is, the heat exchanger 100 can heat not only the sensible heat of the combustion gas but also the latent heat released when the combustion gas condenses to heat the hot water.

本発明においては、熱交換時に主にフィン１２０の表面で燃焼ガスから生成される凝縮水は、そのままフィン１２０の表面を伝わって流れ落ち、フィン１２０の延設部１２１に至るので、非接触と成るチューブ１１０との間で膜を張ることが無い。   In the present invention, the condensed water generated from the combustion gas mainly on the surface of the fin 120 during heat exchange flows down as it is on the surface of the fin 120 and reaches the extended portion 121 of the fin 120, so that it becomes non-contact. A film is not stretched between the tube 110.

そして、凝縮水は、図５に示すように、ルーバ１２２によって、点あるいは線で接触することになるので、延設部１２１内での付着、膜張りが抑えられて、スムースに落下していくようになり、凝縮水の詰まりが抑制される。よって、燃焼ガスがコア部１００ａを流通する際の通風抵抗が増大するのを抑えて熱交換効率の悪化を防止することができる。   Then, as shown in FIG. 5, the condensed water comes into contact with the louver 122 at a point or a line, so that adhesion and film tension in the extended portion 121 are suppressed, and the condensed water falls smoothly. As a result, clogging of condensed water is suppressed. Therefore, it is possible to prevent the heat exchange efficiency from deteriorating by suppressing an increase in ventilation resistance when the combustion gas flows through the core portion 100a.

図６、図７は、フィン１２０に延設部１２１を有さない従来技術と、延設部１２１（ここでは延設部１２１の長さを１４ｍｍとした）およびこの延設部１２１にルーバ１２２を設けた本発明との燃焼ガス風速に対するコア部１００ａの通風抵抗、熱伝達率を比較したものである。本発明においては、常用領域（燃焼ガス風速２．９ｍ／ｓ）で、通風抵抗を４０％低減でき、熱伝達率を４４％向上させることができた。   6 and 7 show a conventional technique in which the fin 120 does not have the extending portion 121, the extending portion 121 (the length of the extending portion 121 is 14 mm here), and the louver 122 in the extending portion 121. Is compared with the ventilation resistance and heat transfer coefficient of the core part 100a with respect to the combustion gas wind speed. In the present invention, the ventilation resistance can be reduced by 40% and the heat transfer rate can be improved by 44% in the normal range (combustion gas wind speed 2.9 m / s).

（第２実施形態）
本発明の第２実施形態を図８、図９に示す。第２実施形態は、上記第１実施形態に対して、フィン１２０の仕様、突出部の形状および延設部１２１の長さを変更したものとしている。 (Second Embodiment)
A second embodiment of the present invention is shown in FIGS. In the second embodiment, the specification of the fin 120, the shape of the protruding portion, and the length of the extending portion 121 are changed with respect to the first embodiment.

ここでは、フィン１２０は、断面が凹凸状に形成されるストレートフィンをベースにして、このフィン１２０のチューブ１１０に当接する面に、三角状に切り起こすことで形成される切り起こし部（以下、ウイングと呼ぶ）１２３を設けたものとしている（図９）。   Here, the fin 120 is based on a straight fin whose cross section is formed in an uneven shape, and a cut-and-raised portion (hereinafter referred to as “triangular”) formed by cutting the fin 120 into a triangular shape on the surface of the fin 120 that contacts the tube 110. It is assumed that a wing 123 is provided (FIG. 9).

そして、上記第１実施形態と同様に延設部１２１を設け、この延設部１２１にウイング（本発明における突出部に対応）１２３が形成されるようにしている。尚、延設部１２１の下端部位置は、チューブ１１０のフランジ部１１１ａ、１１２ａの下端部位置に合わせるようにしている（延設部１２１の長さ６ｍｍ）。   And the extended part 121 is provided similarly to the said 1st Embodiment, and the wing (corresponding | corresponding to the protrusion part in this invention) 123 is formed in this extended part 121. As shown in FIG. In addition, the lower end part position of the extension part 121 is made to match the lower end part position of the flange parts 111a and 112a of the tube 110 (length of the extension part 121 is 6 mm).

これにより、上記第１実施形態と同様にフィン１２０における凝縮水の詰まりが抑制され、熱交換効率の悪化を防止することができる。また、フィン１２０の下端部位置をチューブ１１０の下端部位置に合わせるようにしているので、チューブ１１０に対するフィン１２０の位置合わせがやり易くなり、組み付けが容易になる。   Thereby, like the said 1st Embodiment, clogging of the condensed water in the fin 120 is suppressed, and deterioration of heat exchange efficiency can be prevented. In addition, since the position of the lower end portion of the fin 120 is aligned with the position of the lower end portion of the tube 110, it is easy to align the fin 120 with respect to the tube 110, and assembly is facilitated.

（その他の実施形態）
上記第１、第２実施形態に対して、図１０、図１１に示すように、フィン１２０には、燃焼ガスの流入側に、即ち、上方側に延設される延設部１２１ａを設けるようにしても良い。尚、延設部１２１の下端部位置は、チューブ１１０のフランジ部１１１ａ、１１２ａの下端部位置に合わせ、延設部１２１ａの上端部位置は、フランジ部１１１ａ、１１２ａの上端部位置に合わせるようにしている。 (Other embodiments)
In contrast to the first and second embodiments, as shown in FIGS. 10 and 11, the fin 120 is provided with an extending portion 121 a extending on the combustion gas inflow side, that is, on the upper side. Anyway. Note that the position of the lower end portion of the extended portion 121 is aligned with the position of the lower end portion of the flange portions 111a and 112a of the tube 110, and the position of the upper end portion of the extended portion 121a is aligned with the position of the upper end portion of the flange portions 111a and 112a. ing.

これにより、フィン１２０の放熱面積を増大させて、熱交換性能を向上させることができると共に、チューブ１１０に対するフィン１２０の位置合わせを更に容易にすることができる。   Thereby, the heat dissipation area of the fin 120 can be increased to improve the heat exchange performance, and the alignment of the fin 120 with respect to the tube 110 can be further facilitated.

尚、上記各実施形態では熱交換器１００を給湯器用に使用するものとして説明したが、これに限らずその他のものにも広く活用できる。   In each of the above embodiments, the heat exchanger 100 is described as being used for a hot water heater. However, the present invention is not limited to this and can be widely used for other things.

第１実施形態における熱交換器を示す側面図である。It is a side view which shows the heat exchanger in 1st Embodiment. 図１のＡ方向から見た矢視図（平面図）である。It is an arrow view (plan view) seen from the A direction of FIG. 図１のＢ方向から見た矢視図（左側面図）である。It is an arrow view (left side view) seen from the B direction of FIG. 図３のＣ−Ｃ部における断面図である。It is sectional drawing in the CC section of FIG. 図４のＤ方向から見た矢視図である。It is the arrow line view seen from the D direction of FIG. 燃焼ガス風速に対するコア部の通風抵抗における第１実施形態の効果を示すグラフである。It is a graph which shows the effect of 1st Embodiment in the ventilation resistance of the core part with respect to combustion gas wind speed. 燃焼ガス風速に対するコア部の熱伝達率における第１実施形態の効果を示すグラフである。It is a graph which shows the effect of 1st Embodiment in the heat transfer rate of the core part with respect to combustion gas wind speed. 図３のＣ−Ｃ部における第２実施形態を示す断面図である。It is sectional drawing which shows 2nd Embodiment in CC part of FIG. 第２実施形態におけるフィンを示す斜視図である。It is a perspective view which shows the fin in 2nd Embodiment. 図３のＣ−Ｃ部におけるその他の実施形態１を示す断面図である。It is sectional drawing which shows the other Embodiment 1 in the CC section of FIG. 図３のＣ−Ｃ部におけるその他の実施形態２を示す断面図である。It is sectional drawing which shows other Embodiment 2 in the CC section of FIG. 従来技術の熱交換器におけるチューブおよびフィンを示す断面図である。It is sectional drawing which shows the tube and fin in the heat exchanger of a prior art. 図１２のＥ方向から見た矢視図（平面図）である。It is an arrow line view (plan view) seen from the E direction of FIG.

符号の説明Explanation of symbols

１００ 熱交換器
１１０ チューブ
１２０ アウターフィン（フィン）
１２１ 延設部
１２２ ルーバ（突出部）
１２３ 切り起こし部（突出部） 100 heat exchanger 110 tube 120 outer fin (fin)
121 Extension part 122 Louver (protrusion part)
123 Cut and raised part (protruding part)

Claims (4)

内部に流体通路を形成すると共に、積層配置される複数のチューブ（１１０）と、
前記複数のチューブ（１１０）の間に介在されて、伝熱面積を増大するフィン（１２０）とを備え、
前記フィン（１２０）の領域を上方から下方に向かって水蒸気を含む高温の気体が流れ、前記チューブ（１１０）の流体通路内に前記高温の気体より低温となる低温の流体を流通させて、前記高温の気体から顕熱のみならず凝縮潜熱をも回収して前記低温の流体を加熱する熱交換器であって、
前記フィン（１２０）の前記高温の気体の出口側には、前記チューブ（１１０）の表面と非接触となって下方へ延設される延設部（１２１）が設けられ、
且つ、前記延設部（１２１）には、前記フィン（１２０）の表面から突出する突出部（１２２、１２３）が設けられたことを特徴とする熱交換器。 A plurality of tubes (110) that form a fluid passage therein and are arranged in layers;
A fin (120) interposed between the plurality of tubes (110) to increase a heat transfer area;
A high-temperature gas containing water vapor flows from above to below the fin (120), and a low-temperature fluid having a temperature lower than that of the high-temperature gas is circulated in the fluid passage of the tube (110). A heat exchanger that recovers not only sensible heat but also latent heat of condensation from a high-temperature gas to heat the low-temperature fluid,
On the outlet side of the high-temperature gas of the fin (120), an extending portion (121) is provided that extends downward without being in contact with the surface of the tube (110).
The extension portion (121) is provided with protrusions (122, 123) protruding from the surface of the fin (120). 前記突出部（１２２、１２３）は、ルーバ（１２２）であることを特徴とする請求項１に記載の熱交換器。   The heat exchanger according to claim 1, wherein the protrusions (122, 123) are louvers (122). 前記突出部（１２２、１２３）は、前記フィン（１２０）の表面から切り起こされて形成される切り起こし部（１２３）であることを特徴とする請求項１に記載の熱交換器。   The heat exchanger according to claim 1, wherein the protrusions (122, 123) are cut and raised portions (123) formed by being cut and raised from the surface of the fin (120). 前記高温の気体は、燃焼ガスであり、
前記低温の流体は、給湯水であることを特徴とする請求項１〜請求項３のいずれかに記載の熱交換器。 The high temperature gas is a combustion gas,
The heat exchanger according to any one of claims 1 to 3, wherein the low-temperature fluid is hot water.
JP2004134423A 2004-04-28 2004-04-28 Heat exchanger Expired - Fee Related JP4211671B2 (en)

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DE102005018312A DE102005018312A1 (en) 2004-04-28 2005-04-20 Heat exchanger for water heater, has extension portion which is extended along downward direction of hot gas exit side of fin between hot-water tubes, such that extension portion is in non-contact with surface of tubes

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CN101358771B (en) * 2008-09-08 2010-06-02 中山华帝燃具股份有限公司 Plate heat exchanger for condensing gas water heater
CN103090543A (en) * 2013-02-01 2013-05-08 广东万和新电气股份有限公司 Gas appliance compact type heat exchanger
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JP2014044002A (en) * 2012-08-27 2014-03-13 Sumitomo Precision Prod Co Ltd Heat exchange unit
CN109974303A (en) * 2019-04-16 2019-07-05 廊坊一萍锅炉保养工程有限公司 A kind of gas-fired water heating boiler energy-saving appliance
CN110887232A (en) * 2018-09-07 2020-03-17 陕西希特新能源有限公司 Finned tube type heat exchanger of condensing boiler
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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101358771B (en) * 2008-09-08 2010-06-02 中山华帝燃具股份有限公司 Plate heat exchanger for condensing gas water heater
KR101326973B1 (en) * 2009-04-22 2013-11-13 니폰게이긴조쿠가부시키가이샤 Heat exchanger and air conditioner having the heat exchanger mounted therein
CN103238038A (en) * 2010-08-24 2013-08-07 开利公司 Microchannel heat exchanger fin
JP2014044002A (en) * 2012-08-27 2014-03-13 Sumitomo Precision Prod Co Ltd Heat exchange unit
CN103090543A (en) * 2013-02-01 2013-05-08 广东万和新电气股份有限公司 Gas appliance compact type heat exchanger
CN110887232A (en) * 2018-09-07 2020-03-17 陕西希特新能源有限公司 Finned tube type heat exchanger of condensing boiler
CN109974303A (en) * 2019-04-16 2019-07-05 廊坊一萍锅炉保养工程有限公司 A kind of gas-fired water heating boiler energy-saving appliance
CN109974303B (en) * 2019-04-16 2024-04-26 廊坊一萍锅炉保养工程有限公司 Energy-saving device for gas-fired hot water boiler
CN116293667A (en) * 2023-04-07 2023-06-23 西安交通大学 Combustor with inclined high-low staggered fire hole plates
CN116293667B (en) * 2023-04-07 2024-01-30 西安交通大学 Combustor with inclined high-low staggered fire hole plates

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